JP4751551B2 - Opening and closing mechanism for vehicle opening and closing body - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to an opening / closing mechanism for opening and closing various vehicle opening / closing bodies such as a rear door of a one-box car and a sunroof of a general vehicle.
[0002]
[Prior art]
Conventionally, as this type of opening / closing mechanism, for example, there has been one disclosed in Japanese Patent Application Laid-Open No. 2000-335245.
The technology has the following configuration in configuring a vehicle door opening and closing device.
First, the driving force from the electric motor is transmitted to the slider member via a worm fixed to the motor and a worm wheel meshing with the worm, and further via a pinion gear formed coaxially with the worm wheel.
[0003]
This slider member is a substantially rectangular plate member, and a rack is formed on one edge of a pair of long sides. The driving force to the slider member is input to this rack. In the slider member, a guide groove is formed in the center of the plate width along the longitudinal direction. By engaging the guide groove with two guide pins having an enlarged head, the slider member that has obtained the driving force performs a linear reciprocating motion.
[0004]
Further, a shaft support portion formed by bending the slider member itself at a right angle is formed at a substantially central portion of the other side of the pair of long sides, and the shaft portion is fixed to the shaft support portion. That is, the shaft portion is attached to the main body portion with a predetermined height. An arm member connected to the door side is pivotally supported on the shaft portion so as to be swingable. As the slider member reciprocates, the arm member moves in and out of the vehicle body and swings to open and close the vehicle door.
[0005]
[Problems to be solved by the invention]
However, in the above conventional opening / closing mechanism, the driving force generated by the electric motor is all transmitted to the slider member through the meshing of the gears. Therefore, in order to reduce backlash and prevent the gears themselves from being disengaged, it is necessary to accurately dispose each gear and maintain the disposition for a long period of time.
For this reason, an efficient opening / closing mechanism could not be formed because the assembly of the opening / closing mechanism becomes complicated and the gear mounting portion needs to be strengthened.
[0006]
Moreover, in the said conventional technique, when the said slider member is seen from the extending direction of a guide pin, it exists in the positional relationship which the said rack and the said shaft part offset. In addition, as described above, the shaft portion has a predetermined height from the main body portion of the slider member having a planar shape, and therefore, the portion where the slider member is slidably received by the two guide pins. However, it is in a state of being out of the plane including the rack and the shaft portion.
That is, when the conventional slider member is reciprocated, a force to rotate the slider member in a plane formed by the main body of the slider member with the guide pin slidably receiving the slider member as a fulcrum, A force for lifting the slider member in the out-of-plane direction of the plane always acts on the slider member.
[0007]
For this reason, in order to eliminate the backlash of the slider member due to the above two forces, there has been a need to reinforce the constituent members such as strengthening the guide pin mounting structure or increasing the thickness of the slider member itself.
As described above, in the conventional opening and closing mechanism, it is difficult to say that the driving force from the electric motor is transmitted sufficiently efficiently, and the opening and closing mechanism itself has to be subjected to extra processing. I had a point to do.
[0008]
An object of the present invention is to provide an opening / closing mechanism for a vehicle opening / closing body capable of solving the above-described conventional problems and transmitting a driving force reliably and efficiently.
[0009]
[Means for Solving the Problems]
[Characteristic configuration 1]
To achieve this object, an opening / closing mechanism for a vehicle opening / closing body according to claim 1 of the present invention includes a crank gear that can be driven to rotate around a crankshaft core to open and close the vehicle opening / closing body,
A slider capable of reciprocating along a guide member; a crank arm having one end pivotally supported by the crank gear via a crank pin and the other end pivotally supported by the slider via a slider pin; An opening / closing body operating member is provided between the slider and the vehicle opening / closing body so as to be swingable with respect to the slider, and interlocks the slider and the vehicle opening / closing body . It is pivotally supported by the slider via an actuating member pivot shaft, and when the slider reciprocates, one end of the opening / closing body actuating member and the slider pin are perpendicular to the axis of the actuating member pivot shaft. It is characterized in that it is configured to be located on the same plane .
