JP2018141323A - Vehicle door check device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a vehicle door check device that improves operability at the time of door closing operation of a vehicle door and suppresses operation load at the time of opening operation of the vehicle door without increasing the number of components.SOLUTION: A vehicle door check device is featured in that a long hole 10 for moving a bracket pin 9d formed in a bracket 9 depending on a rotational position of a vehicle door D is formed at one end of a check lever 2, which allows a distance between the bracket pin and a rotation center T of the vehicle door D to change while the vehicle door D rotates between its fully opened position and fully closed position.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a vehicle door check device.

  2. Description of the Related Art Conventionally, a vehicle door check device including a check lever that is rotatably supported on the vehicle body side of a vehicle and a sliding portion that slides on the surface of the check lever according to the rotation of the vehicle door is known. . In such a vehicle door check device, the check lever is provided with a check pattern in which the thickness of the check lever changes along its longitudinal direction. Thus, the operation load on the vehicle door is increased or decreased as the sliding portion slides on the check pattern in accordance with the rotation of the vehicle door when the vehicle door is opened and closed.

  Patent Document 1 discloses that the change in the opening / closing force when the vehicle door is opened / closed is set to a desired mode by arbitrarily changing the setting of the check pattern recess of the check link arm.

JP 2013-87483 A

  However, there is a limit in product design to set a large inclination angle of the check pattern for improving the door closing performance as in Patent Document 1. Furthermore, if the inclination angle of the check pattern is set to a large value in pursuit of improved vehicle door closing performance, a large operating load is required when opening the vehicle door as a contradiction, which may make it difficult for the occupant to open the vehicle door. There is.

  This invention is made | formed in view of such a situation, The objective is to provide the vehicle door check apparatus which suppresses the operation load at the time of opening operation of a vehicle door.

  A vehicle door check device that solves the above problems is a door check device that is disposed between a vehicle body and a vehicle door that is rotatably attached to the vehicle body, and the thickness thereof changes in the longitudinal direction. A check lever having a check pattern, a one end portion of the check lever that is rotatably supported, a bracket that connects the check lever to the vehicle body, and a vehicle door that are pressed in the thickness direction of the check lever. A sliding portion, wherein the sliding portion slides on the surface of the check lever according to a change in the opening degree of the vehicle door, thereby increasing or decreasing the operation load of the vehicle door. And when the distance between the rotating shaft of the check lever and the rotating shaft of the vehicle door is the distance between the rotating shafts, the bracket has a distance between the rotating shafts according to the opening of the vehicle door. It can be changed to, for supporting the check lever.

  In the above configuration, the moment arm on the rotation axis of the check lever and the rotation axis of the vehicle door is shortened by changing the distance between the rotation axes. As a result, since the operation load of the vehicle door can be changed, the operation load during the opening operation of the vehicle door can be suppressed.

  In the vehicle door check device, the check pattern of the check lever is formed such that the operation load has a first peak load and a second peak load as the opening degree of the vehicle door increases. The opening between the opening of the vehicle door when the operating load becomes the first peak load and the opening of the vehicle door when the operating load becomes the second peak load is the intermediate opening When the opening of the vehicle door is less than the intermediate opening, the bracket is configured such that the distance between the rotating shafts is shorter than when the opening of the vehicle door is greater than or equal to the intermediate opening. In addition, it is preferable to support the check lever.

