JP2015086520A - Vehicular door opening and closing device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a vehicular door opening and closing device which can suppress increase in size of first and second clutches or the like in an axial direction.SOLUTION: A vehicular door opening and closing device includes: a worm wheel part 45a which is rotationally driven by a motor; a drum 23 which is arranged coaxially with the worm wheel part 45a and performs opening and closing actuation of a slide door by moving a cable in accordance with the rotation; an output lever 37 which is arranged coaxially with the worm wheel part 45a and turns a door lock into the holding state of the slide door, or turns the door lock into the holding release state of the slide door in accordance with the rotation; a first clutch C1 which is stored in the drum 23 coaxially with the worm wheel part 45a, and connects and disconnects rotation transmission between the worm wheel part 45a and the drum 23; and a second clutch C2 which is stored in the worm wheel part 45a coaxially with the worm wheel part 45a and connects and disconnects rotation transmission between the worm wheel part 45a and the output lever 37.

Description

  The present invention relates to a vehicle door opening and closing device.

  Conventionally, as a vehicle door opening and closing device, for example, the one described in Patent Document 1 is known. This device includes a wire drum that opens and closes a vehicle door (sliding door) by winding and unwinding one or the other of a door opening cable and a door closing cable with rotation. In addition, this device includes a swing arm that disengages a pawl (ratchet) from a latch of a door lock that holds the vehicle door in a fully closed state with rotation. A first clutch is provided between the first worm wheel meshing with the output shaft (cylindrical worm) of the motor and the wire drum, and between the second worm wheel meshing with the output shaft and the swing arm. A second clutch is provided. Thus, by controlling the first clutch and the second clutch, the rotation of the wire drum and the swing arm can be performed while one motor is continuously rotated.

Japanese Patent No. 3694493

  By the way, in patent document 1, the wire drum, the 1st clutch, and the 1st worm wheel are supported by the 1st support axis arranged on the diameter one side centering on the axis to the output axis of a motor, The swing arm, the second clutch, and the second worm wheel are supported by a second support shaft that is parallel to the first support shaft disposed on the other side in the radial direction. For this reason, when the vehicle door opening / closing device is projected in the axial direction of the output shaft of the motor, the occupied area of the vehicle door opening / closing device increases, and the vehicle mountability is inevitably deteriorated.

  Therefore, the present inventor proposed that the first support shaft and the second support shaft are arranged coaxially, and the wire drum and the swing arm are arranged so as to overlap with the first and second clutches in the common axial direction. ing. However, in this case, another problem arises that the vehicle door opening and closing device is enlarged in the axial direction.

  An object of the present invention is to provide a vehicle door opening / closing device capable of suppressing an increase in size in the axial direction of the first and second clutches.

  A vehicle door opening and closing device that solves the above problems includes a transmission gear that is rotationally driven by a motor, a pulley that is arranged coaxially with the transmission gear, and that opens and closes the vehicle door by moving a rope member with rotation. An output member arranged coaxially with the transmission gear and causing the door lock to be held by the vehicle door as it rotates, or the door lock to be released from holding the vehicle door, and coaxial with the transmission gear A first clutch that is housed in the pulley and that connects and disconnects rotation transmission between the transmission gear and the pulley, and is accommodated in the transmission gear coaxially with the transmission gear, and transmits rotation between the transmission gear and the output member. And a second clutch that is connected and disconnected.

  According to this configuration, the rotation transmission between the transmission gear and the pulley is connected by the first clutch, and the rotation transmission between the transmission gear and the output member is disconnected by the second clutch. Thus, the rotation of the transmission gear driven to rotate by the motor is transmitted only to the pulley. As a result, the pulley rotates, the rope member moves, and the vehicle door opens and closes. On the other hand, the rotation transmission between the transmission gear and the pulley is disconnected by the first clutch, and the rotation transmission between the transmission gear and the output member is connected by the second clutch. The rotation of the transmission gear that is driven to rotate is transmitted only to the output member. As a result, the output member rotates to bring the door lock into the vehicle door holding state, or the door lock into the vehicle door holding release state. In particular, although the transmission gear, the pulley, the output member, the first clutch and the second clutch are arranged coaxially with each other, the first clutch is accommodated in the pulley, and the second clutch is the transmission gear. By being accommodated in, the enlargement to those axial directions can be suppressed.

In the vehicle door opening and closing device, it is preferable that the first clutch and the second clutch are both constituted by a planetary gear mechanism.
According to this configuration, each of the first clutch and the second clutch employs the sun gear, the internal gear, and the carrier of the planetary gear mechanism as any of an input shaft, an output shaft, and a fixed shaft during rotation transmission. And the degree of design freedom can be improved.

In the vehicle door opening and closing device, it is preferable that the transmission gear is integrally formed with sun gears of the planetary gear mechanisms.
According to this configuration, the two sun gears are integrally formed with the transmission gear, so that the number of parts can be reduced.

  In the vehicle door opening and closing device, a motor housing that supports the motor, a first housing that forms a first housing space for housing the pulley and the first clutch together with the motor housing, the transmission gear, and the first A second housing that forms a second housing space for housing the two clutches together with the motor housing, the motor housing having a through-hole that communicates the first housing space and the second housing space; It is preferable that the through hole is set larger than the diameter of the sun gear of the first clutch.

According to this configuration, it is possible to assemble the members in the axial direction while separating the first accommodation space and the second accommodation space.
In the vehicle door opening and closing device, it is preferable that the transmission gear is formed of a resin material, and the sun gears are set to have different diameters.

  According to this configuration, by setting the two sun gears to have different diameters, it is possible to prevent sinks when the transmission gear is formed of the resin material. In addition, by using the sun gear having the smaller diameter for the output-side clutch that requires a high reduction ratio, for example, it is possible to obtain a high reduction ratio without increasing the diameter of the ring gear.

  In the vehicle door opening and closing device, the first support shaft that supports the pulley and the first clutch together with the transmission gear, and the first support shaft that supports the output member and the second clutch together with the transmission gear. It is preferable to have an independent second support shaft.

  According to this configuration, the first support shaft that supports the pulley and the like and the second support shaft that supports the output member and the like are independent from each other, so that the first support shafts are not restricted to each other. And each of the second support shafts can be employed as any of the input shaft, the output shaft and the fixed shaft at the time of rotation transmission of the planetary gear mechanism, and the degree of freedom in design can be improved.

  The present invention has an effect of suppressing the increase in size in the axial direction of the first and second clutches.

1 is a side view schematically showing a first embodiment of the present invention. The side view which shows the same embodiment typically. (A)-(c) is explanatory drawing which shows operation | movement of a latch mechanism. The disassembled perspective view which shows the same embodiment. The longitudinal cross-sectional view which shows the same embodiment. (A), (b) is explanatory drawing which shows operation | movement of a 2nd clutch. (A), (b) is explanatory drawing which shows operation | movement of a latch mechanism. (A)-(c) is explanatory drawing which shows operation | movement of a latch mechanism. (A)-(c) is explanatory drawing which shows operation | movement of an output lever. The disassembled perspective view which shows the 2nd Embodiment of this invention. The longitudinal cross-sectional view which shows the same embodiment. The fragmentary longitudinal cross-section which shows the modification of this invention.

(First embodiment)
Hereinafter, a first embodiment of a vehicle door opening and closing device will be described. Hereinafter, the front-rear direction of the vehicle is referred to as “front-rear direction”.

