JP2022071457A - Holding device for vehicle door - Google Patents

Abstract

To provide a holding device for vehicle door which can simplify a structure of a clutch mechanism.SOLUTION: A holding device 10 for vehicle door comprises: a first gear part 22 as a gear which has an engagement tooth 22a on the outer periphery and is supported in a rotatable manner in a peripheral direction D; a ratchet 41 as a lock member which is provided in a rotatable manner between a lock position Q1 engaged with the engagement tooth 22a of the first gear part 22 with a rotation shaft part 41a as the center and an unlock position Q2 releasing the engagement with the engagement tooth 22a; and a clutch mechanism 44 which adjusts the load transmission between the first gear part 22 and the ratchet 41. The clutch mechanism 44 comprises: a guide part 45 which guides the ratchet 41 in a front-rear direction Y being the slide direction between the lock position Q1 and the overload release position released from the engagement tooth 22a; and a spring member 46 as an elastic member which elastically biases the rotation shaft part 41a in the front-rear direction Y.SELECTED DRAWING: Figure 2

Description

The present invention relates to a vehicle door holding device for holding a vehicle door.

Conventionally, in a vehicle such as a minivan, a situation may occur in which sufficient space cannot be secured to fully open the back door behind the vehicle, or a situation in which the user cannot easily reach the back door in the fully opened position. Therefore, in order to deal with such a situation, a technique is desired in which the user can hold the back door at an arbitrary intermediate position between the fully open position and the fully closed position.

The following Patent Document 1 discloses an opening degree holding device for a back door of an automobile. This holding device generally includes a rotating drum for winding the cable, a cable having one end locked to the rotating drum and the other end locked to the back door, and a cable unwinding direction (back door) of the rotating drum. It is equipped with a rotation control mechanism that switches between a one-way rotation state that restrains rotation only in the opening direction of the) and a restraint release state that allows rotation in both directions (opening direction and closing direction of the back door) of the rotating drum.

The rotation control mechanism consists of a ratchet wheel, which is a gear that has multiple engaging teeth on the outer circumference and rotates integrally with the drum, a ratchet claw, which is a lock member that can rotate around a pin that is a rotation axis, and a ratchet claw. It has a spring that elastically urges it. The rotation of the ratchet wheel is locked by the ratchet claws moving in a direction approaching the engaging teeth by the elastic urging force of the spring and engaging with the engaging teeth. Further, the ratchet claw moves in a direction away from the engaging tooth by the elastic urging force of the spring, and the meshing with the engaging tooth is released, so that the rotation lock is released.

Japanese Unexamined Patent Publication No. 2011-46280

By the way, in this kind of holding device provided in a vehicle, when a gear such as a ratchet wheel is locked by a lock member such as a ratchet claw, an overload state occurs in which the gear receives a large load in the rotational direction from the door side. Is assumed. Therefore, it is preferable to enable the lock member to unlock the gear when such an overload state occurs.

In the case of a structure in which the lock member simply rotates around the rotation shaft as in the above rotation control mechanism, the lock member is rotated about the rotation shaft by the load received from the engaging teeth from the engaging teeth. It can be detached while sliding. At this time, in order to ensure that the lock member is disengaged from the engaging tooth of the gear, it is necessary to precisely design the meshing shape of each of the locking member and the engaging tooth.

Therefore, as another means, a plurality of plungers configured to be pressed against the gear in a state where the pressing member made of a ball or a pin is elastically urged by a spring is used for the fixing member that can rotate relative to the gear. Can be done. Such a plunger type clutch mechanism prevents the gear from rotating by the pressing load of the pressing member when the gear receives a normal load in the rotational direction, while presses when the gear receives an overload load in the rotational direction. The member moves to allow the push gear to rotate. However, the plunger type clutch mechanism is disadvantageous in that the structure is complicated because a plurality of plungers are used and it is difficult to reassemble the plunger.

The present invention has been made in view of the above problems, and an object of the present invention is to provide a holding device for a vehicle door that can simplify the structure of a clutch mechanism.

One aspect of the present invention is
A holding device for vehicle doors
A gear that has engaging teeth on the outer circumference and is rotatably supported in the circumferential direction.
A lock member rotatably provided between a lock position that engages with the engaging tooth of the gear and an unlocking position that disengages the engaging tooth with the rotation shaft portion as the center.
A clutch mechanism that adjusts the load transmission between the gear and the lock member,
Equipped with
The clutch mechanism elastically urges the guide portion that guides the lock member between the lock position and the overload release position disengaged from the engaging teeth in the slide direction, and the rotation shaft portion in the slide direction. With elastic members,
When the lock member receives a normal load in the rotational direction of the gear from the engaging teeth while the lock member is in the lock position, the clutch mechanism locks the lock member in the lock position according to the elastic urging force of the elastic member. When the locking member is in the locked position and receives an overload load from the engaging teeth in the rotational direction that exceeds the normal load, the overload load is applied to the rotating shaft portion. A holding device for a vehicle door, which is configured to move against the elastic urging force of the elastic member and convert the lock member into a force for sliding the lock member to the overload release position.
It is in.

In the above-mentioned vehicle door holding device, the clutch mechanism for adjusting the load transmission between the gear and the lock member includes a guide portion for guiding the lock member in the sliding direction between the lock position and the overload release position, and a lock. An elastic member that elastically biases the rotation shaft portion of the member in the slide direction is provided. According to this clutch mechanism, when a normal load in the rotational direction is applied from the engaging teeth of the gear while the lock member is in the lock position, the lock member can be held in the lock position according to the elastic urging force of the elastic member. can. Further, when the lock member is in the locked position and receives an overload load in the rotational direction from the engaging teeth of the gear, the rotation shaft portion of the lock member is moved against the elastic urging force of the elastic member to lock. The member can be slid to the overload release position.