  In the above configuration, when the distance between the rotating shafts is long, the moment arm between the rotating shaft of the check lever and the rotating shaft of the vehicle door becomes long. As a result, the operation load on the vehicle door increases and the passenger feels heavy in the opening operation of the vehicle door. In the region of the first opening of the vehicle door where the operation load during the opening operation of the vehicle door increases, the opening operation of the vehicle door is easier by shortening the distance between the rotating shafts and shortening the moment arm. become. On the other hand, since the vehicle door is already open in the region of the second opening, it is assumed that a strong impact is applied in the opening direction of the vehicle door due to wind, vehicle inclination, or the like. In this region, when the moment arm between the rotating shaft of the check lever and the rotating shaft of the vehicle door is short, the effect of suppressing high impact in the opening direction with respect to the vehicle door is small. Therefore, at the second opening degree that requires a high operation load, the distance between the rotation axes is made longer than the region of the first opening degree of the vehicle door. Thereby, the moment arm of the rotating shaft of the check lever and the rotating shaft of the vehicle door can be lengthened, and the impact force acting on the vehicle door can be reduced.

  Further, in the vehicle door check device, the bracket is configured such that a bracket pin formed on the bracket is moved according to a rotation position of the vehicle door, and a longitudinal direction is a radial direction in the rotation of the vehicle door. Preferably, holes are formed.

  In the above configuration, the bracket pin of the bracket that fixes the check lever so as to be able to swing is rotated based on the intermediate opening by moving in a long hole formed in the bracket according to the rotation position of the vehicle door. The distance between axes can be changed.

  Further, in the above vehicle door check device, the check lever has a long hole in a direction intersecting with a longitudinal direction of the check lever that moves a bracket pin formed on the bracket according to a rotation position of the vehicle door. Is preferably formed.

  In the above configuration, the distance between the rotating shafts can be changed based on the intermediate opening by moving the bracket pin of the bracket through the long hole formed in the check lever in accordance with the rotational position of the vehicle door.

  Further, in the above vehicle door check device, a contact portion that contacts the bracket is formed at the one end of the check lever, and the bracket pin is attached to the bracket as the opening degree of the vehicle door increases. It is preferable that a pressing portion that presses the check lever is formed so that the distance between the rotation axes is increased by moving in the long hole.

  In the above configuration, the pressing portion of the bracket comes into contact with the contact portion of the check lever after the first peak load is generated, and further, the contact portion is pressed into the bracket, so that the bracket pin moves in the long hole of the bracket. It becomes possible.

1 is a side view of a vehicle door check device according to the present invention. It is a top view of the said vehicle door check apparatus attached to the vehicle door. In a vehicle provided with the vehicle door check device of a comparative example, it is a top view showing the state of the vehicle door check device according to the opening of the vehicle door. It is a top view which shows the state of the vehicle door check apparatus according to the opening degree of a vehicle door in a vehicle provided with the vehicle door check apparatus of this embodiment. It is a top view which shows the positional relationship of the bracket of a vehicle door check apparatus according to the opening degree of a vehicle door, and a check arm. It is a graph which shows the fluctuation | variation of the operation load according to the position of a moving body.

  Hereinafter, an embodiment embodying the present invention will be described in detail with reference to FIGS. The vehicle door check device according to the present embodiment is disposed between the vehicle and the vehicle door, and limits the opening degree of the vehicle door or adjusts the operation load when opening and closing the vehicle door. .

  As shown in FIG. 1, the vehicle door check device 1 includes a long check lever 2, a case 6 inserted through the check lever 2, and a bracket 9 that rotatably supports the check lever 2. The check lever 2 is provided with a check pattern 20 on the check surface 3 whose thickness varies along the longitudinal direction thereof. The check pattern 20 has an expanded portion 20a that is a thick portion and a concave portion 20b that is a thin portion. The check pattern 20 is formed so as to form a pair on both side surfaces in a direction orthogonal to the longitudinal direction of the check lever 2 (vertical direction in the present embodiment).

  As shown in FIG. 1, the check lever 2 has a communication hole 4 penetratingly formed at one end in the longitudinal direction. Further, the check lever 2 has a pressing portion that protrudes in a direction intersecting (orthogonal) with the longitudinal direction on one end side in the longitudinal direction. In the check lever 2, the surface on which the pressing portion is formed is a surface different from the surface on which the check pattern 20 is formed. In addition, the direction in which the pressing portion protrudes and the direction in which the communication hole 4 is formed to cross each other (orthogonal). In addition, the check lever 2 has a stopper portion 5 that is in contact with a case 6 that moves in the longitudinal direction of the check lever 2 on the other end side in the longitudinal direction.