  As shown in FIG. 1, the vehicle body 10 is provided with an upper rail 11 and a lower rail 12 along an upper edge and a lower edge of a door opening 10a formed on a side portion thereof, and at the rear of the vehicle with the door opening 10a. A center rail 13 extending in the front-rear direction is installed in the quarter panel 10b. A slide door 20 as a vehicle door is supported on the upper rail 11, the lower rail 12 and the center rail 13 via a guide roller unit 14 so as to be movable in the front-rear direction. The sliding door 20 opens and closes the door opening 10a as it moves in the front-rear direction. The quarter panel 10b is provided with a cable guide 15 along the lower edge of the center rail 13 over substantially the entire length thereof.

  A drive member 21 is fixed to the inside lower part of the slide door 20. The drive member 21 includes a motor 22 and a drum 23 as a pulley that is rotationally driven by the motor 22, and a first cable 24 and a second cable 25 as rope members are wound around the drum 23. ing. That is, each of the first and second cables 24 and 25 is wound around the drum 23 in a state where one terminal is connected to the drum 23. The first and second cables 24 and 25 are selectively wound and unwound by the drive member 21.

  Each of the first and second cables 24 and 25 passes from the slide door 20 side to the vehicle body 10 side via a guide pulley 27 connected to the intermediate pulley 26 and the guide roller unit 14 that moves the center rail 13. And routed in the front-rear direction along the cable guide 15. The first cable 24 is guided by the cable guide 15 and routed in front of the vehicle, and is connected to the vehicle body 10 side on the front end side of the cable guide 15 via a tensioner 28 connected to the other terminal. ing. The second cable 25 is guided by the cable guide 15 and routed behind the vehicle, and is connected to the vehicle body 10 side on the rear end side of the cable guide 15 via a tensioner 29 connected to the other terminal. Has been.

  In such a configuration, for example, when the second cable 25 is wound up while the first cable 24 is wound out by the driving member 21, the slide door 20 moves to the rear of the vehicle so as to open the door opening 10a. On the other hand, when the second cable 25 is unwound while winding the first cable 24 by the drive member 21, the slide door 20 moves forward of the vehicle to close the door opening 10a.

  As shown in FIG. 2, a remote controller (remote controller) 30 is installed in the slide door 20. The remote controller 30 has a known mechanism 31 composed of a plurality of levers and the like. The slide door 20 is provided with a front lock 32 and a rear lock 33 as door locks at the front and rear, respectively, and a fully open lock 34 as a door lock at the bottom.

  Each of the front lock 32 and the rear lock 33 is engaged with the vehicle body 10 side to hold the slide door 20 in a closed state (fully closed state or half door state), or engaged with the vehicle body 10 side. The slide door 20 in the closed state is released to be in an openable state. The fully open lock 34 engages with the vehicle body 10 side to hold the slide door 20 in a fully open state, or releases the engagement with the vehicle body 10 side to make the slide door 20 in the fully open state closeable. To do.

Here, the structure of the rear lock 33 will be described.
As shown in FIGS. 3A to 3C, a base plate 20 a is fixed to the slide door 20. The rear lock 33 has a latch mechanism 70 supported by the base plate 20a. The latch mechanism 70 includes a latch 73 and a pole 74 that are rotatable around a pair of parallel rotation shafts 71 and 72 disposed on the base plate 20a.

  The latch 73 is formed with a substantially U-shaped engaging recess 73a. The latch 73 has a first claw portion 73b and a second claw portion 73c on one side and the other side of the engagement recess 73a (on the clockwise and counterclockwise sides in FIG. 3A), respectively. Form. The latch 73 forms a third claw portion 73d that protrudes from the middle portion in the longitudinal direction of the first claw portion 73b. In the circumferential direction, the end surface of the first claw portion 73b and the end surface of the third claw portion 73d facing the second claw portion 73c form a full latch engagement surface 73e and a half latch engagement surface 73f, respectively. The latch 73 is biased by a latch biasing spring (not shown) to the side rotated counterclockwise in the figure, and is also referred to as a predetermined rotation position (hereinafter referred to as “unlatch position”) shown in FIG. ). The latch 73 has an arm-like interlocking piece 73g that extends from the rotating shaft 71 to the opposite side of the engaging recess 73a.

  On the other hand, the pole 74 forms a substantially claw-like engagement end portion 74a that extends from the rotating shaft 72 to one side in the radial direction (the right side in FIG. 3A). The pole 74 is biased by a pole biasing spring (not shown) to the side that rotates in the clockwise direction in the drawing, that is, the side that moves the engagement end 74a downward in the drawing, as shown in FIG. It is held at a predetermined rotational position.

Here, the basic operation of the latch mechanism 70 will be described.
As shown in FIG. 3A, in a state where the slide door 20 is opened, the latch 73 held at the unlatched position makes the engaging recess 73 a face the striker 75 fixed to the vehicle body 10. That is, the engagement recess 73a opens the entry path of the striker 75 that accompanies the closing operation of the slide door 20. Further, the pole 74 held at the predetermined rotation position has an engagement end 74a disposed on the upper side of the third claw 73d in the drawing. The state of the latch mechanism 70 at this time is referred to as an unlatched state (release state).

  Next, as shown by the change from FIG. 3A to FIG. 3B, it is assumed that the striker 75 has entered the engagement recess 73a as the slide door 20 is closed. At this time, the striker 75 presses the inner wall surface of the engaging recess 73a, so that the latch 73 rotates in the clockwise direction against the latch urging spring and engages with the half latch engaging surface 73f. The end 74a is locked to prevent rotation. At this time, the sliding door 20 is in a half-door state that engages with the striker 75 in the engaging recess 73a and prevents it from coming off. The state of the latch mechanism 70 at this time is called a half latch state, and the rotation position of the latch 73 is called a half latch position.

  Subsequently, as shown by a change from FIG. 3B to FIG. 3C, it is assumed that the striker 75 further enters the engagement recess 73 a as the slide door 20 is further closed. At this time, the inner wall surface of the engaging recess 73a is pressed by the striker 75, whereby the latch 73 further rotates in the clockwise direction shown in the figure against the latch urging spring and engages with the full latch engaging surface 73e. The end 74a is locked to prevent rotation. At this time, the slide door 20 is in a fully closed state in which it engages with the striker 75 in the engagement recess 73a and prevents it from coming off. The state of the latch mechanism 70 at this time is called a full latch state (engaged state), and the rotation position of the latch 73 is called a full latch position.

  Further, in the half latch state or the full latch state, when the pole 74 rotates counterclockwise in the illustrated direction against the pole biasing spring, the half latch engagement surface 73f or the full latch engagement surface 73e formed by the engagement end portion 74a. The lock is released. At this time, the latch 73 is pressed against the inner wall surface of the engagement recess 73a by the striker 75 that retreats from the engagement recess 73a as the slide door 20 starts to open due to the repulsive force of the seal member, for example. Thus, it rotates in the counterclockwise direction shown in the figure. The slide door 20 can be released by releasing the engagement with the striker 75 in the engagement recess 73a.

  The front lock 32 includes a latch mechanism 70 similar to the rear lock 33 except that the interlocking piece 73g of the latch 73 is omitted, and operates in the same manner as the rear lock 33. On the other hand, the fully open lock 34 includes a latch mechanism 70 similar to that of the rear lock 33, and operates similarly to the rear lock 33 by replacing "open" and "close" with "closed" and "open", respectively.

  By the way, each of the front lock 32 and the rear lock 33 is mechanically linked to the mechanism portion 31 of the remote controller 30 at the pole 74, and the release operation force from the mechanism portion 31 is input to the vehicle body as described above. 10, the slide door 20 is opened. On the other hand, the fully open lock 34 is also mechanically linked to the mechanism portion 31 of the remote controller 30 at the pole 74, and the sliding door 20 can be closed with respect to the vehicle body 10 by inputting a release operation force from the mechanism portion 31. Put it in a state. That is, this release operation force is an operation force that rotates the pole 74 against the pole biasing spring to release the holding state of the slide door 20 by the latch mechanism 70.