Such a clutch mechanism needs to precisely design the meshing shape of the lock member and the engaging tooth of the gear by using a structure that slides the lock member from the lock position to the overload release position in an overload state. It has the advantage that the structure is simpler than that of the plunger type clutch mechanism.

As described above, according to the above aspect, it is possible to provide a vehicle door holding device that can simplify the structure of the clutch mechanism.

It is a side view which looked at the rear part of the vehicle body from the side, and is the figure which shows the state when the back door which concerns on Embodiment 1 is in an arbitrary intermediate position. The cross-sectional view which shows typically the initial state of the holding device for a vehicle door of Embodiment 1. FIG. FIG. 2 is a cross-sectional view schematically showing a door opening operation state of the vehicle door holding device of FIG. FIG. 2 is a cross-sectional view schematically showing a door closing operation state of the vehicle door holding device of FIG. FIG. 2 is a cross-sectional view schematically showing a door holding state of the vehicle door holding device of FIG. A partially enlarged view of FIG. FIG. 6 is a diagram showing a state when the ratchet slides from the lock position to the overload release position in FIG. FIG. 6 is a diagram showing a state when the clutch load is adjusted in the direction of weakening by the adjusting portion. FIG. 6 is a diagram showing a state when the clutch load is adjusted in the direction of increasing the clutch load by the adjusting portion. FIG. 5 is a cross-sectional view of the vehicle door holding device of the second embodiment corresponding to FIG.

Preferred embodiments of the above embodiments will be described below.

In the vehicle door holding device, the clutch mechanism preferably includes an adjusting portion capable of adjusting the clutch load applied to the rotating shaft portion by the elastic member.

According to this holding device, by providing the adjusting unit in the clutch mechanism, the user can operate the adjusting unit to appropriately adjust the clutch load. Therefore, after assembling the holding device, it is possible to correct the variation in the clutch load and adjust the clutch load to a desired state.

In the vehicle door holding device, the elastic member is a spring member in which one end of the expansion / contraction direction is connected to the rotation shaft portion with the slide direction as the expansion / contraction direction, and the adjustment portion is the spring member. It has a screw member connected to the other end portion in the expansion / contraction direction, and is configured so that the position of the other end portion of the spring member is adjusted in the expansion / contraction direction by a screw turning operation of the screw member. Is preferable.

According to this holding device, when the other end of the spring member is adjusted in the direction away from one end by the screw turning operation of the screw member in the adjusting portion, the spring member is stretched more than before the adjustment, and the clutch load is weakened. .. Further, when the other end of the spring member is adjusted in a direction closer to one end by the screw turning operation of the screw member, the spring member contracts more than before the adjustment, and the clutch load increases. Therefore, the user can easily adjust the clutch load by turning the screw member.

The vehicle door holding device includes a case for accommodating the gear and the lock member, and the adjusting portion is configured so that the screw member can be screwed outside the case. Is preferable.

According to this holding device, the user can easily adjust the clutch load by screwing the screw member of the adjusting portion outside the case without opening the case.

Hereinafter, a specific embodiment of the vehicle door holding device attached between the vehicle body and the back door at the rear of the vehicle will be described with reference to the drawings.

In the drawings for explaining this embodiment, unless otherwise specified, the front of the vehicle is indicated by an arrow FR, and the upper portion of the vehicle is indicated by an arrow UP.

Regarding the vehicle door holding device, in the vehicle-mounted state, the left-right direction corresponding to the vehicle width direction is indicated by an arrow X, the front-rear direction corresponding to the vehicle length direction is indicated by an arrow Y, and the up-down direction corresponding to the vehicle height direction is indicated by an arrow. It is indicated by Z, and the circumferential direction centered on the left-right direction X is indicated by an arrow D. At this time, one of the front-back directions Y is the first slide direction Y1, and the opposite direction is the second slide direction ZZ. Further, one of the vertical directions Z is the first slide direction Z1, and the opposite direction is the second slide direction Z2. Further, one direction of the circumferential direction D is referred to as the direction D1 in the first rotation, and the opposite direction is referred to as the second rotation direction D2.

(Embodiment 1)
As shown in FIG. 1, a back door 6 as a vehicle door and a vehicle door holding device (hereinafter, also simply referred to as “holding device”) 10 of the first embodiment are attached to the rear portion 2 of the vehicle body 1. It is provided.

The back door 6 is a flip-up type vehicle door that can rotate from the fully closed position P1 to the fully open position P2 via the intermediate position (also referred to as “half open position”) P3 via the rotation shaft 7. .. By the rotational operation of the back door 6, the luggage room 4 behind the rearmost row seat 3 can be opened and closed. The rear of the luggage room 4 is partitioned by a back door 6, and both sides thereof are partitioned by left and right pillar trims 5.

Each of the right end portion and the left end portion of the back door 6 is connected to the rear portion 2 of the vehicle body 1 by a known hydraulic damper stay 8. Therefore, the operation of opening and closing the back door 6 by the user is assisted by the damper stay 8. For example, when the user releases his hand from the back door 6 at the intermediate position P3, the damper stay 8 can prevent the back door 6 from moving toward the fully closed position P1 by its own weight. Further, according to the damper stay 8, the force required for the user to flip the back door 6 from the intermediate position P3 toward the fully open position P2 can be reduced.