[0010]
(Function and effect)
By adopting the crank mechanism as the opening / closing mechanism of the vehicle opening / closing body as in this configuration, the driving force of the crankshaft can be reliably transmitted to the slider via the crank arm. That is, the crank gear and the crank arm are connected via a crank pin, while the crank arm and the slider are connected via a slider pin. Therefore, there is no possibility that communication between the members is impaired, and force is reliably transmitted between the members.
[0011]
In addition, since the drive system uses a crank gear, even if the size of the crank gear itself is constant, the drive position of the drive motor, the weight of the door to be opened and closed, etc. can be set by appropriately setting the crank pin formation position. Accordingly, an optimum drive mechanism can be configured. Therefore, various opening / closing mechanisms can be formed while reducing the number of necessary parts.
[0013]
Further, the opening / closing mechanism uses a crank mechanism, and in order to efficiently transmit the driving force, for example, it is conceivable to make the slider move smoothly with respect to the guide member. The invention according to this configuration is to prevent the changed driving force from rotating the slider around the slider pin after the driving force from the crank gear is changed in the advancing direction of the slider.
[0014]
Therefore, in this configuration, one end of the opening / closing body operating member and the slider pin are positioned on the same plane perpendicular to the axis of the operating member pivot shaft. That is, the opening / closing body operating member swings in a plane substantially perpendicular to the operating member pivot shaft, and the moving path of the slider and the slider pin are included in the plane.
[0015]
If it is this structure, when the driving force after the said direction change acts on a slider pin and is transmitted to an opening-and-closing body operation member, a slider will not rotate. As a result, the driving force after the direction change is efficiently transmitted to the opening / closing body operating member without causing the slider to inadvertently interfere with the guide member.
[0016]
[Characteristic configuration 2 ]
According to a second aspect of the present invention, an opening / closing mechanism for a vehicle opening / closing body includes a first rotating member that rotates around a first rotating shaft that is parallel to an axis of the operating member pivot shaft. With
The guide member is characterized in that a first guide surface for guiding the first rotating member is formed.
[0017]
(Function and effect)
In the opening / closing mechanism, the opening / closing body operating member swings relative to the slider as the slider reciprocates. That is, in this swing plane, the force transmission direction changes sequentially between the opening / closing member operating member and the slider.
For this reason, for example, when the slider operates to pull in the opening / closing body operating member, the slider may be pulled upward or downward depending on the swinging posture of the opening / closing body operating member.
[0018]
However, as in this configuration, the slider includes a first rotating member that rotates around a first rotating shaft that is parallel to the axis of the operating member pivot shaft, and a first guide surface that guides the first rotating member. By forming the guide member on the guide member, it is possible to prevent the slider from rattling and minimize the friction between the slider and the guide member, thereby making the opening / closing operation of the vehicle opening / closing member extremely smooth. it can.
[0019]
[Characteristic configuration 3 ]
An opening / closing mechanism for a vehicle opening / closing body according to a third aspect of the present invention includes a second rotating member that rotates around a second rotation axis parallel to the axis of the slider pin on the slider.
The guide member is characterized in that a second guide surface for guiding the second rotating member is formed.
[0020]
(Function and effect)
In this opening / closing mechanism, the crank arm swings with respect to the slider as the crank gear rotates. In other words, in the swing plane, the force transmission direction changes sequentially between the crank arm and the slider. At this time, since the slider and the guide member interfere with each other, some of the driving force transmitted from the crank arm is consumed as resistance. In order to efficiently transmit the driving force, it is preferable to reduce such resistance as much as possible.
[0021]
Therefore, as in the present configuration, the slider includes a second rotating member that rotates around a second rotating axis that is parallel to the axis of the slider pin, and the guide member has a second rotating member that guides the second rotating member. By forming the two guide surfaces, interference between the slider and the guide member can be mitigated, and generation of the extra resistance can be suppressed. As a result, the slider and the vehicle opening / closing body can be smoothly moved.
[0022]
[Characteristic configuration 4 ]
The opening / closing mechanism for a vehicle opening / closing body according to a fourth aspect of the present invention is characterized in that one end of the opening / closing body operating member is pivotally supported on the operating member pivot shaft via a spherical joint.