  As shown in FIG. 2, the remote control 30 is provided with an inside handle 35 on the inner side of the vehicle. The inside handle 35 is mechanically linked to the mechanism portion 31 of the remote controller 30, and inputs a release operation force to each of the front lock 32, the rear lock 33, and the fully open lock 34 via the mechanism portion 31.

  For example, when the inside handle 35 is operated from the neutral position to the rear of the vehicle (hereinafter referred to as “opening direction”) by the occupant in the closed state of the slide door 20, the inside handle 35 is connected via the mechanism unit 31. A release operation force is input to each of the front lock 32 and the rear lock 33. Thereby, each of the front lock 32 and the rear lock 33 brings the slide door 20 into an openable state with respect to the vehicle body 10.

  On the other hand, when the inside handle 35 is operated from the neutral position to the front of the vehicle (hereinafter referred to as “closing direction”) by the occupant in the fully opened state of the slide door 20, the inside handle 35 is interposed via the mechanism unit 31. The release operation force is input to the fully open lock 34. As a result, the fully open lock 34 brings the slide door 20 into a closeable state with respect to the vehicle body 10.

  The slide door 20 is provided with an outside handle 36 on the outside of the vehicle. The outside handle 36 is mechanically linked to a mechanism portion 31 of the remote controller 30, and inputs a release operation force to each of the front lock 32, the rear lock 33, and the fully open lock 34 via the mechanism portion 31.

  An output lever 37 as an output member that is rotationally driven by the motor 22 is provided in the lower part of the slide door 20. The output lever 37 is disposed coaxially with the drum 23, is mechanically linked to the mechanism 31 of the remote controller 30 via a release cable 38, and a rear lock 33 (latch 73) via a closer cable 39. Are mechanically linked to each other.

  The output lever 37 rotates in one direction to input a release operation force to each of the front lock 32, the rear lock 33, and the fully open lock 34 via the release cable 38 and the mechanism portion 31. As a result, the slide door 20 in the closed state can be opened as described above, or the slide door 20 in the fully opened state can be closed.

  Further, the output lever 37 rotates in the other direction, thereby inputting an engaging operation force to the rear lock 33 via the closer cable 39. This engagement operation force is an operation force for rotating the latch 73 of the rear lock 33 from the half latch position to the full latch position against the latch biasing spring. Thereby, for example, the rear lock 33 is switched together with the front lock 32 from a state in which the slide door 20 is held in a half door state to a state in which the slide door 20 is held in a fully closed state.

Next, the structure of the drive member 21 will be further described.
As shown in FIGS. 4 and 5, the drive member 21 has a motor housing 41 that forms its outer shape, a drum cover 42 as a first housing, and a locking housing 43 as a second housing. The motor housing 41 is made of, for example, a resin material. The motor housing 41 rotatably accommodates a worm 44 provided on the rotating shaft of the motor 22 that supports the motor housing 41 and serves as a transmission gear that meshes with the worm 44 of the worm wheel 45 made of a resin material. The worm wheel portion 45a is rotatably accommodated. Note that the worm wheel portion 45a is formed in a substantially cylindrical shape with a lid that opens to the lower side in the figure, and forms a gear-side accommodation space Sg. This is because the worm wheel portion 45a is difficult to use in the outer space because the worm 44 (motor 22) is disposed along the outer periphery thereof, but the inner peripheral portion of the worm wheel portion 45a can be used as a storage space. Because there is. Further, the worm wheel 45 integrally includes a first sun gear portion 45b and a second sun gear portion 45c that protrude from the lid wall portion of the worm wheel portion 45a coaxially to the upper side and the lower side in the drawing, respectively. The second sun gear portion 45c is shaped so as to be generally contained within the gear-side accommodation space Sg. The first sun gear portion 45b and the second sun gear portion 45c are set to have different diameters, that is, the diameter of the second sun gear portion 45c is smaller than the diameter of the first sun gear portion 45b.

  The drum cover 42 is formed, for example, with a resin material into a substantially cylindrical shape with a lid that opens downward in the figure, and is fixed to the upper side of the motor housing 41 in the figure to accommodate the drum 23 rotatably. That is, the drum 23 is fixed so as to rotate integrally with a first support shaft 46 disposed coaxially with the worm wheel 45. One end of the first support shaft 46 is pivotally supported by the first sun gear portion 45 b, and the other end is pivotally supported by a bearing 47 fitted to the lid wall portion of the drum cover 42. As described above, the drum 23 is rotatable in the drum cover 42.

  The drum 23 is formed in a substantially cylindrical shape with a lid that opens to the lower side in the figure, and forms a drum-side accommodation space Sd. This is because the drum 23 has a large length and diameter in the axial direction, and the inner peripheral portion can be used as a storage space. A first ring gear 48 and a first carrier 49 are accommodated in the drum-side accommodation space Sd. The first sun gear portion 45b, the first ring gear 48, and the first carrier 49 constitute a first clutch C1.

  The first ring gear 48 is formed in a substantially cylindrical shape with a lid that opens to the lower side of the figure, has a first internal gear 48a formed on the inner peripheral portion, and is radially from the tip that protrudes from the drum-side accommodation space Sd. An annular large wheel gear 48 b that extends outward and covers the opening end surface of the drum 23 is provided. The first internal gear 48 a constitutes a planetary gear mechanism together with the first sun gear portion 45 b and the first carrier 49.

  The first carrier 49 has a substantially Y-shaped first holding plate 49a fixed so as to rotate integrally with the first support shaft 46, and at the three branched ends of the first holding plate 49a. Three first planetary gears 49b each rotatably supported are provided. The first carrier 49 has a substantially annular first carrier plate 49c that prevents the three first planetary gears 49b from coming off in the axial direction between the first carrier plate 49a and the first holding plate 49a. When the first carrier 49 is inserted into the first ring gear 48, the three first planetary gears 49b mesh with the first internal gear 48a, and the first sun gear 45b is inserted into the first sun gear 45b with 3 Two first planetary gears 49b mesh with each other.

  As shown in FIG. 4, the drum cover 42 accommodates the first clutch C <b> 1 in addition to the drum 23. That is, the drum cover 42 forms a first accommodation space S1 that accommodates the drum 23 and the first clutch C1 together with the motor housing 41. The drum cover 42 is formed with a guide hole 42a that opens in the radial direction so as to include the position in the axial direction of the large wheel gear 48b. And the guide block 50 is being fixed to the drum cover 42 (or motor housing 41) facing the radial direction of the guide hole 42a. The guide block 50 is formed with a first guide groove 50a that opens in the radial direction of the drum cover 42 at the position of the guide hole 42a. A first internal gear fixing block 51 is movably mounted in the first guide groove 50a.

  When the first internal gear fixing block 51 moves in the first guide groove 50 a in one direction approaching the first ring gear 48, the first internal gear fixing block 51 engages with the large wheel gear 48 b to make the first ring gear 48 non-rotatable. At this time, the first sun gear portion 45b, the first internal gear 48a, and the first carrier 49 serve as an input shaft, a fixed shaft, and an output shaft of the planetary gear mechanism, respectively, and the rotation of the first sun gear portion 45b (worm wheel 45) is caused. Transmission to the first carrier 49 is possible. This state is referred to as a connected state of the first clutch C1.

  On the other hand, the first internal gear fixing block 51 rotates the first ring gear 48 by releasing the engagement with the large gear 48b when moving in the other direction away from the first ring gear 48 in the first guide groove 50a. to enable. At this time, the rotation of the first sun gear portion 45 b (worm wheel 45) cannot be transmitted to the first carrier 49. This state is referred to as a disconnected state of the first clutch C1.