  One end of the check lever 2 in the longitudinal direction is formed with a communication hole 4 penetrating in the vehicle vertical direction connected to the bracket 9 fastened to the vehicle body B. On the other hand, a stopper portion 5 for locking the case 6 when the vehicle door D is fully opened is formed at the other end in the longitudinal direction of the check lever 2.

  As shown in FIG. 1, the case 6 is fixed to the vehicle door D. The case 6 has an insertion hole (not shown) through which the check lever 2 is inserted. The insertion hole is formed larger than the check lever 2. Thus, the case 6 can move in the longitudinal direction of the check lever 2 with respect to the check lever 2.

  In addition, the case 6 includes a moving body 7a that moves on the check pattern 20 of the check lever 2, a sliding portion 7 that rotatably supports the moving body 7a, and the moving body 7a that passes through the sliding portion 7 as a check pattern. And an urging member 8 that urges toward 20. The moving body 7a, the sliding portion 7 and the urging member 8 are provided so as to form a pair on both sides of the check lever 2 where the check pattern 20 is formed. When the moving body 7a attached to the case 6 slides on the check pattern 20, the vehicle door D is opened and closed with appropriate moderation at each of the fully closed, half open, and fully open positions.

  Next, the sliding of the check lever 2 by the case 6 will be described. As shown in FIG. 1, when the case 6 slides on the check pattern 20 of the check lever 2, the urging member 8 accommodated in the case 6 moves the moving body 7 a in contact with the check pattern 20 to the check pattern 20. Press on. Thereby, the moving body 7a rolls on the check pattern 20 in a state where the check pattern 20 is pressed. When the moving body 7a rolls on the upward gradient of the check pattern 20, the moving body 7a compresses the urging member 8, and the moving body 7a is opposite to the moving direction of the moving body 7a. Force acts. For this reason, the operation load of the vehicle door D becomes large. In addition, the reaction force said here is the force by which the check pattern 20 pushes back the moving body 7a when the moving body 7a presses the check pattern 20. FIG.

  On the other hand, when the moving body 7a rolls on the downward gradient of the check pattern 20, the urging member 8 extends and a reaction force acts on the moving body in the moving direction of the moving body 7a. For this reason, the operation load of the vehicle door D becomes small.

  In this respect, when the moving body 7 a is located in the recess 20 b of the check pattern 20, the case 6 that accommodates the moving body 7 a is difficult to move with respect to the check pattern 20. For this reason, by setting the concave portion 20b of the check pattern 20 at the half-open position of the vehicle door D, the vehicle door D can be held at the half-open position.

  In the present embodiment, the moving body 7a moves by rolling on the check pattern 20. However, the moving body 7a may move by sliding on the check pattern 20. Good. Further, the urging member 8 may be a coil spring or an elastic body made of rubber or resin.

  As shown in FIG. 2, the bracket 9 includes a fixed plate 9a fixed to the vehicle B in a state of facing the vehicle B, a support plate 9b bent with respect to the fixed plate 9a, and a vehicle door D of the support plate 9b. And a pressing plate 9c provided at one end on the rotation center T side.

  The support plates 9b are provided so as to form a pair with an interval corresponding to the thickness of the check lever 2. The support plate 9b is formed with a long hole 10 for fixing the check lever 2 so as to be swingable. The bracket pin 9d is inserted into the long hole 10 of the support plate 9b and the communication hole 4 of the check lever 2 in a state where the check lever 2 is sandwiched between the support plates 9b forming a pair of the brackets 9b. 9, the check lever 2 is rotatably connected. When the bracket 9 and the check arm 2 are attached to the vehicle body B, the axial direction of the bracket pin 9d is the vertical direction, and the longitudinal direction of the communication hole 4 is the longitudinal direction of the vehicle.