[0023]
(Function and effect)
A vehicle opening / closing body is attached to the end side of the opening / closing body operating member. However, the attachment of the vehicle opening / closing body is not always accurate, and for example, an error may occur in the attachment position of the opening / closing body operating member with respect to the vehicle opening / closing body. In such a case, the opening / closing body operating member does not extend in a direction perpendicular to the operating member pivot shaft.
[0024]
Therefore, as in this configuration, one end of the opening / closing body operating member is pivotally supported on the operating member pivot shaft via a spherical joint, so that the opening / closing body operating member is supported by the operating member pivot. It can be allowed to swing out of the plane perpendicular to the axis. As a result, even if there is an attachment error or the like in the vehicle opening / closing body, it is possible to prevent an unreasonable force from acting on the opening / closing body operating member or the operating member pivot shaft and to make the vehicle opening / closing body smooth. Can be opened and closed.
[0025]
DETAILED DESCRIPTION OF THE INVENTION
Embodiments of the present invention will be described below with reference to the drawings.
As shown in FIG. 1, the opening / closing mechanism for a vehicle opening / closing body according to the present invention closes, for example, a rear door 1 of a one-box car (hereinafter, “rear door 1” will be described as an example of the vehicle opening / closing body 100). It is used for the part operated between the state (FIG. 1 (a)) and the open state (FIG. 1 (b)). The operation of the rear door 1 is performed by transmitting the driving force from the driving motor 2 to the opening / closing body operating member 300 (hereinafter simply referred to as “door arm 3”) via the crank mechanism. Hereinafter, a mechanism according to the present invention will be described based on an embodiment in which the rear door 1 is opened and closed.
[0026]
As shown in FIGS. 2 and 3, for example, the opening / closing mechanism according to the present invention mainly includes a drive motor 2 for driving the crank gear 4, a crank arm 5 coupled to the crank gear 4, in addition to the crank gear 4. And a slider 6, a door arm 3 connected to the slider 6 to apply an opening / closing force to the rear door 1, a guide member 7 for guiding the slider 6, and the like.
[0027]
The crank gear 4 and the crank arm 5 are connected through, for example, a crank pin 8, and the crank arm 5 and the slider 6 are connected through, for example, a slider pin 9. Therefore, compared with a mechanism or the like in which power is simply transmitted by a gear, there is no possibility that communication between the members is easily lost, and force is reliably transmitted between the members.
With this configuration, the driving force from the crank gear 4 can be reliably transmitted to the slider 6 via the crank arm 5. For this reason, even if it is the rear door 1 which has predetermined | prescribed weight, it can open and close reliably, and there is no possibility that the rear door 1 in an open position may close unexpectedly, and a safe opening / closing mechanism is comprised. Can do.
[0028]
Further, by using the crank mechanism, for example, even when the driving capability of the driving motor 2 and the size of the crank gear 4 are constant, the formation position of the crank pin 8, the arrangement of the guide member 7, and the length of the crank arm 5 are maintained. By appropriately setting the above, the driving stroke and driving force of the slider 6 can be optimized. In this way, it is possible to obtain the desired opening and closing mechanism by changing a relatively simple shape member or changing the relative position. The mechanism is applicable.
[0029]
(Mechanism body)
The opening / closing mechanism is formed in one unit so that it can be easily attached to the ceiling of a vehicle. A member related to the opening / closing mechanism is attached to a mechanism body 10 having an outer shell structure. The mechanism body 10 is configured to have a concave space by aluminum die casting or the like. The crank gear 4 and other members are attached so as to fit inside the concave space.
The mechanism body 10 is attached to the vehicle using the mechanism attachment portion 11. As the mechanism attaching portion 11, for example, a bolt hole into which an attaching bolt can be inserted is formed in the mechanism main body 10.
[0030]
(Crank gear)
As shown in FIGS. 2 to 5, the crank gear 4 can be driven to rotate around the crankshaft core 4 </ b> A to open and close the rear door 1. The crank gear 4 is finished to have an outer diameter necessary for securing a stroke of a slider 6 described later. The crank gear 4 is engaged with a plurality of reduction gear trains 12 for inputting driving force from the driving motor 2 to the crank gear 4.