  The first internal gear fixing block 51 has an engagement pin 51 a that protrudes upward in the drawing from the guide block 50. A substantially fan-plate-shaped first switching lever 53 is rotatably connected to the upper side surface of the guide block 50 by a pin 52. An elongated cam hole 53 a into which the engagement pin 51 a is inserted is formed at the tip of the first switching lever 53. When the first switching lever 53 rotates in one direction around the pin 52, the first internal gear fixing block 51 approaches the first ring gear 48 by pushing the engagement pin 51 a through the cam hole 53 a. Move in one direction. Alternatively, when the first switching lever 53 rotates in the other direction around the pin 52, the first internal gear fixing block 51 is moved to the first ring gear 48 by pulling the engagement pin 51 a through the cam hole 53 a. Move away from the other direction.

  The first switching lever 53 is connected to a switching actuator 54 mainly composed of, for example, an electric motor via a rod 55, and selectively rotated in one direction and the other direction by the switching actuator 54. Is done. The driving timing of the first switching lever 53 by the switching actuator 54, that is, the switching timing of the first clutch C1 is controlled based on the opening / closing position of the slide door 20 detected by a known door position sensor. Yes.

  The locking housing 43 is made of, for example, a resin material, and has a bottomed substantially cylindrical accommodating portion 43a that opens upward in the figure. The locking housing 43 supports the worm wheel 45 in a rotatable manner. That is, a second support shaft 56 that is disposed coaxially with the worm wheel 45 is supported by the accommodating portion 43a. One end of the second support shaft 56 is inserted and pivotally supported in a substantially circular bearing hole 43b shown in FIG. 5 formed in the bottom wall portion of the accommodating portion 43a, and the other end is supported by the second sun gear portion 45c. It is pivotally supported. As described above, the second sun gear portion 45 c (worm wheel 45) is rotatably supported by the locking housing 43 via the second support shaft 56.

  A second ring gear 57 and a second carrier 58 are accommodated in the gear-side accommodation space Sg. The second sun gear portion 45c, the second ring gear 57, and the second carrier 58 constitute a second clutch C2. That is, the locking housing 43 forms a second housing space S2 that houses the worm wheel portion 45a and the second clutch C2 together with the motor housing 41. The motor housing 41 has a through hole A1 that communicates the first accommodation space S1 and the second accommodation space S2. The through hole A1 is set to be larger than the diameter of the first sun gear portion 45b of the first clutch C1.

  The second ring gear 57 is formed in a substantially cylindrical shape with a bottom opening on the upper side in the drawing, has a second internal gear 57a formed on the inner peripheral portion, and is radially from the tip protruding from the gear-side accommodation space Sg. It has an annular large ring gear 57b extending outward. The second internal gear 57a constitutes a planetary gear mechanism together with the second sun gear portion 45c and the second carrier 58.

  The second carrier 58 has a substantially triangular plate-like second holding plate 58a fixed so as to rotate integrally with the second support shaft 56, and is rotatable at three corners of the second holding plate 58a. There are three supported second planetary gears 58b. The second carrier 58 includes a substantially triangular annular second carrier plate 58c that prevents the three second planetary gears 58b from coming off in the axial direction between the second carrier plate 58a and the second holding plate 58a. When the second carrier 58 is inserted into the second ring gear 57, the three second planetary gears 58b mesh with the second internal gear 57a, and when the second sun gear portion 45c is inserted, the second carrier gear 58b is connected to the second sun gear portion 45c. Two second planetary gears 58b mesh with each other.

  The locking housing 43 is formed with a second guide groove 43c that extends in the radial direction of the housing portion 43a and communicates with the housing portion 43a. A second internal gear fixing block 61 is movably mounted in the second guide groove 43c at an axial position corresponding to the large wheel gear 57b.

  As shown in FIG. 6A, the second internal gear fixing block 61 engages with the large wheel gear 57b when moving the second guide groove 43c in one direction approaching the second ring gear 57. The two-ring gear 57 is made non-rotatable. At this time, the second sun gear 45c, the second internal gear 57a, and the second carrier 58 serve as an input shaft, a fixed shaft, and an output shaft of the planetary gear mechanism, respectively, and the rotation of the second sun gear 45c (worm wheel 45) is caused. Transmission to the second carrier 58 is possible. This state is referred to as a connected state of the second clutch C2.

  On the other hand, as shown in FIG. 6B, when the second internal gear fixing block 61 moves in the second guide groove 43c in the other direction away from the second ring gear 57, the engagement with the large wheel gear 57b is released. Thus, the second ring gear 57 can be rotated. At this time, the rotation of the second sun gear portion 45 c (worm wheel 45) cannot be transmitted to the second carrier 58. This state is referred to as a disconnected state of the second clutch C2.

  The second internal gear fixing block 61 has an engagement pin 61a that protrudes to one side (upper side in FIG. 4). On the other hand, the locking housing 43 is provided with a pin-shaped shaft portion 43d projecting upward from the portion farther from the housing portion 43a than the second guide groove 43c. A substantially fan-shaped second switching lever 62 is rotatably connected to the shaft portion 43d. An elongated cam hole 63 into which the engagement pin 61a is inserted is formed at the distal end of the second switching lever 62.

  As shown in FIG. 6, the cam hole 63 forms an arc-shaped large-diameter groove 63 a centering on the shaft portion 43 d at a portion on one circumferential side (counterclockwise direction in FIG. 6), An arc-shaped small-diameter groove 63b centering on the shaft portion 43d is formed in a portion closer to the shaft portion 43d than the large-diameter groove 63a on the other circumferential side (clockwise direction in FIG. 6). The large diameter groove 63a and the small diameter groove 63b communicate with each other via an inclined guide groove 63c. The circumferential length of the large diameter groove 63a is set sufficiently longer than the same length of the small diameter groove 63b.

  Therefore, the second switching lever 62 pushes the engagement pin 61a through the cam hole 63 (large diameter groove 63a) when rotating in one direction (clockwise rotation direction in FIG. 6) about the shaft portion 43d. Then, the second internal gear fixing block 61 is moved in one direction approaching the second ring gear 57. Alternatively, when the second switching lever 62 is rotated in the other direction (counterclockwise direction side in FIG. 6) about the shaft portion 43d, the engagement pin 61a is inserted into the cam hole 63 (small diameter groove 63b). By pulling in, the second internal gear fixing block 61 is moved in the other direction away from the second ring gear 57.

  The second switching lever 62 has an arm portion 64 extending in the radial direction with the shaft portion 43d as the center. One end of a door position interlocking cable 65 made of, for example, a push-pull cable is connected to the arm portion 64. The other end of the door position interlocking cable 65 is connected to the interlocking piece 73g of the rear lock 33. The arm portion 64 is connected to the opening / closing position (opening / closing state) of the slide door 20 via the door position interlocking cable 65. The engagement / disengagement force is input.

  That is, as shown in FIG. 7A, when the striker 75 enters the engagement recess 73a of the latch 73 of the rear lock 33 as the slide door 20 is closed from the open state, the striker 75 engages. When the inner wall surface of the recess 73a is pressed, the latch 73 starts to rotate from the unlatched position toward the full latched position. Then, the latch 73 pushes the door position interlocking cable 65 with the interlocking piece 73g. At this time, as shown by the change from FIG. 6B to FIG. 6A, the second switching lever 62 pressed by the arm portion 64 by the door position interlocking cable 65 rotates in the clockwise direction shown in the figure. Thus, as described above, the second clutch C2 is in the connected state.

  Even after the second clutch C2 enters the connected state, the second switching lever 62 pushed by the door position interlocking cable 65 continues to rotate as the latch 73 further rotates. At this time, the engagement pin 61a of the second internal gear fixing block 61 runs idle in the large-diameter groove 63a in the circumferential range of the large-diameter groove 63a, so that the connected state of the second clutch C2 is maintained. (2nd clutch side lost motion).