The holding device 10 has a function of holding the back door 6 via the cable member 25 at an arbitrary intermediate position P3 between the fully closed position P1 and the fully open position P2. The cable member 25 is configured as a wire rope in which a plurality of metal strands are combined. If necessary, the wire rope can be changed to a member such as a belt or a tape measure.

As shown in FIG. 2, the holding device 10 is provided on the vehicle body 1. The holding device 10 has a case 11 fixed to the vehicle body 1, and the case 11 has a plurality of configurations including a rotating drum 20, a torque transmission unit 30, a lock unit 40, and a trigger mechanism unit 50. The element is housed.

The rotating drum 20 is a rotating body rotatably supported in the circumferential direction D around a shaft portion 20a provided on the case 11 so as to extend in the left-right direction X. The rotating drum 20 is connected to the back door 6 by a cable member 25 capable of winding and unwinding. The cable member 25 is unwound from the rotary drum 20 to the back door 6 side through the opening 12 provided in the case 11. The rotary drum 20 is configured as a gear having a reel portion 21, which is coaxial and integrated, a first gear portion 22, and a second gear portion 23.

The reel portion 21 has a winding surface for the cable member 25 on the outer periphery in the circumferential direction D, and the rotating drum 20 rotates around the shaft portion 20a, so that the cable member 25 can be wound and unwound. It is the part that was supposed to be. Regarding the reel portion 21, the first rotation direction D1 is the winding direction of the cable member 25, and the second rotation direction D2 is the winding direction of the cable member 25. The reel portion 21 is always elastically urged in the second rotation direction D2 by the spring member 24.

The first gear portion 22 is a ratchet gear provided corresponding to the ratchet 41 of the lock portion 40, and the first gear portion 22 has a plurality of engaging teeth 22a over the entire outer periphery of the circumferential direction D. Is provided. The plurality of engaging teeth 22a extend in a direction inclined with respect to the radial virtual line. In FIG. 2, for convenience, the description of some of the engaging teeth 22a is omitted.

The second gear portion 23 is provided with a plurality of engaging teeth 23a over the entire outer circumference of the second gear portion 23 in the circumferential direction D. In FIG. 2, for convenience, the description of some of the engaging teeth 23a is omitted. In this embodiment, the case where the second gear portion 23 has a smaller diameter than the first gear portion 22 is illustrated.

The torque transmission unit 30 has an idle gear 31, a drive gear 32, and a torque limiter 35, and has a function of transmitting the torque during rotation of the rotary drum 20 to the trigger mechanism unit 50 via the torque limiter 35. ..

The idle gear 31 is an intermediate gear interposed between the rotary drum 20 and the drive gear 32. The idle gear 31 is a rotating body rotatably supported in the circumferential direction D around a shaft portion 31a provided on the case 11 so as to extend in parallel with the shaft portion 20a of the rotating drum 20. The idle gear 31 is provided with a plurality of engaging teeth 31b over the entire outer circumference in the circumferential direction D. In FIG. 2, for convenience, the description of some of the engaging teeth 31b is omitted. The idle gear 31 meshes with the plurality of engaging teeth 23a of the second gear portion 23 of the rotary drum 20 at the plurality of engaging teeth 31b. Therefore, the idle gear 31 is configured to rotate in conjunction with the rotating drum 20 when the rotating drum 20 rotates.

The drive gear 32 is a gear that drives the movable member 51 described later by rotating in conjunction with the rotary drum 20 and the idle gear 31. The drive gear 32 is a rotating body rotatably supported in the circumferential direction D around a shaft portion 32a provided on the case 11 so as to extend in parallel with the shaft portion 31a of the idle gear 31. The drive gear 32 has a first gear portion 33 and a second gear portion 34, both of which are coaxial.

The first gear portion 33 is provided with a plurality of engaging teeth 33a over the entire outer circumference of the first gear portion 33 in the circumferential direction D. In FIG. 2, for convenience, the description of some of the engaging teeth 33a is omitted.

The second gear portion 34 is provided with a plurality of engaging teeth 34a over the entire outer circumference in the circumferential direction D. The second gear portion 34 meshes with the plurality of engaging teeth 31b of the idle gear 31 at the plurality of engaging teeth 34a. Therefore, the drive gear 32 is configured to rotate in conjunction with the idle gear 31 when the idle gear 31 rotates. In this embodiment, the case where the second gear portion 34 has a smaller diameter than the first gear portion 33 is illustrated.

The torque limiter 35 is provided between the first gear portion 33 and the second gear portion 34 of the drive gear 32. The torque limiter 35 has a function of cutting off the torque transmitted at the time of overload. Therefore, in the drive gear 32, when the torque acting on the circumferential direction D is lower than the reference value, the first gear portion 33 and the second gear portion 34 integrally rotate in the circumferential direction D, while acting on the circumferential direction D. When the torque exceeds the reference value, the first gear portion 33 and the second gear portion 34 are in a state of being relatively rotatable according to the function of the torque limiter 35.

The structure of the torque limiter 35 is not particularly limited, but as an example, a known structure having a rotor as a rotating body and a stator in which the rotor is accommodated so as to be rotatable via oil. A rotary oil damper can be adopted. For the specific structure of this oil damper, for example, the structure of the rotary oil damper disclosed in Japanese Patent Application Laid-Open No. 2001-234962 can be referred to.

Further, as a structure in place of the above-mentioned rotary oil damper, a structure in which a ball member interposed between the first gear portion 33 and the second gear portion 34 is disengaged when overloaded, or a structure in which an electromagnetic clutch is controlled to cause an overload. It is also possible to use a structure that separates the 1st gear portion 33 and the 2nd gear portion 34.