  The pressing plate 9c is provided with an inclination at one end on the rotation center T side of the vehicle door D of the support plate 9b. This inclination angle is set so as to come into contact with the contact portion 2a of the check arm 2 when the vehicle door D is opened to the position where the first peak load of the operation load is generated. With the opening operation of the vehicle door D, the contact portion 2a of the check arm 2 and the pressing plate 9c of the bracket 9 come into contact with each other, and when the vehicle door D further rotates in the opening direction, the pressing plate 9c The contact part 2a is pressed. Thereby, the bracket pin 9d of the bracket 9 that fixes the check arm 2 so as to be able to swing is moved in the long hole 10 of the bracket 9 according to the rotation of the vehicle door D. Specifically, as shown in FIG. 5 (a), until the vehicle door D starts to open from the fully closed state and the operation load reaches the first peak, the pressing plate 9c of the bracket 9 is The bracket pin 9d is positioned at one end in the longitudinal direction of the long hole 10 without contacting the contact portion 2a of the check arm 2. As shown in FIG. 5B, when the vehicle door D is opened to the position where the first peak load of the operation load is generated, the pressing plate 9 c of the bracket 9 comes into contact with the contact portion 2 a of the check arm 2. Then, as shown in FIG. 5C, when the vehicle door D is further rotated in the opening direction, the pressing plate 9 c of the bracket 9 presses the contact portion 2 a of the check arm 2 into the bracket 9. As a result, the bracket pin 9d moves to the other end in the longitudinal direction of the long hole 10 of the bracket 9 at the position where the vehicle door D generates the first peak load.

  Next, the difference in operation between the vehicle door check device of the present embodiment and the vehicle door check device of the comparative example will be described. FIG. 3 is a schematic diagram showing the rotation locus of the check arm 2 with the bracket 9 ′ as the rotation axis when the vehicle door D is rotated in the comparative example. In the bracket 9 ′ in the comparative example, a hole 10 ′ corresponding to the long hole 10 of the bracket 9 of the present embodiment for fixing the bracket pin 9 d of the check lever 2 has a substantially circular shape. In this case, the vehicle door rotates without the bracket pin 9d moving in the hole 10 'of the bracket 9'. Accordingly, the distance between the bracket pin 9d serving as the rotation shaft of the check lever 2 and the rotation center T of the vehicle door D (distance L ′ between the rotation shafts) is the fully open position, the first peak load generation position, and the fully closed position of the vehicle door D. The distance is equal regardless of the position.

  On the other hand, as described above, the bracket pin 9d in the present embodiment moves to the other end of the long hole 10 of the bracket 9 after the first peak load is generated in the opening operation of the operation load of the vehicle door D. As a result, as shown in FIG. 4, the distance from the rotation center T of the vehicle door D (distance L between the rotation axes) is the rotation range of the vehicle door from the beginning of the opening of the vehicle door D until the first peak load occurs. In a certain region D1, the distance L between the rotation axes is short. That is, the opening degree between the opening degree of the vehicle door D (region D1) after the first peak load of the operating load is generated from the beginning of opening of the vehicle door D shown in FIG. 4 and the opening degree of the vehicle door D thereafter. When (region D2) is an intermediate opening, the distance L between the rotation axes is set to be shorter in the region D1 and in the region D2 than the intermediate opening.

  The difference between the distance L ′ between the rotation axes in this comparative example and the length L between the rotation axes in the present invention is the length of the moment arm in the comparison example shown in FIG. 3 and the moment arm in the present embodiment shown in FIG. Will be the difference. Specifically, when the vehicle door D is opened, a moment acts on the vehicle door D as the vehicle door D rotates, and this moment becomes an operation load in the opening / closing operation of the vehicle door D. In order to reduce the operation load of the vehicle door D, that is, the moment, it is necessary to shorten the moment arm. The moment arm is the length of the action line where the moment acts on the rotation center of the vehicle door D. In this case, from the rotation center T of the vehicle door D to the bracket pin 9d which is the rotation center of the vehicle door check device 1. Is equivalent to the moment arm.