  On the other hand, as shown in FIG. 8A, when the full latch engagement surface 73e of the latch 73 is unlocked by the engagement end 74a of the pole 74 in the fully closed state of the slide door 20, the engagement recess When the inner wall surface of the engaging recess 73a is pressed by the striker 75 that retreats from the inside of 73a, the latch 73 starts to rotate from the full latch position toward the unlatched position. The latch 73 of the rear lock 33 pulls the door position interlocking cable 65 with the interlocking piece 73g. At this time, as shown in the change from FIG. 6A to FIG. 6B, the second switching lever 62 pulled by the arm portion 64 to the door position interlocking cable 65 rotates in the counterclockwise direction shown in the drawing. As a result, the second clutch C2 is in the disconnected state as described above. It goes without saying that the second clutch C2 is disconnected after a period during which the engagement pin 61a of the second internal gear fixing block 61 idles in the large diameter groove 63a in the circumferential direction of the large diameter groove 63a. Absent.

  The fully open lock 34 is similarly connected to the second switching lever 62 in the interlocking piece 73g of the latch 73, and the rear part is read by replacing "open" and "closed" with "closed" and "open", respectively. Similar to the lock 33, the second clutch C2 is operated.

  As shown in FIGS. 4 and 5, the output lever 37 is connected to the tip of the second support shaft 56 that penetrates the accommodating portion 43 a so as to rotate integrally. As shown in FIGS. 9A to 9C, a slit 37 a having a long hole extending in the circumferential direction around the second support shaft 56 is formed at the tip of the output lever 37. Yes. The slit 37a has a terminal 38a of the release cable 38 and a terminal 39a of the closer cable 39 inserted therein and prevented from coming off.

  Further, at the base end of the output lever 37, there is formed a substantially square plate-like movable side locking piece 37b bent to one side (the back side orthogonal to the paper surface in FIG. 9). On the other hand, the locking housing 43 is provided with a substantially square plate-like fixed side locking piece 43e that can face the movable side locking piece 37b at a position farther from the second support shaft 56 than the movable side locking piece 37b. Has been.

  A return spring 66 made of a torsion coil spring is wound around the second support shaft 56. Both ends of the return spring 66 extend in the radial direction toward the fixed-side locking piece 43e and the like centering on the second support shaft 56, and elastically extend to both ends in the circumferential direction of the fixed-side locking piece 43e and the like. Can be contacted.

  9A, the return spring 66 biases and holds the output lever 37 so that the fixed side locking piece 43e and the movable side locking piece 37b are aligned in the radial direction. The rotation position of the output lever 37 at this time is referred to as an initial position Ps.

  Here, as shown in FIG. 9A, when the output lever 37 is held at the initial position Ps, the terminal 38a of the release cable 38 and the terminal 39a of the closer cable 39 are both ends in the circumferential direction of the slit 37a. Respectively. Therefore, in this state, as shown in FIG. 9B, when the output lever 37 rotates in the illustrated counterclockwise rotation direction (hereinafter also referred to as “release direction”) against the urging force of the return spring 66, The release cable 38 to be pushed by the terminal 38a is pulled by the slit 37a. At this time, a release operation force is input to each of the front lock 32, the rear lock 33, and the fully open lock 34 via the mechanism portion 31. On the other hand, since the terminal 39a runs idle in the range of the slit 37a, the closer cable 39 is not pulled (closer side lost motion).

  On the other hand, as shown in FIG. 9C, when the output lever 37 rotates from the initial position Ps in the clockwise rotation direction (hereinafter also referred to as “closer direction”) against the urging force of the return spring 66, the slit The closer cable 39 to be pushed by the terminal 39a is pulled by 37a. At this time, an engaging operation force is input to the latch 73 of the rear lock 33. On the other hand, the release cable 38 is not pulled by the terminal 38a running idle in the range of the slit 37a (release-side lost motion).

Next, the operation of this embodiment will be described.
First, it is assumed that the slide door 20 is in an open state. At this time, the engagement pin 61a of the second internal gear fixing block 61 is positioned in the small-diameter groove 63b of the second switching lever 62 interlocked with the latch 73 of the rear lock 33 in the unlatched position via the door position interlocking cable 65. Thus, the second clutch C2 is in a disconnected state.

  In this state, when the first clutch C1 is switched to the connected state by the switching actuator 54 and the motor 22 is rotated so as to close the slide door 20, the rotation of the worm 44 is performed via the worm wheel 45a and the first clutch C1. Then, the slide door 20 starts closing operation.

  As shown in FIG. 7A, when the striker 75 enters the engaging recess 73a of the latch 73 as the slide door 20 is closed, the striker 75 presses the inner wall surface of the engaging recess 73a. 73 starts to rotate from the unlatched position. In addition, the second switching lever 62 pushed by the interlocking piece 73g of the latch 73 of the rear lock 33 via the door position interlocking cable 65 starts to rotate. Then, when the latch 73 rotates to near the half latch position, the large diameter groove 63a of the second switching lever 62 reaches the engagement pin 61a of the second internal gear fixing block 61, as described above. The second clutch C2 is switched to the connected state.

  Subsequently, when the first clutch C1 is switched to the disconnected state by the switching actuator 54 and the motor 22 is continuously rotated, the rotation of the worm 44 is transmitted to the output lever 37 via the worm wheel portion 45a and the second clutch C2. . As a result, the output lever 37 rotates in the closer direction from the initial position Ps, pulls the closer cable 39, and inputs an engaging operation force to the latch 73 of the rear lock 33.

  Accordingly, as shown in FIG. 7B, the latch 73 of the rear lock 33 rotates to the full latch position while pulling in the striker 75, and the engagement end portion 74a of the pole 74 moves the full latch engagement surface 73e. By latching, the latch mechanism 70 is in a fully latched state, and the slide door 20 is held in a fully closed state. In the fully latched state of the latch mechanism 70, the second clutch C2 maintains the connected state even if the motor 22 is stopped by the latch 73 maintaining the full latch position. When the motor 22 is stopped, the output lever 37 is urged by the return spring 66 and returns to the initial position Ps. Note that the latch mechanism 70 of the front lock 32 is in a fully latched state in accordance with the closing operation of the slide door 20 by the rear lock 33.

  By the way, while the latch 73 rotates to the full latch position, the second switching lever 62 pushed through the door position interlocking cable 65 continues to rotate. At this time, absorption by the second clutch-side lost motion by the large-diameter groove 63a is as described above. Further, when inputting the engagement operation force to the latch 73 of the rear lock 33, the release operation force is input to each of the front lock 32, the rear lock 33, and the fully open lock 34 by absorbing the release side lost motion by the slit 37a. It will never be done.

Next, it is assumed that the slide door 20 is in a fully closed state. At this time, as described above, the second clutch C2 is in the connected state.
In this state, when the motor 22 is rotated to input a release operation force to each of the front lock 32, the rear lock 33, and the fully open lock 34 with the first clutch C1 being disconnected, the rotation of the worm 44 causes the worm wheel 45a to rotate. And is transmitted to the output lever 37 via the second clutch C2. As a result, the output lever 37 rotates in the release direction from the initial position Ps to pull the release cable 38, and a release operation force is input to each of the front lock 32, the rear lock 33, and the fully open lock 34 via the mechanism unit 31. .