The lock portion 40 is set to either a locked state that locks the rotation of the rotating drum 20 or an unlocked state that allows the rotation of the rotating drum 20. The lock portion 40 has a ratchet 41 as a lock member and a support arm 43 connected to the ratchet 41.

The ratchet 41 has a locking claw 42, and is a lock position Q1 (position indicated by a two-dot chain line) with respect to the rotating drum 20 around a rotating shaft portion 41a provided on the case 11 so as to extend in the left-right direction X. It is configured to be rotatable from to the unlock position Q2 (the position indicated by the solid line). The lock position Q1 is a position where the ratchet 41 meshes with the engaging tooth 22a of the first gear portion 22 at the locking claw 42. The unlock position Q2 is a position where the ratchet 41 disengages the engaging tooth 22a of the first gear portion 22 at the locking claw 42.

The support arm 43 is connected to the ratchet 41 by engaging the connecting pin 43a provided at one end with the elongated hole 41b provided in the ratchet 41. At this time, the connecting pin 43a is configured so that the elongated hole 41b of the ratchet 41 can be slid in the longitudinal direction.

The support arm 43 is connected to a link arm 56 described later of the trigger mechanism unit 50 via a connecting pin 43b provided at the other end. Although not particularly shown, the support arm 43 is always elastically urged by a spring member (not shown) so as to move the ratchet 41 toward an unlocked position with respect to the rotating drum 20.

Therefore, when the elastic urging force received by the ratchet 41 from the spring member exceeds the load received from the trigger mechanism portion 50, the ratchet 41 is unlocked. On the other hand, when the load received by the ratchet 41 from the trigger mechanism portion 50 exceeds the elastic urging force received from the spring member, the ratchet 41 rotates around the rotating shaft portion 41a toward the rotating drum 20. When the locking claw 42 engages with the engaging teeth 22a of the rotating drum 20, the locking state is set.

The lock portion 40 is provided with a clutch mechanism 44 that adjusts the load transmission between the first gear portion 22, which is the gear of the rotary drum 20, and the ratchet 41. The clutch mechanism 44 has a guide portion 45, a spring member 46, and an adjusting portion 47.

The guide portion 45 has a function of guiding the ratchet 41 in the front-rear direction Y, which is the slide direction, between the lock position Q1 and the overload release position Q3 (see FIG. 7). The guide portion 45 is composed of a support piece 45a erected on the inner wall surface of the case 11, an elongated hole 45b formed in the case 11, and an elongated hole 41b of the ratchet 41.

Here, the overload release position Q3 is a position where the locking claw 42 of the ratchet 41 is separated from the engaging tooth 22a from the locking claw 42 by moving away from the engaging tooth 22a of the first gear portion 22. This overload release position Q3 is a slide position with respect to the lock position Q1 and is a position different from the unlock position Q2 which is the rotation position with respect to the lock position Q1.

The support piece 45a is configured to support the front end portion of the ratchet 41 from below when the ratchet 41 is in the lock position Q1. The elongated hole 45b is a guide hole extending in the front-rear direction Y, and the rotating shaft portion 41a of the ratchet 41 is inserted into the elongated hole 45b. The elongated hole 45b is configured to allow the rotating shaft portion 41a to slide in the front-rear direction Y, while preventing the rotating shaft portion 41a from moving in the vertical direction Z. While the elongated hole 41b is used for engaging the connecting pin 43a of the support arm 43, it also has a function of guiding the ratchet 41 in the front-rear direction Y. Therefore, the elongated hole 41b is formed so as to extend in the front-rear direction Y when the ratchet 41 is in the lock position Q1.

The spring member 46 is a tension spring that pulls the rotating shaft portion 41a of the ratchet 41 rearward. The spring member 46 is configured as an elastic member in which one end portion 46a in the expansion / contraction direction is connected to the rotation shaft portion 41a with the front-rear direction Y as the expansion / contraction direction. According to the spring member 46, since the rotation shaft portion 41a of the ratchet 41 is always elastically urged in the first slide direction Y1, a tensile load in the first slide direction Y1 is applied to the rotation shaft portion 41a. Ru.

It should be noted that any spring may be used as long as the rotation shaft portion 41a of the ratchet 41 can be elastically urged in the first slide direction Y1 at all times, and instead of the spring member 46, the rotation shaft portion 41a is compressed from the front. A spring can also be used.

The adjusting portion 47 is configured to be able to adjust the elastic urging force (clutch load) applied to the rotating shaft portion 41a of the ratchet 41 by the spring member 46. The adjusting portion 47 has a screw member 48 and a spring member 49 that elastically urges the screw member 48.

The screw member 48 is configured as a bolt member having a screw shaft portion 48a screwed to the vertical wall portion 13 provided in the case 11 and a head portion 48b provided at one end of the screw shaft portion 48a. .. In the screw member 48, the other end of the screw shaft portion 48a is connected to the other end portion 46b of the spring member 46.

The screw member 48 moves in the first slide direction Y1 with respect to the vertical wall portion 13 according to the elastic urging force of the spring member 49 by a one-way screw turning operation on the head 48b. Further, the screw member 48 moves in the second slide direction Y2 with respect to the vertical wall portion 13 against the elastic urging force of the spring member 49 by the screw turning operation in the reverse direction on the head 48b.

By the screw turning operation of the screw member 48, the position of the other end 46b of the spring member 46 is adjusted to the front-rear direction Y which is the expansion / contraction direction. Thereby, the elastic urging force applied from the spring member 46 to the rotating shaft portion 41a can be adjusted.