  That is, since the distance L ′ between the rotation axes in the comparative example is always constant after the first peak load is generated due to the opening operation of the vehicle door D, the moment arm of the bracket pin 9d and the rotation center T of the vehicle door D is The length is the same. For this reason, the operation load accompanying the operation of the vehicle door D is only the fluctuation of the operation load due to the inclination of the check pattern 20 between the fully closed state and the fully open state. On the other hand, the distance L between the rotation axes in the present embodiment is shortened in the region D1 due to the movement of the bracket pin 9d in the long hole 10 in the region D1. Thereby, in the area | region D1, the moment arm in the rotation center T of the bracket pin 9d and the vehicle door D becomes short. As a result, compared with the vehicle door D in the comparative example, the operation load in the operation load region D1 of the vehicle door D is further reduced.

  The effect brought about by the reduction in the operation load of the vehicle door D in the region D1 will be described with reference to FIG. FIG. 6 is a graph showing the transition of the fluctuation of the operation load at each position of the moving body 7a sliding on the check pattern 20. As shown in FIG. The upper part of FIG. 6 represents the point F from each point A of the moving body 7a in the case 6 that slides on the check pattern 20 as the vehicle door D rotates and the biasing member 8 that presses it. The lower part of FIG. 6 is a graph in which changes in the operation load T at each point of the upper moving body 7a are represented by lines. The solid line represents the load fluctuation line Y of the operation load in the present invention, and the broken line represents the load fluctuation line Y 'of the operation load in the comparative example. The upper line in the lower graph represents the transition of the operation load variation when the vehicle door D is opened from the fully closed state to the fully opened position, and the lower line is the fully closed position from the fully opened position of the vehicle door D. It represents the transition of the operation load fluctuation when it is closed.

  As shown in FIG. 6, the transition of the operation load fluctuation when the vehicle door D is opened from the fully closed state (fully closed position) to the fully opened position, and the operation load when the vehicle door D is closed from the fully opened position to the fully closed position. There is a gap G in the change transition. The gap G is due to a difference in frictional force acting on the moving body 7a of the sliding portion 7 that slides on the check pattern 20 of the check lever 2. Specifically, the moving body 7a passes through the reverse path on the check pattern 20 of the check arm 2 from the fully closed position to the fully open position of the vehicle door D and from the fully open position to the fully closed position. The difference in the path on the check pattern 20 through which the moving body 7a passes from the fully closed position to the fully open position of the vehicle door D causes a difference in the frictional force acting on the moving body 7a. As a result, as shown in FIG. 6, the frictional force acting on the moving body 7a from the fully closed position to the fully open position of the vehicle door D exceeds the frictional force acting on the moving body 7a from the fully open position to the fully closed position, Accordingly, the operation load of the vehicle door D is also exceeded.

  A point A shown in FIG. 6 represents the position of the moving body 7a when the occupant starts to open the vehicle door D. At this point, since the moving body 7a is before reaching the expansion portion 20a of the check pattern 20 formed on the check pattern 20 of the check lever 2, the operation load G has a relatively low value. Further, at the point A, since the moving body 7a is located in the inflated portion 20a and the recessed portion 20b of the check pattern 20, the urging force against the moving body 7a by the urging member 8 is relatively weak. At the point B, the moving body 7a approaches the expansion portion 20a of the check pattern 20 on the first check pattern 20 set between the fully open position and the fully closed position of the vehicle door D, and the door starts to open. The point at which the first peak load, which is the peak of the first operating load, acts. Along with this, the urging of the urging member 8 to the moving body 7a also becomes stronger. Thereafter, the operating load is relatively low from point C to point D, that is, while the vehicle door D reaches the half-open position from the beginning of opening, and is lowest immediately before the vehicle door D approaches the half-open position (point D). It becomes the operation load. When the vehicle door D is further operated in the fully open direction from the half-open position (point D) of the vehicle door D (point E), the second peak load that becomes a large operation load is reached again. Thereafter, from point E to point F at which the vehicle door D reaches the fully open state, the operating load rapidly decreases, and then at the point F, the vehicle door D reaches the fully open state.