  Accordingly, as shown in FIG. 8 (a), when the engagement end 74a of the pole 74 releases the locking of the full latch engagement surface 73e, the striker 75 retracts from the engagement recess 73a to engage the recess 73a. When the inner wall surface is pressed, the latch 73 starts to rotate from the full latch position toward the unlatch position. Further, the second switching lever 62 pulled by the interlocking piece 73g of the latch 73 of the rear lock 33 via the door position interlocking cable 65 starts to rotate. Then, as shown in FIG. 8B, when the latch 73 is rotated until it exceeds the half-latch position, the small-diameter groove 63b of the second switching lever 62 is formed on the engaging pin 61a of the second internal gear fixing block 61. By arriving, the second clutch C2 is switched to the disconnected state as described above. When the second clutch C2 is switched to the disconnected state, the output lever 37 is biased by the return spring 66 and returns to the initial position Ps. As shown in FIG. 8C, the second switching lever 62 continues to rotate until the latch 73 of the rear lock 33 reaches the unlatched position, but as described above, the second clutch by the large-diameter groove 63a. Absorb with side lost motion.

  Subsequently, when the first clutch C1 is switched to the connected state by the switching actuator 54 and the motor 22 is continuously rotated, the rotation of the worm 44 is transmitted to the drum 23 via the worm wheel portion 45a and the first clutch C1. . Then, the sliding door 20 starts to open. When the latch 73 of the full-open lock 34 is brought into the full latch state while pulling the corresponding striker 75 with the opening operation of the slide door 20, the slide door 20 is held in the full open state.

  As described above, since the fully open lock 34 operates the second clutch C2 similarly to the rear lock 33, the second clutch C2 is in the connected state when the slide door 20 is fully open. Accordingly, in the closing operation of the slide door 20, the motor 22 is rotated to input the release operation force to each of the front lock 32, the rear lock 33, and the fully open lock 34, and the second clutch C2 is switched to the disconnected state. Accordingly, the first clutch C1 is connected and the motor 22 is rotated in the reverse direction. Accordingly, the rotation of the worm 44 is transmitted to the drum 23 via the worm wheel portion 45a and the first clutch C1, and the sliding door 20 starts to close. The transition to the fully closed state accompanying the closing operation of the slide door 20 is as described above.

As described above in detail, according to the present embodiment, the following effects can be obtained.
(1) In this embodiment, the worm wheel portion 45a, the drum 23, the output lever 37, the first clutch C1, and the second clutch C2 are arranged coaxially with each other. However, since the first clutch C1 is accommodated in the drum 23 and the second clutch C2 is accommodated in the worm wheel portion 45a, their axial size increases, that is, in the vehicle width direction (door thickness direction). An increase in size can be suppressed. And the vehicle mounting property (door mounting property) of the drive member 21 can be improved. Alternatively, since it is not necessary to increase the door thickness in order to mount the driving member 21 on the slide door 20, it is possible to suppress the indoor space from being narrowed by the slide door 20.

  (2) In the present embodiment, each of the first clutch C1 and the second clutch C2 is composed of a planetary gear mechanism, so that the sun gear, the internal gear, and the carrier of the planetary gear mechanism serve as the input shaft, the output shaft, and the rotation. It can be employed as one of the fixed shafts during transmission, and the degree of freedom in design can be improved.

  (3) In the present embodiment, the sun gear (first sun gear portion 45b and second sun gear portion 45c) of both planetary gear mechanisms is integrally formed on the worm wheel portion 45a, so that the number of parts can be reduced. . In addition, since a shape for connecting the worm wheel portion 45a and the sun gears of the planetary gear mechanisms (the first sun gear portion 45b and the second sun gear portion 45c) is unnecessary, the size in the axial direction is increased accordingly. That is, an increase in size in the vehicle width direction (door thickness direction) can be suppressed.

  (4) In the present embodiment, the first support shaft 46 on the opening / closing operation side that supports the drum 23 and the like, and the second support shaft 56 on the release / closer operation side that supports the output lever 37 and the like are independent of each other. Accordingly, each of the first support shaft 46 and the second support shaft 56 can be employed as any of the input shaft, the output shaft, and the fixed shaft at the time of rotation transmission of the planetary gear mechanism without restricting each other. The degree of freedom can be improved. For example, the torque and rotation speed required for opening and closing the slide door 20 can be suitably ensured.

  (5) In the present embodiment, since the first support shaft 46 and the second support shaft 56 are independent from each other, each can be used as the output shaft of the corresponding planetary gear mechanism, and the degree of freedom in gear layout is improved. Can do.

  (6) In this embodiment, by using the first support shaft 46 and the second support shaft 56 that are independent from each other, the drum 23 related to the opening / closing operation and the output lever 37 related to the release / closer operation are both decelerated. It can be rotated with the sun gear input / carrier output with the largest ratio. For example, when the slide door 20 is retracted to the fully closed state, the rotation of the output lever 37 requiring a large torque can be handled with the maximum reduction ratio.

  In addition, since the first and second clutches C1 and C2 are both fixed to the internal gear, the connected state thereof can be maintained with a force smaller than that of, for example, carrier fixing. For example, even when a heavy load is input from the slide door 20, the connection state of the first clutch C1 can be more easily maintained.

  (7) In the present embodiment, since the first support shaft 46 and the second support shaft 56 are independent from each other, for example, the first clutch C1 on the opening / closing operation side and the second clutch C2 on the release / closer operation side are individually provided. The degree of freedom in the assembling order and the assembling direction can be improved. And the assembly man-hour of the drive member 21 can be reduced, and by extension, cost can be reduced.

  (8) In the present embodiment, since the first support shaft 46 and the second support shaft 56 are independent from each other, for example, the entire drive member 21 is divided into two on the first support shaft 46 side and the second support shaft 56 side. A pair of subassemblies, that is, an opening / closing operation subassembly and a release / closer operation subassembly can be used. In this case, the drive member 21 can be easily assembled using both of these subassemblies.

  (9) In the present embodiment, since the first support shaft 46 and the second support shaft 56 are independent from each other, for example, it is possible to cope with a vehicle specification in which only the release / closer function is mounted by a simple design change. be able to. That is, it can be easily handled by removing the first clutch C1 and the like on the opening / closing operation side.

  (10) In this embodiment, the first clutch C1 and the second clutch C2 are used to switch the output of one common motor 22 to realize the opening / closing operation and the release / closer operation. The number of parts, mass, and cost can be reduced as compared with the case where each motor is used. And since the mass of the slide door 20 can be reduced, it is advantageous for pinching detection and the like.

  (11) In the open state of the slide door 20 (excluding the fully open state), the motor 22 is rotated in one direction in the connected state of the first clutch C1 to close it, and then the first and second clutches C1, C2 are operated If the motor 22 is continuously rotated in one direction by switching to the disconnected state and the connected state, the sliding door 20 is fully closed along with the closer operation. In this manner, since the sliding door 20 can be handed over from the closing operation to the closing operation without rotating the motor 22 in the reverse direction, it is possible to suppress the delay in starting the operation and the complicated control due to the reversal.

  Further, in the fully closed state of the slide door 20, the motor 22 is rotated in the other direction with the second clutch C2 connected to perform release operation, and then the first and second clutches C1 and C2 are connected and disconnected respectively. If the motor 22 is continuously rotated in the other direction, the sliding door 20 is fully opened along with the opening operation. In this way, since the release operation can be taken over to the opening operation of the slide door 20 without rotating the motor 22 in the reverse direction, it is possible to suppress the delay of the operation start and the complicated control due to the reversal.

  (12) Since the connection and disconnection of the first and second clutches C1 and C2 can be switched independently of each other, the opening / closing operation and the release / closer operation can be performed independently of each other. For this reason, it is possible to prevent the first and second cables 24 and 25 from being stretched during the reverse operation, for example, the release operation, and the pulling of the release cable 38 and the closer cable 39 during the opening / closing operation.