The head portion 48b of the screw member 48 is arranged so as to be exposed to the outside of the case 11. Therefore, the user can perform a screw turning operation of the screw member 48 outside the case 11.

The adjusting unit 47 having the above configuration may adopt a structure in which a nut member is appropriately combined with the screw member 48, if necessary.

The trigger mechanism unit 50 is for driving the lock unit 40. The trigger mechanism portion 50 includes a movable member 51, a heart cam mechanism 53, and two stoppers 58 and 59.

The movable member 51 has a rack portion 52 extending in the vertical direction Z, and is slidable between the first position Q1 (see FIG. 5) and the second position Q2 (see FIGS. 2 and 4). be. The rack portion 52 is provided with a plurality of rack teeth 52a along the vertical direction Z, which is the sliding direction, so as to mesh with the plurality of engaging teeth 33a provided in the first gear portion 33 of the drive gear 32. There is. As a result, the rotation of the drive gear 32 is converted into the movement of the movable member 51 in the vertical direction Z. At this time, the movable member 51 is configured to move between the first position Q1 and the second position Q2 in conjunction with the rotary drum 20 by the torque transmitted from the torque transmission unit 30 when the back door 6 is opened and closed. ing.

The two stoppers 58 and 59 have a function of stopping the movable member 51 at each of the first position Q1 and the second position Q2. Therefore, the movement of the movable member 51 in the vertical direction Z is blocked by the two stoppers 58 and 59 arranged on both sides of the rack portion 52 in the vertical direction Z.

Specifically, when the movable member 51 slides in the second slide direction Z2, the rack portion 52 stops at the first position Q1 where the rack portion 52 abuts on the stopper 58, and slides further in the second slide direction Z2. Is blocked. Further, when the movable member 51 slides in the first slide direction Z1, the rack portion 52 is stopped at the second position Q2 where the rack portion 52 abuts on the stopper 59, and further slide in the first slide direction Z1 is prevented. Slide.

The heart cam mechanism 53 has a heart cam-shaped cam groove 54, a cam pin 55 that engages with the cam groove 54, and two link arms 56 and 57. The two link arms 56 and 57 are for connecting the cam pin 55 of the heart cam mechanism 53 and the movable member 51, and the link arm 56 is provided with the cam pin 55. At this time, the movable member 51 is connected to the support arm 43 of the lock portion 40 via the two link arms 56 and 57.

The cam groove 54 includes a first cam region 54a, a second cam region 54b, a third cam region 54c, and a fourth cam region 54d on the groove path. The first cam region 54a and the third cam region 54c are defined as the highest region of the cam groove 54 in the vertical direction Z. The fourth cam region 54d is the lowest region of the cam groove 54 in the vertical direction Z. The second cam region 54b is a region of the cam groove 54 that is lower than the first cam region 54a and the third cam region 54c and is located higher than the fourth cam region 54d.

For a more specific structure and modification of the heart cam mechanism 53, for example, the structure of the heart cam mechanism disclosed in JP-A-2009-140037 can be referred to.

Further, another mechanism having the same function as the heart cam mechanism 53 can be adopted. As another mechanism, for example, a knock-type ballpoint pen structure can be adopted. In this structure, each time the knock rod repeats one-push operation in one direction, the replacement core alternately switches between the locked state and the unlocked state via the cam mechanism interposed between the knock rod and the replacement core. It has become. In contrast to this structure, the movable member 51 corresponds to the knock rod, the lock portion 40 corresponds to the replacement core, and the heart cam mechanism 53 corresponds to the cam mechanism.

The trigger mechanism portion 50 is locked by utilizing the movement in which the cam pin 55 of the heart cam mechanism 53 is guided along the cam groove 54 when the movable member 51 moves between the first position Q1 and the second position Q2. The unit 40 is configured to be set to either a locked state or an unlocked state.

At this time, the vertical Z sliding motion of the movable member 51 is converted into a circulation motion along the cam groove 54 of the cam pin 55, and further converted into a vertical Z sliding motion of the support arm 43 of the lock portion 40.

Further, the movable member 51 is in one direction (first slide direction Z1 in FIG. 2) between the first position Q1 and the second position Q2 during the closing operation at the intermediate position P3 (see FIG. 1) of the back door 6. The lock unit 40 is alternately switched between the locked state and the unlocked state each time the movement is repeated. That is, by repeating the movement corresponding to the one-push operation of the movable member 51, the lock portion 40 can be alternately switched between the locked state and the unlocked state.

On the other hand, the torque transmission unit 30 is configured to cut off the torque transmitted by the torque limiter 35 when the movable member 51 of the trigger mechanism unit 50 is stopped to release the interlocking between the movable member 51 and the rotary drum 20. There is.

Next, the operation of the holding device 10 will be described with reference to FIGS. 2 to 8.

(initial state)
The holding device 10 shown in FIG. 2 is for an initial state when the back door 6 is in the fully closed position P1 (see FIG. 1). At this time, in the trigger mechanism portion 50, the movable member 51 is in the second position Q2 where the rack portion 52 is in contact with the stopper 59, and the cam pin 55 of the heart cam mechanism 53 is in the first cam region 54a of the cam groove 54. .. At this time, the lock portion 40 is in the unlocked state.

Although not particularly shown, the holding device 10 is equipped with a canceller mechanism for preventing the lock portion 40 from being locked in the initial state. As an example of this canceller mechanism, when the back door 6 reaches the fully closed position P1, the movable body that moves in conjunction with the idle gear 31 or the movable body that moves by the actuator unlocks the lock portion 40. It is possible to adopt a structure that urges the user. As a result, when the user closes the back door 6 to the fully closed position P1 and then opens the back door 6 from the fully closed position P1, the canceller mechanism can prevent the opening operation from being blocked.