[0031]
(Drive motor)
As shown in FIG. 1, the drive motor 2 for opening and closing the rear door 1 is provided at the end of the opening / closing mechanism. As shown in FIG. 2, the output shaft 13 of the drive motor 2 is
The crank gear 4 is disposed on the opposite side of the vehicle interior space. Thereby, for example, when the present opening / closing mechanism is attached to the rear ceiling of the vehicle body, the drive motor 2 is arranged on the ceiling side with respect to the crank gear 4, and a large indoor space can be secured.
[0032]
(Crank arm)
As shown in FIG. 3 or 5, one end of the crank arm 5 is pivotally supported by the crank gear 4 via a crank pin 8. The other end is pivotally supported on the slider 6 via a slider pin 9.
The length of the crank arm 5 is appropriately set according to the diameter of the crank gear 4 and the distance between a guide member 7 (to be described later) and the crankshaft core 4A. For example, when the crank arm 5 is lengthened, the swing angle of the crank arm 5 itself is reduced, the change in the relative angle with the slider 6 is reduced, and the driving force can be smoothly transmitted to the slider 6. However, as the crank arm 5 becomes longer, the size of the opening / closing mechanism increases.
On the other hand, if the crank arm 5 is shortened, the opening / closing mechanism itself can be made compact. However, in this case, the swing angle of the crank arm 5 increases, and the efficiency in transmitting the driving force to the slider 6 is impaired.
[0033]
(slider)
As shown in FIGS. 2 to 5, the slider 6 can reciprocate along the guide member 7. The slider 6 is interposed between the crank arm 5 and the door arm 3 and interlocks both members while changing the transmission direction of the driving force.
The slider pin 9 is provided at the center in the width direction X of the slider 6. Here, the width direction X refers to a direction perpendicular to the moving direction Y of the slider 6 in FIG.
[0034]
(First rotating member and second rotating member)
As shown in FIGS. 6 and 8, the slider 6 is provided with a first rotating member 14 and a second rotating member 15 that smoothly guide the reciprocating motion of the slider 6. Among these, the first rotating member 14 is rotatable around a first rotating shaft core 14 </ b> A extending in a direction perpendicular to the slider pin 9 in a direction view along the moving direction Y of the slider 6. Further, the first rotating shaft core 14A is perpendicular to the moving direction Y of the slider 6 in the same plane (extends in the left-right direction in FIG. 6).
[0035]
As shown in FIG. 2 or FIG. 8, the slider 6 is provided with two first rotating shaft cores 14A along the moving direction Y, and the slider 6 is sandwiched between the first rotating shaft cores 14A. Two first rotating members 14 are attached.
The first rotating member 14 is particularly for responding to an input from the door arm 3 that is transmitted while its direction changes sequentially. The function of the first rotating member 14 will be described later.
[0036]
As the first rotating member 14, as shown in FIG. 6, a general radial bearing can be used. Further, a cylindrical rotatable collar member may be used. In short, the first rotating member 14 has any configuration as long as it can reciprocate the slider 6 along the guide member 7 while reducing the frictional force with the guide member 7 described later. There may be.
Even if the slider 6 is simply provided with a non-rotating protruding member or the like, it can be substituted for the first rotating member 14 as long as the slider 6 can be smoothly guided along the guide member 7. .
[0037]
As shown in FIGS. 2 to 6, the slider 6 is provided with two second rotating shaft cores 15A. The second rotating member 15 can rotate around the second rotating shaft core 15A. One of the two second rotating shaft cores 15 </ b> A is made to coincide with the shaft core 9 </ b> A of the slider pin 9. That is, in the present embodiment, the slider pin 9 is also used as an attachment portion for the second rotating member 15.
In addition to guiding the slider 6, the second rotating member 15 is particularly for responding to an input from the crank arm 5 that is transmitted while its direction changes sequentially.
[0038]
As the second rotating member 15, as in the case of the first rotating member 14, a general radial bearing, a rotatable cylindrical member, and a protruding member that does not rotate but has sliding properties are used. it can.
[0039]
(Guide member)
The guide member 7 regulates the movement direction of the slider 6. As shown in FIG. 4 or FIG. 6, the guide member 7 includes a guide main body 71 and a rail member 72.
[0040]
In the present embodiment, the guide body 71 is formed integrally with the mechanism body 10. For example, the groove-shaped portion is integrally formed by aluminum die casting or the like, and the rail member 72 is attached thereto.