  (13) When the sliding door 20 is manually opened and closed, if the first ring gear 48 is switched to the rotation-permitted state by the first internal gear fixing block 51 or the like, the drum rotates while the first ring gear 48 is idling. 23 (first carrier 49) is allowed to rotate. In this manner, the sliding door 20 can be opened and closed with a slight operating force by separating the rotational torque from the drum 23 side and the driving torque from the motor 22 side by the first internal gear fixing block 51 and the like. .

  (14) Since the switching state and the allowable state of the rotation of the first ring gear 48 by the first internal gear fixing block 51 and the like can be switched electrically by the switching actuator 54, for example, when manually performed Annoyance can be eliminated.

  (15) In the present embodiment, the switching between the restricted state and the allowable state of the rotation of the first ring gear 48 by the first internal gear fixing block 51 and the like is realized by a small number of components such as a small switching actuator 54 and the like. For example, the cost and weight can be reduced as compared with an electromagnetic clutch.

  (16) In the present embodiment, the motor housing 41 has a through hole A1 that communicates the first accommodation space S1 and the second accommodation space S2, and the through hole A1 is the first sun gear portion of the first clutch C1. By setting it larger than the diameter of 45b, it is possible to assemble the members in the axial direction while separating the first accommodation space S1 and the second accommodation space S2.

  (17) In the present embodiment, sink marks can be made difficult to occur by setting the first sun gear portion 45b and the second sun gear portion 45c of the worm wheel 45 formed of a resin material to have different diameters. Further, by using the second sun gear portion 45c having a smaller diameter for the second clutch C2 on the output side that requires a high reduction ratio, for example, a high reduction ratio can be obtained without increasing the diameter of the second ring gear 57. It becomes possible.

(Second Embodiment)
Hereinafter, a second embodiment of the vehicle door opening and closing device will be described. Note that the second embodiment has a configuration in which only the drive member of the first embodiment is changed, and therefore, detailed description of the same parts is omitted.

  As shown in FIGS. 10 and 11, the drive member 80 of the present embodiment has a drum cover 81 as a first housing and a locking housing 82 as a second housing that form the outer shape together with the motor housing 41.

  The drum cover 81 is formed, for example, with a resin material into a substantially cylindrical shape with a lid that opens downward in the figure, and is fixed to the upper side of the motor housing 41 in the figure, and rotatably accommodates a drum 83 as a pulley. That is, the drum 83 is rotatably supported by a support shaft 86 disposed coaxially with the worm wheel 45. One end of the support shaft 86 is inserted and pivotally supported by a bearing 87a fitted in a boss-like mounting hole 82a formed in the locking housing 82 (the bottom wall portion of the accommodating portion 43a), and the other end is a drum. It is inserted and pivotally supported by a bearing 87 b fitted to the cover wall portion of the cover 81. As described above, the drum 83 is rotatable in the drum cover 81. The support shaft 86 is inserted and supported by the worm wheel 45 between the motor housing 41 and the drum 83.

  The drum 83 is formed in a substantially cylindrical shape with a lid that opens to the lower side in the figure, and has a first internal gear 83a formed on the inner peripheral portion to form a drum-side accommodation space Sd1. A first carrier 89 that constitutes a planetary gear mechanism together with the first sun gear portion 45b is accommodated in the drum-side accommodation space Sd1. The first sun gear portion 45b, the first internal gear 83a, and the first carrier 89 constitute a first clutch C11.

  The first carrier 89 has a substantially annular first holding plate 89a into which the first sun gear portion 45b is loosely inserted. The first holding plate 89a extends outward in the radial direction from the opening end surface of the drum 83, and has a large wheel gear 89b formed on the outer peripheral portion. The first carrier 89 has three first planetary gears 89c that are rotatably supported at the tip of the first holding plate 89a. The first planetary gears 89 c are prevented from coming off in the axial direction between the first planetary gear 89 c and the drum 83. When the first carrier 89 is inserted into the drum 83, the three first planetary gears 89c mesh with the first internal gear 83a, and when the first sun gear portion 45b is inserted, the first sun gear portion 45b has three first gears. One planetary gear 89c meshes.

  As shown in FIG. 10, the drum cover 81 houses the first clutch C <b> 11 in addition to the drum 83. The drum cover 81 is formed with a guide hole 81a that opens in the radial direction so as to include the position in the axial direction of the large wheel gear 89b. A guide block 90 is fixed to the drum cover 81 (or the motor housing 41) so as to face the radial direction of the guide hole 81a. The guide block 90 is formed with a first guide groove 90a that opens in the radial direction of the drum cover 81 at the position of the guide hole 81a. A first carrier fixing block 91 is movably mounted in the first guide groove 90a.

  When the first carrier fixing block 91 moves along the first guide groove 90 a in one direction approaching the first carrier 89, the first carrier fixing block 91 engages with the large wheel gear 89 b to make the first carrier 89 non-rotatable. At this time, the first sun gear portion 45b, the first internal gear 83a, and the first carrier 89 serve as an input shaft, an output shaft, and a fixed shaft of the planetary gear mechanism, respectively, and the rotation of the first sun gear portion 45b (worm wheel 45) is performed. It can be transmitted to the first internal gear 83a (drum 83). This state is referred to as a connected state of the first clutch C11.

  On the other hand, the first carrier fixing block 91 can rotate the first carrier 89 by releasing the engagement with the large wheel gear 89b when moving in the other direction away from the first carrier 89 in the first guide groove 90a. To. At this time, the rotation of the first sun gear portion 45 b (worm wheel 45) cannot be transmitted to the first carrier 89. This state is referred to as a disconnected state of the first clutch C11.

  The first carrier fixing block 91 is connected to the switching actuator 54 according to the first embodiment, and is selectively driven to move in one direction and the other direction. Further, the second clutch C2 (the second sun gear portion 45c, the second ring gear 57, and the second carrier 58) is accommodated in the gear-side accommodation space Sg, as in the first embodiment. However, the second carrier 58 (second holding plate 58a) is coupled to the support shaft 86 so as to rotate integrally. As described above, the second clutch C2 is connected or disconnected as the second switching lever 62 rotates. Further, the output lever 37 is connected to the tip of the support shaft 86 penetrating the locking housing 82 (the bottom wall portion of the accommodating portion 43a) so as to rotate integrally therewith.

As described above in detail, according to the present embodiment, in addition to the effects (1) to (3) and (10) to (17) in the first embodiment, the following effects can be obtained. Become.
(1) In the present embodiment, the first clutch C11 and the second clutch C2 are supported by a common support shaft 86 inserted through them, so that the accuracy of both axes of the first clutch C11 and the second clutch C2 is improved. Can be further improved. The worm wheel 45 is also supported by the support shaft 86 inserted therethrough, whereby the radial load on the worm wheel 45 can be more firmly supported by the support shaft 86. Shaking or misalignment in the direction can be suppressed. And the precision of the axis line of the worm wheel 45 can be improved more.

  (2) In the present embodiment, the first clutch C11, the second clutch C2, the worm wheel 45, the drum 83, and the output lever 37 are supported by a common support shaft 86 inserted therethrough, for example, in one direction. It can be assembled by stacking those parts in order.

  (3) In this embodiment, the output lever 37 related to the release / closer operation can be rotated with the sun gear input / carrier output having the largest reduction ratio. For example, when the slide door 20 is retracted to the fully closed state, the rotation of the output lever 37 requiring a large torque can be handled with the maximum reduction ratio.

  (4) Since the operation range (rotation range) and operation time of the output lever 37 related to the release / closer operation are very short, the support shaft 86 that rotates integrally with the output lever 37 can be used in substantially the same manner as the fixed shaft. In addition, the support structure of the support shaft 86 can be further simplified. There is a possibility that a highly durable and costly bearing structure such as a bearing (rolling bearing) may not be employed. In addition, wear due to rotation of the support shaft 86 itself can be suppressed, and wear of the support shaft 86 can be localized.