(Door open operation state)
The holding device 10 shown in FIG. 3 is for a door opening operation state when the user opens the back door 6 from the fully closed position P1 to the intermediate position P3 (see FIG. 1). At this time, in conjunction with the opening operation of the back door 6, the rotating drum 20 rotates in the first rotation direction D1 around the shaft portion 20a while unwinding the cable member 25. Further, in conjunction with this, the drive gear 32 rotates in the first rotation direction D1 around the shaft portion 32a.

In the trigger mechanism portion 50, the movable member 51 descends in the second slide direction Z2 toward the first position P1 as the drive gear 32 rotates, and the cam pin 55 of the heart cam mechanism 53 has a two-dot chain line in the cam groove 54. It is guided from the first cam region 54a shown by the above to the second cam region 54b shown by the solid line. When the cam pin 55 is in the second cam region 54b of the cam groove 54, the movable member 51 is in the stopped state in which the sliding operation in the second sliding direction Z2 is blocked, and the locked portion 40 is in the unlocked state.

At this time, when the user further opens the back door 6, the drive gear 32 tries to rotate in the first rotation direction D1 with respect to the movable member 51 in the stopped state and becomes an overload state. Therefore, the drive gear 32 to the movable member 51 The transmission of torque to is cut off by the torque limiter 35. As a result, the interlocking of the movable member 51 and the rotating drum 20 is released, so that the back door 6 can be opened to an arbitrary intermediate position P3.

(Door closing operation state)
The holding device 10 shown in FIG. 4 is for a door closing operation state in which the user temporarily closes the back door 6 from an arbitrary intermediate position P3. At this time, in conjunction with the closing operation of the back door 6, the rotating drum 20 rotates in the second rotation direction D2 around the shaft portion 20a while winding the cable member 25. Further, in conjunction with this, the drive gear 32 rotates in the second rotation direction D2 about the shaft portion 32a.

In the trigger mechanism portion 50, the movable member 51 rises in the first slide direction Z1 toward the second position P2 as the drive gear 32 rotates, and the cam pin 55 of the heart cam mechanism 53 has a two-dot chain line in the cam groove 54. It is guided from the second cam region 54b shown by the solid line to the third cam region 54c shown by the solid line. When the cam pin 55 is in the third cam region 54c of the cam groove 54, the movable member 51 is in a stopped state in which the slide operation in the first slide direction Z1 is blocked by the stopper 59, and the lock portion 40 is in the unlocked state. be.

At this time, when the user further closes the back door 6, the drive gear 32 tries to rotate in the second rotation direction D2 with respect to the movable member 51 in the stopped state and becomes an overload state. Therefore, the drive gear 32 to the movable member 51 The transmission of torque to is cut off by the torque limiter 35. As a result, the interlocking between the movable member 51 and the rotating drum 20 is released, so that the back door 6 can be closed.

(Door holding state)
The holding device 10 shown in FIG. 5 is for a door holding state in which the opening / closing operation of the back door 6 is locked by the user stopping the temporary closing operation of the back door 6. At this time, the back door 6 moves in the opening direction by the assisting force of the damper stay 8, so that the rotating drum 20 rotates in the first rotation direction D1 around the shaft portion 20a while unwinding the cable member 25. Further, in conjunction with this, the drive gear 32 rotates in the first rotation direction D1 around the shaft portion 32a.

In the trigger mechanism portion 50, the movable member 51 descends in the second slide direction Z2 toward the first position P1 as the drive gear 32 rotates, and the cam pin 55 of the heart cam mechanism 53 has a two-dot chain line in the cam groove 54. It is guided from the third cam region 54c shown by the solid line to the fourth cam region 54d shown by the solid line. When the cam pin 55 is in the fourth cam region 54d of the cam groove 54, the movable member 51 is in a stopped state in which the slide operation in the second slide direction Z2 is blocked by the stopper 58. Further, in the lock portion 40, the ratchet 41 rotates toward the rotary drum 20 around the rotary shaft portion 41a as the movable member 51 slides, and the locking claw 42 thereof engages with the rotary drum 20 side. By engaging with the tooth 22a, it becomes a locked state. As a result, the back door 6 can be held at an arbitrary intermediate position P3.

In the door holding state of FIG. 5, a closing operation from an arbitrary intermediate position P3 of the back door 6 toward the fully closed position P1 is permitted. At the time of this closing operation, in the trigger mechanism portion 50, the movable member 51 rises in the first slide direction Z1 toward the second position P2, and the cam pin 55 of the heart cam mechanism 53 moves the cam groove 54 into the fourth cam region 54d. It is guided from (see FIG. 5) to the first cam region 54a (see FIG. 2). Therefore, in this holding device 10, the locking claw 42 of the ratchet 41 of the lock portion 40 is switched to the unlocked state in which the engagement with the engaging tooth 22a on the rotating drum 20 side is released, and the back door 6 is in the fully closed position P1. Until, the same state as the initial state of FIG. 2 is maintained. Therefore, when the user closes the back door 6 to the fully closed position P1, the holding device 10 returns to the initial state shown in FIG.

On the other hand, when the closing operation of the back door 6 is stopped before reaching the fully closed position P1, the holding device 10 is in the same state as the door opening operation state of FIG. 3, and the lock portion 40 is unlocked. The state is maintained. In this way, the holding device 10 alternately switches between the door holding state of FIG. 5 and the door opening operation state of FIG. 3 each time the movable member 51 of the trigger mechanism portion 50 repeatedly moves in the first slide direction Z1. It has become like. As a result, the lock portion 40 alternately switches between the locked state and the unlocked state.