If it is this structure, it is not necessary to provide the guide main body 71 separately, and the thickness for this member is reduced. Therefore, space saving of the opening / closing mechanism can be achieved.
Further, omitting the guide main body 71 is advantageous in terms of economy.
[0041]
Moreover, the rail member 72 is comprised using two substantially U-shaped elongate members, for example. In this case, as shown in FIG. 6, the first guide surface 16 is formed on the upper side portion and the lower side portion of the U-shape. Then, the second guide surface 18 is formed on the flange portion 17 connected to the edge portion of the upper side portion of the U-shape. The rail member 72 can be attached to the guide body 71 using, for example, a screw member.
[0042]
As apparent from FIG. 6, in the rail member 72 in the present embodiment, both the first guide surface 16 and the second guide surface 18 are formed on one rail member 72. As a result, the opening / closing mechanism can be saved in space.
The rail member 72 can be formed by bending a plate-like long member, for example. Therefore, it is advantageous in terms of economy, such as reducing labor for manufacturing the rail member 72.
[0043]
(Operation mode of first rotating member)
When the rear door 1 is opened and closed, the relative angle between the door arm 3 and the slider 6 changes sequentially, and the force transmission angle between the two changes. As a result, a force acts on the slider 6 from a direction different from the reciprocating direction of the slider 6.
For example, FIG. 4 shows a state in which the rear door 1 has started to close. When starting to close the rear door 1 from the open position, the extending direction of the door arm 3 is directed upward of the vehicle with respect to the moving direction Y of the slider 6. Therefore, when the slider 6 operates to pull in the door arm 3, the slider 6 is pulled upward. At this time, when the first guide surface 16 receives the first rotating member 14, even if the upward force is generated, the slider 6 is prevented from being lifted and the friction between the slider 6 and the rail member 72 is reduced. Can be kept to a minimum. As a result, the operation at the beginning of closing the rear door 1 becomes very smooth.
[0044]
On the other hand, FIG. 4 shows a state in which the rear door 1 approaches the open position from the closed position. In this case, a pressing force acts between the slider 6 and the door arm 3. As a result, the first rotating member 14 is pressed against the lower first guide surface 16. However, also in this case, the slider 6 can operate very smoothly by the cooperation of the first rotating member 14 and the first guide surface 16.
As described above, as long as the first rotating member 14 is guided by the upper and lower first guide surfaces 16, the door arm 3 is in any posture with respect to the slider 6, and the pressing force is between the two. Alternatively, it is possible to prevent the slider 6 from rattling and to make the slider 6 move smoothly regardless of which tensile force is applied.
[0045]
In the present embodiment, the shaft core 19A of the door arm shaft 19 (shown as an embodiment of the operating member pivot shaft 190) that pivotally supports the door arm 3 on the slider 6 and one first rotating shaft core 14A. Are matched. According to this configuration, the slider 6 can be configured in a simple and compact manner compared to the case where the two shaft cores are configured separately, and the opening / closing mechanism can be reduced. Further, the number of processing steps of the slider 6 can be reduced, which is advantageous in terms of economy.
[0046]
(Operation mode of second rotating member)
In the opening / closing mechanism, the crank arm 5 swings with respect to the slider 6 as the crank gear 4 rotates. That is, in this swing plane, the force transmission direction changes sequentially between the crank arm 5 and the slider 6.
At this time, since the slider 6 and the rail member 72 interfere with each other, some of the driving force transmitted from the crank arm 5 is consumed as resistance. In order to efficiently transmit the driving force, it is preferable to reduce such resistance as much as possible.
[0047]
Therefore, in this opening / closing mechanism, the slider 6 includes the second rotating member 15 that rotates around the second rotating shaft core 15A that is parallel to the shaft core 9A of the slider pin 9, and the rail that constitutes the guide member 7 A second guide surface 18 for guiding the second rotating member 15 is formed on the member 72.
[0048]
Thus, by receiving the second rotating member 15 by the second guide surface 18, interference between the slider 6 and the rail member 72 can be reduced. As a result, it is possible to suppress the occurrence of the extra resistance between the two and to smoothly move the slider 6 and the rear door 1.