In addition, you may change the said embodiment as follows.
As shown in FIG. 12, a second gear 102 that constitutes a so-called parallel shaft gear may be employed as the transmission gear together with the first gear 101 coupled to rotate integrally with the rotating shaft of the motor 22. . The first gear 101 and the second gear 102 are spur gears or helical gears that mesh with each other. Accordingly, when the motor 22 rotates, the rotation is transmitted to the second gear 102 via the first gear 101. Also in this case, the first clutches C1 and C11 are accommodated in the drum-side accommodation spaces Sd and Sd1 of the drums 23 and 83, and the rotation of the second gear 102 is performed via the first clutches C1 and C11. Can be communicated to. On the other hand, the second gear 102 is formed in a substantially cylindrical shape with a lid in accordance with the worm wheel 45 (worm wheel portion 45a) to form a gear-side accommodation space Sg1. The second clutch C12 is accommodated in the gear-side accommodation space Sg1, and the rotation of the second gear 102 can be transmitted to the output lever 37 via the second clutch C12.

  In the second embodiment, the connection state and disconnection state of the first clutch C11 may be switched by an appropriate carrier fixing block that moves in the radial direction of the first carrier 89 with a circular motion. The carrier fixing block may be moved electrically by a switching actuator or may be manually operated.

  In the second embodiment, the connection state and disconnection state of the first clutch C11 may be switched by an appropriate carrier fixing block that moves substantially parallel to the axial direction of the first carrier 89. In this case, the movement of the carrier fixing block may be a linear movement or a circular movement. The carrier fixing block may be moved electrically by a switching actuator or may be manually operated.

In each of the above embodiments, the switching actuator may be omitted and the connection state and disconnection state of the first clutch may be switched manually.
In each of the above embodiments, the connection state and disconnection state of the second clutch may be switched by a dedicated switching actuator as in the first clutch.

  In each of the above embodiments, the second internal gear and the second carrier of the second clutch may be an output shaft and a fixed shaft of the planetary gear mechanism, respectively. In this case, switching between the connected state and the disconnected state of the second clutch may be performed by an appropriate carrier fixing block that moves in the radial direction of the second carrier, or moves substantially parallel to the axial direction of the second carrier. An appropriate carrier fixing block may be used. Further, the movement of the carrier fixing block may be a linear movement or a circular movement. Furthermore, the movement of the carrier fixing block may be performed electrically by a switching actuator, or may be performed manually.

  In each of the embodiments, the first sun gear portion 45b and the second sun gear portion 45c may be set to have the same diameter, or the diameter of the second sun gear portion 45c is larger than the diameter of the first sun gear portion 45b. May be set larger.

  In each of the above embodiments, the first sun gear portion may be a first sun gear that is separate from the worm wheel portion. In this case, an appropriate connecting structure for rotating the first sun gear part integrally with the worm wheel part may be provided.

  In each of the above embodiments, the first sun gear portion may be a first sun gear that can rotate independently of the worm wheel portion. In this case, the first sun gear, the first internal gear, and the first carrier may be arbitrarily employed for the input shaft, the output shaft, and the fixed shaft of the planetary gear mechanism as long as they do not overlap each other.

  In each of the embodiments, the second sun gear portion may be a second sun gear that is separate from the worm wheel portion. In this case, an appropriate connection structure for rotating the second sun gear part integrally with the worm wheel part may be provided.

  In each of the above embodiments, the second sun gear portion may be a second sun gear that can rotate independently of the worm wheel portion. In this case, the second sun gear, the second internal gear, and the second carrier may be arbitrarily adopted as the input shaft, the output shaft, and the fixed shaft of the planetary gear mechanism as long as they do not overlap each other.

  In each of the above embodiments, the first clutch or the second clutch may be, for example, a friction type or tooth type electromagnetic clutch. Alternatively, the first clutch or the second clutch may be a so-called circumferential friction type (cone type, drum type) clutch.

In each of the above embodiments, two cables of the first cable 24 and the second cable 25 are used as the rope member, but one cable may be used.
-You may fix the drive member 21 to the vehicle body 10 side. For example, when the drive member 21 is mounted on the quarter panel 10b, it is more preferable to connect the tensioners 28 and 29 to the drive member 21 side. Moreover, when mounting the drive member 21 in the step used as the step of the door opening 10a, it is more preferable to employ a belt pulley as a pulley and a belt as a rope member.

Next, the technical idea that can be grasped from the above embodiment and other examples will be described below.
(A) In the vehicle door opening and closing device,
A vehicle door opening and closing device having one support shaft supported at both ends by a support member and supporting the transmission gear, the pulley, the output member, the first clutch, and the second clutch.

  According to this configuration, the first clutch and the second clutch are supported by the common support shaft together with the transmission gear, the pulley, and the output member, so that the first clutch and the second clutch The accuracy of both axes can be further improved.

  A1 ... through hole, C1, C11 ... first clutch, C2, C12 ... second clutch, S1 ... first accommodation space, S2 ... second accommodation space, 20 ... slide door (vehicle door), 22 ... motor, 23, 83 ... Drum (pulley), 24 ... First cable (rope member), 25 ... Second cable (rope member), 32 ... Front lock (door lock), 33 ... Rear lock (door lock), 34 ... Full open lock ( Door lock), 37 ... output lever (output member), 41 ... motor housing, 42, 81 ... drum cover (first housing), 43, 82 ... locking housing (second housing), 45 ... worm wheel, 45a ... worm Wheel portion (transmission gear), 45b ... first sun gear portion (sun gear), 45c ... second sun gear portion (sun gear), 46 ... first support shaft, 56 ... first The support shaft, 86 ... support shaft.

Claims (6)

A transmission gear driven to rotate by a motor;
A pulley that is arranged coaxially with the transmission gear and that opens and closes the vehicle door by moving the rope member with rotation;
An output member that is arranged coaxially with the transmission gear and causes the door lock to be held by the vehicle door as it rotates, or the door lock to be released from being held by the vehicle door;
A first clutch which is accommodated in the pulley coaxially with the transmission gear and which connects and disconnects rotation transmission between the transmission gear and the pulley;
A vehicle door opening and closing device comprising: a second clutch that is coaxially accommodated in the transmission gear and accommodated in the transmission gear, and that connects and disconnects rotation transmission between the transmission gear and the output member. The vehicle door opening and closing device according to claim 1,
The first clutch and the second clutch are both vehicle door opening and closing devices configured by a planetary gear mechanism. The vehicle door opening and closing device according to claim 2,
A vehicle door opening and closing device in which a sun gear of both the planetary gear mechanisms is integrally formed on the transmission gear. The vehicle door opening and closing device according to claim 3,
A motor housing for supporting the motor;
A first housing that forms a first housing space for housing the pulley and the first clutch together with the motor housing;
A second housing that forms a second housing space for housing the transmission gear and the second clutch together with the motor housing;
The motor housing has a through hole that communicates the first accommodation space and the second accommodation space;
The vehicle door opening and closing device, wherein the through hole is set larger than a diameter of the sun gear of the first clutch. In the vehicle door opening and closing device according to claim 3 or 4,
The vehicle door opening and closing device, wherein the transmission gear is formed of a resin material, and the sun gears are set to have different diameters. In the vehicle door opening and closing device according to any one of claims 2 to 5,
A first support shaft that supports the pulley and the first clutch together with the transmission gear;
A vehicle door opening and closing device having a second support shaft independent of the first support shaft that supports the output member and the second clutch together with the transmission gear.