  On the other hand, when the vehicle door D is closed from the fully open state, that is, when the vehicle door D moves from the fully open position (point F) to the fully closed position (point A), the operation load applied is from the fully closed position to the fully open position. Draw a load fluctuation line that is almost parallel to the fluctuation of the operation load when moving to

  Here, the difference between the load fluctuation line Y ′ in the comparative example and the load fluctuation line Y of the operation load in the present embodiment will be described. The operation load from the fully closed position (point A) to the fully open position (point F) of the vehicle door D, and the position before the vehicle door D is closed beyond the half open position (point D) from the fully open position (point F) (point C). In FIG. 3, there is no significant difference between the load fluctuation line Y ′ in the comparative example and the load fluctuation line Y of the operation load in the present embodiment. However, there is a prominent difference in the operation load acting immediately before the vehicle door D is closed, that is, the operation load E (this embodiment) and the operation load E ′ (comparative example) of the vehicle door D at the point B. That is, when the vehicle door D is closed, the operation load E in the present embodiment exceeds the operation load E ′ in the comparative example in the operation load of the vehicle door D that affects the ease of closing the vehicle door D.

  In order to increase the operation load when closing the vehicle door D, it is necessary to set the inclination angle of the expansion portion 20a and the recess portion 20b of the check pattern 20 formed on the check pattern 20 of the check lever 2 high. That is, by setting the inclination of the expansion portion 20a of the check pattern 20 high, hysteresis loss is reduced, the load from the fully closed position of the vehicle door D to the fully open position, and the fully open position of the vehicle door D to the fully closed position. It is possible to reduce the load difference up to, that is, the gap G shown in FIG. However, as a contradiction, the operation load generated when the vehicle door D is opened, that is, the operation load value V when the vehicle door D at the point B in FIG. Here, by adopting the bracket 9 according to the present invention, the operation load value V can be lowered by shortening the moment arm at the rotation center T of the bracket pin 9d and the vehicle door D in the region D1 of the vehicle door D.

  In addition, the operation load E in this embodiment also falls by employ | adopting the bracket 9 in this invention and shortening the moment arm in the point B. FIG. However, by setting the inclination of the expansion portion 20a of the check pattern 20 high and reducing the hysteresis loss, the operation load E in the closing operation of the vehicle door D in this embodiment is equivalent to that of the comparative example. It can be secured larger than the operation load E ′.

  On the other hand, after the operation load value V is exceeded (region D2 in FIG. 3B and FIG. 6), the bracket pin 9d in the long hole 10 of the bracket 9 is long as shown in FIG. 3B. It moves to the other end in the longitudinal direction of the hole 10. Thereby, in the area | region D2 where a strong impact force may act on the vehicle door D by the over-opening of the vehicle door D, the distance between rotating shafts is made longer than the area | region D1. As a result, the moment arm between the rotating shaft of the check lever 2 and the rotating shaft of the vehicle door D is set longer to increase the operation load of the vehicle door D, and the impact force acting on the vehicle door D can be suppressed. .