(Overload condition)
As shown in FIG. 6, in a state where the ratchet 41 is in the lock position Q1, the locking claw 42 of the ratchet 41 is caused by the torque of the first rotation direction D1 of the rotary drum 20 to cause the engaging teeth 22a of the first gear portion 22. Receives the load F in the first rotation direction D1 from. This load F is input from the back door 6 via the cable member 25. This load F is applied to the virtual circle centered on the shaft portion 20a passing through the contact point between the locking claw 42 of the ratchet 41 and the engaging tooth 22a of the first gear portion 22 at this contact point on the virtual circle. It is formed in the tangential direction.

Here, when the load F is the normal load F1, the rotating shaft portion 41a is held at the first position R1 according to the elastic urging force of the spring member 46 of the clutch mechanism 44. That is, the clutch load Fc due to the elastic urging force of the spring member 46 is set to exceed the component force Fa of the normal load F1. As a result, the ratchet 41 is held at the lock position Q1, so that the locked state of the rotating drum 20 by the ratchet 41 can be maintained. The component force Fb of the normal load F1 at this time is received by the support piece 45a.

As shown in FIG. 7, when the load F is an overload load F2 that exceeds the normal load F1, the clutch mechanism 44 applies the overload load F2 to the rotating shaft portion 41a of the ratchet 41 and the elasticity of the spring member 46. It is converted into a force that moves from the first position R1 to the second position R2 against the urging force. That is, the clutch load Fc due to the elastic urging force of the spring member 46 is set to be lower than the component force Fa of the overload load F2.

At this time, since the ratchet 41 is slidably guided in the front-rear direction Y between the lock position Q1 and the overload release position Q3 by the guide portion 25, the ratchet 41 is guided from the lock position Q1 by the component force Fa of the overload load F2. It slides in the second slide direction Y2 until the overload release position Q3.

In the state where the ratchet 41 is supported from below by the support piece 45a, the rotation shaft portion 41a of the ratchet 41 slides in the slotted hole 45b in the second slide direction Y2, and the connecting pin 43a of the support arm 43 is relative. By sliding in the slotted hole 41b of the ratchet 41 in the first slide direction Y1, the ratchet 41 can be slid in the second slide direction Y2 up to the second position R2. As a result, the locked state of the rotating drum 20 by the ratchet 41 can be temporarily released. The component force Fb of the overload load F2 at this time is received by the support piece 45a as in the case of the normal load F1.

After that, when the load F falls below the overload load F2, the rotation shaft portion 41a moves from the second position R2 to the first position R1 according to the elastic urging force of the spring member 46, and the ratchet 41 moves to the overload release position Q3. Return to the lock position Q1. As a result, the locked state of the rotating drum 20 by the ratchet 41 can be maintained again.

(Clutch load adjustment)
The user can adjust the clutch load Fc due to the elastic urging force of the spring member 46 by operating the screw member 48 of the adjusting portion 47.

For example, by a one-way screw turning operation of the head 48b of the screw member 48, the screw member 48 is moved in the first slide direction Y1 from the first position S1 shown in FIG. 6 to the second position S2 shown in FIG. Can be made to. As a result, the length of the spring member 46 is extended, so that the direction in which the clutch load Fc is weakened can be adjusted. If the clutch load Fc is set low, the required component strength can be reduced and the cost of the component can be reduced.

Further, the screw member 48 is moved in the second slide direction Y2 from the first position S1 shown in FIG. 6 to the third position S3 shown in FIG. 9 by the screw turning operation in the reverse direction of the head 48b of the screw member 48. Can be made to. As a result, the length of the spring member 46 is shortened, so that the direction in which the clutch load Fc is strengthened can be adjusted.

According to the above-mentioned first embodiment, the following effects can be obtained.

In the holding device 10, the clutch mechanism 44 for adjusting the load transmission between the first gear portion 22 of the rotary drum 20 and the ratchet 41 has the ratchet 41 between the lock position Q1 and the overload release position Q3. A guide portion 45 that guides the ratchet 41 in the front-rear direction Y and a spring member 46 that elastically biases the rotation shaft portion 41a of the ratchet 41 in the front-rear direction Y are provided.

According to this clutch mechanism 44, when the ratchet 41 is in the lock position Q1 and receives the normal load F1 in the first rotation direction D1 from the engaging teeth 22a of the first gear portion 22, the elastic urging force by the spring member 46. Therefore, the ratchet 41 can be held at the lock position Q1. Further, when the ratchet 41 receives the overload load F2 (> F1) in the first rotation direction D1 from the engaging teeth 22a of the first gear portion 22 while the ratchet 41 is in the lock position Q1, the rotation shaft portion 41a of the ratchet 41 Can be moved against the elastic urging force of the spring member 46 to slide the ratchet 41 to the overload release position Q3.

Such a clutch mechanism 44 uses a structure in which the ratchet 41 is slid from the lock position Q1 to the overload release position Q3 in an overloaded state, so that the engaging teeth of the locking claw 42 of the ratchet 41 and the first gear portion 22 are engaged. It is not necessary to precisely design the meshing shape of each of the 22a, and there is an advantage that the structure is simpler than that of the plunger type clutch mechanism.

Therefore, according to the first embodiment described above, it is possible to provide the holding device 10 that can simplify the structure of the clutch mechanism 44.