[0049]
(Door arm)
As described above, the door arm 3 is interposed between the slider 6 and the rear door 1 so as to interlock with each other.
As shown in FIGS. 1 and 2, the rear door 1 is attached to a hinge 20 provided at an upper part on the rear side of the vehicle body. For this reason, the door arm 3 connected to the rear door 1 and the slider 6 swings in a plane substantially perpendicular to the hinge 20 and the door arm shaft 19 as the slider 6 reciprocates.
[0050]
In the present embodiment, the shaft core 19A of the door arm shaft 19 and the crank shaft core 4A are substantially perpendicular. For example, when the opening / closing mechanism is attached to the rear ceiling of the vehicle and the rear door 1 opens upward, the door arm 3 needs to swing in the vertical direction. In this case, the shaft core 19A of the door arm shaft 19 is directed substantially in the horizontal direction, and the crank shaft core 4A of the crank gear 4 is directed in the vertical direction.
As described above, the crank gear 4 according to the present invention has a relatively large diameter in order to ensure the stroke of the slider 6. Therefore, by attaching the crank gear 4 in a horizontal posture in this way, the plate surface of the crank gear 4 can be along the ceiling of the vehicle, and a large interior space can be secured.
[0051]
The opening / closing mechanism according to the present invention can smoothly open and close the rear door 1 even when an attachment error occurs in the width direction of the vehicle, for example, when the rear door 1 is attached.
As shown in FIG. 7, in this embodiment, one end of the door arm 3 is pivotally supported on the door arm shaft 19 via a spherical joint 21. A mounting member 22 for the rear door 1 is provided at the other end of the door arm 3.
[0052]
Depending on the mounting state of the rear door 1, the door arm 3 may not extend in a direction perpendicular to the door arm shaft 19. However, through the spherical joint 21, the door arm 3 is allowed to swing out of the plane perpendicular to the door arm shaft 19. As a result, excessive force can be prevented from acting on the door arm 3 or the door arm shaft 19 and the rear door 1 can be smoothly opened and closed.
[0053]
(Crank mechanism operation mode 1)
As shown in FIGS. 2 to 5, when the rear door 1 is opened and closed, the crank gear 4 reciprocates between a closed position and an open position. At that time, as shown in FIG. 9, the position and direction of the arm center line 23 connecting the crank pin 8 and the slider pin 9 or its extension line changes. Then, the perpendicular length from the crank shaft core 4A lowered to the arm center line 23 changes, and as a result, the driving force applied from the crank gear 4 to the crank arm 5 and further from the crank arm 5 to the slider 6 is increased. Change.
[0054]
FIG. 9A shows a state where the crank gear 4 is in the closed position. FIG. 9C shows a state where the crank gear 4 is in the open position. FIG. 9 (b) shows a state at the intermediate position. As shown in these drawings, in this mechanism, a longer vertical line is formed at a position between the closed position and the open position than the closed position normal length d1 at the closed position and the open position normal length d2 at the open position. The length d3 can be taken.
[0055]
The shorter the perpendicular length, the shorter the moment arm from the crankshaft core 4A, so the driving force transmitted from the crank gear 4 to the crank arm 5 increases. For example, in FIGS. 9A and 9C, relatively large driving forces F10 and F30 act along the longitudinal direction of the crank arm 5, but in FIG. 9B, a smaller F20 acts. Will do.
[0056]
In general, for example, when closing the rear door 1 of a one-box car, a large force is required at the beginning of closing and at the fully closed position. Usually, the rear door 1 is often provided with a gas damper or the like to support the weight of the opened rear door 1. For this reason, at the beginning of closing, a large operating force is required due to the operating resistance of the gas damper and the like. In addition, if the dirt of the hinge portion of the rear door accumulates with use over many years and the movement of the hinge portion becomes hard, a larger operating force is required.
Further, in the fully closed position, it is necessary to resist the elastic resistance of the seal member provided between the rear door 1 and the vehicle body, so that a large operating force is also required. When this seal member is cured over time, the required operating force further increases.
[0057]
On the other hand, when operating the rear door 1 in the closed position to the open position, a large operating force is required at the beginning of opening. This is because when opening the rear door 1 from the closed position, it is necessary to give an opening speed to the rear door 1 against the inertia of the rear door 1.