Therefore, according to the present embodiment, the following effects can be obtained.
(1) When the maximum load of the operation load is applied in the opening operation of the vehicle door D, the distance between the bracket pin 9d located in the long hole 10 of the bracket 9 and the rotation center of the vehicle door D is shortened. As a result, the moment arm from when the maximum operating load is generated to the fully closed position becomes shorter than before. As a result, it is possible to suppress the maximum load acting when opening the vehicle door D as compared with the conventional case, and the opening operation of the vehicle door D becomes easier.
(2) Further, when the bracket pin 9d moves in the long hole 10 of the bracket 9 according to the rotational position of the vehicle door D, the contact portion 2a of the check lever 2 and the pressing plate 9c of the bracket 9 contact each other. This serves to position the bracket pin 9d, so that the bracket pin 9d can stably move in the long hole 10 of the bracket 9.
(3) After the first peak load of the vehicle door D is generated, the bracket pin 9d in the long hole 10 of the bracket 9 moves to the other end of the long hole 10 in the longitudinal direction. As a result, the moment arm is changed longer by increasing the distance between the bracket pin 9d serving as the rotation axis of the check lever 2 and the rotation center T of the vehicle door D. As a result, in a region where a strong impact force may act on the vehicle door D due to over-opening of the vehicle door D, the operation load on the vehicle door D may be increased to reduce the impact force on the vehicle door D. it can.

DESCRIPTION OF SYMBOLS 1 ... Vehicle door check apparatus, 2 ... Check lever, 2a ... Contact part, 3 ... Check surface, 4 ... Communication hole, ... Contact part, 5 ... Stopper part, 6 ... Case, 6a ... Case part, 6b ... Housing 7, sliding portion, 7 a, movable body, 8, biasing member, 9, bracket, 9 a, fixed plate, 9 b, support plate, 9 c, pressing plate, 9 d, bracket pin, 10, long hole, 20,. Check pattern, 20a ... expanded portion, 20b ... concave, B ... vehicle body, D ... vehicle door, L ... moment arm in this embodiment, L '... moment arm in comparative example, T ... center of rotation of vehicle door, V ... opening Initial maximum load value, Y: load fluctuation line of operation load in this embodiment, Y ′: load fluctuation line of operation load in comparative example

Claims (5)

A door check device disposed between a vehicle body and a vehicle door rotatably attached to the vehicle body,
A check lever having a check pattern whose thickness varies in the longitudinal direction;
A bracket for rotatably supporting one end of the check lever, and connecting the check lever to the vehicle body;
A sliding portion provided on the vehicle door and pressing in the thickness direction of the check lever,
The sliding portion is configured to increase or decrease the operation load of the vehicle door by sliding on the surface of the check lever according to a change in the opening degree of the vehicle door.
When the distance between the rotating shaft of the check lever and the rotating shaft of the vehicle door is the distance between the rotating shafts, the bracket can change the distance between the rotating shafts according to the opening of the vehicle door. Vehicle door check device that supports the lever. The check pattern of the check lever is formed such that the operation load has a first peak load and a second peak load as the opening degree of the vehicle door increases.
The opening between the opening of the vehicle door when the operating load becomes the first peak load and the opening of the vehicle door when the operating load becomes the second peak load is the intermediate opening When
The bracket is configured such that when the opening degree of the vehicle door is less than the intermediate opening degree, the distance between the rotating shafts is shorter than when the opening degree of the vehicle door is equal to or more than the intermediate opening degree. The vehicle door check device according to claim 1, wherein the check lever is supported. The bracket is formed with a long hole whose longitudinal direction is a radial direction in the rotation of the vehicle door that moves a bracket pin formed on the bracket according to a rotation position of the vehicle door.
The vehicle door check device according to claim 1 or 2. The check lever is formed with a long hole in a direction intersecting with a longitudinal direction of the check lever, which moves a bracket pin formed on the bracket according to a rotation position of the vehicle door.
The vehicle door check device according to claim 1 or 2.   A contact portion that contacts the bracket is formed at the one end of the check lever, and the bracket pin moves in the elongated hole as the opening degree of the vehicle door increases. The vehicle door check device according to claim 3 or 4, wherein a pressing portion that presses the check lever is formed such that a distance between the shafts becomes long.

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