According to the holding device 10, the user can operate the adjusting unit 47 to appropriately adjust the clutch load Fc by providing the adjusting unit 47 in the clutch mechanism 44. Therefore, after assembling the holding device 10, it is possible to correct the variation in the clutch load Fc and adjust the clutch load Fc to a desired state. As a result, the man-hours for inspecting the product can be reduced.

According to the holding device 10, when the other end portion 46b of the spring member 46 is adjusted in the direction away from the one end portion 46a by the screw turning operation of the screw member 48 in the adjusting portion 47, the spring member 46 is adjusted from before the adjustment. The clutch load Fc weakens as it also stretches. Further, when the other end portion 46b of the spring member 46 is adjusted in the direction closer to the one end portion 46a by the screw turning operation of the screw member 48, the spring member 46 contracts more than before the adjustment, and the clutch load Fc is strengthened. Therefore, the user can easily adjust the clutch load Fc by the screw turning operation of the screw member 48.

According to the above-mentioned holding device 10, the user can easily adjust the clutch load Fc by screwing the screw member 48 of the adjusting portion 47 outside the case 11 without opening the case 11. become.

Next, other embodiments related to the above-described first embodiment will be described with reference to the drawings. In other embodiments, the same elements as those in the first embodiment are designated by the same reference numerals, and the description of the same elements will be omitted.

(Embodiment 2)
As shown in FIG. 10, the holding device 110 of the second embodiment is different from the holding device 10 of the first embodiment in that it does not include an element corresponding to the adjusting unit 47.

In the clutch mechanism 44 of the holding device 10, one end portion 46a of the spring member 46 is connected to the rotation shaft portion 41a, and the other end portion 16b is fixed to the vertical wall portion 13 of the case 11. The clutch load can be adjusted by the spring member 46 by replacing the spring member 46 itself.

Other configurations are the same as those in the first embodiment.

According to the holding device 110 of the second embodiment, the structure of the clutch mechanism 44 can be simplified as compared with the holding device 10 of the first embodiment.

Other than that, it has the same effect as that of the first embodiment.

The present invention is not limited to the above-described embodiment, and various applications and modifications can be considered as long as the object of the present invention is not deviated. For example, the following embodiments to which the above-described embodiments are applied can also be implemented.

In the above-described embodiment, the guide portion 45 that slideably guides the ratchet 41 between the lock position Q1 and the overload release position Q3 is provided by the support piece 45a of the case 11, the elongated hole 45b of the case 11, and the ratchet 41. Although the case of being configured by the long hole 41b of the above is illustrated, when the guide function can be achieved by the two long holes 45b and the long hole 41b, the support piece 45a is omitted and the two long holes 45b and the long hole are used. The guide portion 45 may be configured only with 41b.

In the above-described embodiment, the holding devices 10 and 110 for the back door have been exemplified, but the clutch mechanism 44, which is one of the features of the holding devices 10 and 110, may be applied to another door other than the back door. can. Another door is, for example, a type of door that can be opened by a user by pulling it toward you, and has a door check mechanism. The door check mechanism temporarily holds the door in the intermediate position between the fully closed position and the fully open position, while the door receives an overload load that exceeds the reference load due to contact with a person or the like at the intermediate position. It operates to release the temporary holding. Therefore, the structure of the clutch mechanism 44 of the present embodiment can be suitably used for the door check mechanism.

10,110 Vehicle door holding device (holding device)
11 Case 44 Clutch mechanism 22 First gear (gear)
22a Engagement tooth 41 Ratchet (lock member)
41a Rotating shaft part 41b Long hole (guide part)
44 Clutch mechanism 45 Guide part 45a Support piece (guide part)
45b long hole (guide part)
46 Spring member (elastic member)
46a One end 46b The other end 47 Adjustment part 48 Screw member D Circumferential direction (rotational direction)
F1 Normal load F2 Overload load Fc Clutch load Q1 Lock position Q2 Unlock position Q3 Overload release position Y Front-back direction (slide direction)

Claims (4)

A gear that has engaging teeth on the outer circumference and is rotatably supported in the circumferential direction.
A lock member rotatably provided between a lock position that engages with the engaging tooth of the gear and an unlocking position that disengages the engaging tooth with the rotation shaft portion as the center.
A clutch mechanism that adjusts the load transmission between the gear and the lock member,
Equipped with
The clutch mechanism elastically urges the guide portion that guides the lock member between the lock position and the overload release position disengaged from the engaging teeth in the slide direction, and the rotation shaft portion in the slide direction. With elastic members,
When the lock member receives a normal load in the rotational direction of the gear from the engaging teeth while the lock member is in the lock position, the clutch mechanism locks the lock member in the lock position according to the elastic urging force of the elastic member. When the locking member is in the locked position and receives an overload load from the engaging teeth in the rotational direction that exceeds the normal load, the overload load is applied to the rotating shaft portion. A holding device for a vehicle door, which is configured to move against an elastic urging force of an elastic member to convert the lock member into a force that slides the lock member to the overload release position. The vehicle door holding device according to claim 1, wherein the clutch mechanism includes an adjusting portion capable of adjusting a clutch load applied to the rotating shaft portion by the elastic member. The elastic member is a spring member in which one end in the expansion / contraction direction is connected to the rotation shaft portion with the slide direction as the expansion / contraction direction.
The adjusting portion has a screw member connected to the other end of the spring member in the expansion / contraction direction, and the position of the other end of the spring member is adjusted in the expansion / contraction direction by a screw turning operation of the screw member. The vehicle door holding device according to claim 2, which is configured to be the same. A case for accommodating the gear and the lock member is provided.
The vehicle door holding device according to claim 3, wherein the adjusting unit is configured so that a screw turning operation of the screw member can be performed outside the case.

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