[0058]
In this regard, with this configuration, the opening / closing force can be increased at both positions. Therefore, the opening / closing force at the closed position and the open position can be set as appropriate without using a motor having a large driving force. Furthermore, the degree of increase in the driving force at the closed position and the open position can be arbitrarily set by devising the size of the crank gear 4 and the arrangement position of the rail member 72 with respect to the crank gear 4.
[0059]
(Crank mechanism operation mode 2)
As shown in FIG. 9, during the operation of the slider 6, the relative angle between the direction of the crank arm 5 and the moving direction Y of the slider 6 is not constant. Therefore, for example, in FIG. 9A, the driving force F10 transmitted from the crank arm 5 to the slider 6 is perpendicular to the force F11 along the moving direction Y of the slider 6 at the position of the slider pin 9. Is decomposed into a force F12 in a different direction. Among these, the component force F <b> 12 becomes a resistance to the operation of the slider 6. Therefore, in order to reduce such resistance and efficiently transmit the driving force of the crank arm 5 to the slider 6, it is preferable that the longitudinal direction of the crank arm 5 is brought close to the moving direction Y of the slider 6.
[0060]
Therefore, in this embodiment, the reciprocating locus 24 of the slider pin 9 or its extension line intersects with the rotational locus 25 of the crank pin 8 when viewed along the extending direction of the crankshaft core 4A as shown in FIG. Thus, the guide member 7 is arranged. Then, the position of the crank pin 8 in the closed position (FIG. 9 (A)) and the open position (FIG. 9 (C)) is the side of the crank shaft core 4A with respect to the reciprocating locus 24 or its extension line. It is comprised so that it may be located in.
[0061]
With this configuration, for example, when the crank gear 4 rotates from the closed position to the intermediate position, the crank pin 8 temporarily crosses the reciprocating locus 24 of the slider pin 9, and further, the crank pin 8 further moves to the intermediate position. When going to the open position, the traverse path 24 is crossed again. Thus, with this configuration, the reciprocating locus 24 of the crank arm 5 and the slider pin 9 coincides twice, and the crank arm 5 performs one reciprocating swing motion around the reciprocating locus 24. .
[0062]
In this way, by arranging the slider 6 and the crank arm 5 and keeping the direction of the crank arm 5 and the moving direction of the slider 6 as close as possible, the generation of the extra component force can be minimized. The driving force from the crank arm 5 can be transmitted to the slider 6 most efficiently.
[0063]
(Crank mechanism operation mode 3)
Further, in this configuration, the slider pin 9 is formed at the center in the width direction X of the slider 6, and the door arm 3 is attached to the approximate center of the door arm shaft 19 attached to the slider 6. That is, the door arm 3 is configured to swing in a plane substantially perpendicular to the door arm shaft 19, and the moving path of the slider 6 and the slider pin 9 are included in the plane.
[0064]
Thus, by setting the position of the slider pin 9 and the mounting portion of the door arm 3 so as not to be offset in the moving direction of the slider 6, the driving force once inputted in the moving direction of the slider 6 can be efficiently used once. 3 can be transmitted. That is, by not creating the offset, it is possible to prevent a force that causes the slider 6 to rotate.
[0065]
Therefore, for example, when the transmission of force in the plane of FIG. 9 is seen, the slider 6 can be prevented from inadvertently interfering with the guide member 7, and the force acting on the guide member 7 from the slider 6 Only the component force F12 generated when the force is transmitted from 5 to the slider 6 is obtained. As a result, the driving force from the crank gear 4 can be transmitted to the rear door 1 with maximum efficiency.
[0066]
[Another embodiment]
<1>
In the above embodiment, two long members having a U-shaped cross section are used to form the rail member 72. However, as shown in FIG. It is also possible to use four members.
[0067]
In this other embodiment, four rail members 73 having a rectangular cross section are used. In a cross-sectional view perpendicular to the longitudinal direction of the guide body 71, four rail members 73 are arranged at the four corners. In this arrangement, the rail member 73 may be screwed to the guide main body 71 or may be fitted. As a result, a substantially cross-shaped space appears inside the guide body 71. As shown in FIG. 10, the slider 6, the first rotating member 14, and the second rotating member 15 are disposed inside the space.
[0068]
The four rail members 73 are respectively formed with first guide surfaces 16 for guiding the first rotating member 14. Of the four rail members 73, two rail members 73 are formed with second guide surfaces 18 that guide the second rotating member 15. That is, both the first guide surface 16 and the second guide surface 18 are formed on the two rail members 73 arranged so as to sandwich the slider pin 9 therebetween.
[0069]
As in this configuration, a plurality of functions of the first guide surface 16 and the second guide surface 18 are carried on one rail member 73, thereby reducing the number of parts of the rail member 73 and simplifying the structure. 7 can be configured compactly.
[0070]
Further, as in this configuration, if the four rail members 73 are configured independently, illustration is omitted, but it is also possible to provide a position adjusting function for determining the relative positions of the rail members 73, It is also easy to obtain the guide member 7 without backlash.
[0071]
<2>
In addition, the rail members 72 and 73 can be formed of a single member.
Although illustration is omitted, for example, the two rail members 72 shown in FIG. 6 are connected on the side opposite to the flange portion 17. In that case, a bulging portion is provided on the side opposite to the flange portion 17 in order to secure a swinging space of the door arm 3.
If it is this structure, the number of members of a rail member can be reduced further, the effort of attachment with respect to the guide main body 71 can also be reduced, and an opening-and-closing mechanism can be obtained more efficiently.
[Brief description of the drawings]
FIG. 1 is an explanatory view showing a mounting state of an opening / closing mechanism according to the present invention. FIG. 2 is a side sectional view showing a state in which the opening / closing mechanism is in a closed position. FIG. 4 is a side sectional view showing a state in which the opening / closing mechanism is in the open position. FIG. 5 is a plan sectional view showing a state in which the opening / closing mechanism is in the vicinity of the open position. FIG. 7 is an explanatory view showing an operation mode of a spherical joint. FIG. 8 is an exploded perspective view showing a configuration near a slider. FIG. 9 is an explanatory view showing an operation mode of a crank mechanism. FIG. 10 is a guide member according to another embodiment. Sectional view showing [signs]
4 crank gear 4A crankshaft core 5 crank arm 7 guide member 6 slider 8 crankpin 9 slider pin 9A slider pin shaft 14 first rotating member 14A first rotating shaft 15 second rotating member 15A second rotating shaft 16 First guide surface 18 Second guide surface 19A Axle core 21 of actuating member pivot shaft 21 Spherical joint 23 Arm center line 24 Reciprocating locus of slider pin 25 Crank pin rotation locus 100 Opening and closing body for vehicle 190 Actuating member pivot shaft 300 Opening and closing Body actuating members d1, d2, d3 Perpendicular length Y Slider moving direction

Claims (4)

A crank gear that can be rotated around the crankshaft core to open and close the vehicle opening and closing body;
A slider capable of reciprocating along the guide member;
A crank arm having one end pivotally supported by the crank gear via a crank pin and the other end pivotally supported by the slider via a slider pin;
An opening / closing body actuating member interposed between the slider and the vehicle opening / closing body so as to be swingable with respect to the slider and interlocking the slider and the vehicle opening / closing body ;
The opening / closing body operating member is pivotally supported by the slider via an operating member pivot shaft;
Upon reciprocation of the slider, one end and the slider pin of the closing member actuating member, the opening and closing structure to tear Ru vehicle so as to be positioned on the vertical same plane with the axis of the actuating member pivot shaft Body opening and closing mechanism. The slider includes a first rotating member that rotates around a first rotating shaft that is parallel to the axis of the operating member pivot shaft;
Said guide member, said first rotary member a closure for a vehicle of the opening and closing mechanism according to claim 1 which is formed a first guide surface for guiding the. The slider includes a second rotating member that rotates about a second rotating axis parallel to the axis of the slider pin;
Said guide member, said second rotary member a closure for a vehicle of the opening and closing mechanism according to claim 1 which is formed a second guide surface for guiding the. 4. The opening / closing mechanism for a vehicle opening / closing body according to claim 1, wherein one end of the opening / closing body operating member is pivotally supported by the operating member pivot shaft via a spherical joint.

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