JP6566264B2 - Door closing brake device - Google Patents

Description

  The present invention relates to a door closing brake device.

  A conventional door closing brake device (door closer) is a mechanism for controlling the linear motion of a door closer body by converting the rotational movement of an arm member into a linear motion of a relatively short distance in the closing brake device. A compression spring and piston are inserted inside the cylinder, the gear rotates by the rotation of the arm member that interlocks with the opening and closing of the door, the piston moves linearly by the movement of the rack engaged with the gear, and the piston moves There are many configurations in which a load is applied by the oil filled in the cylinder between the two separated chambers flowing through the orifice, and most of them use hydraulic pressure for the basic mechanism. As a feature of this mechanism, the door is always controlled with a strong force over the entire range where the door can be opened, and during the closing operation, it is decelerated to a low speed once and then slowly closed to the end, then the door is opened largely. The same closing operation can be obtained from a state where the door is opened or a state where the door is slightly opened.

  In these conventional door closers, the closure braking device main body is attached to the door, the two arm members are connected in a folded state, and one end of the two connected arm members can be rotated using the attachment member. Is attached to the upper frame, the other end is attached to the main body of the closing brake device, the angle of the two arm members changes as the door opens and closes, and the rotation of the arm member on the closing brake device side moves linearly within the closing brake device A two-arm foldable type that converts to motion, and a rail body with a sliding member movably incorporated in the upper frame, with one end of a linear arm member attached to the closed braking device main body located on the door The other end of the arm member is pivotally attached to the slide member, and the movement of the arm member rotating while the slide member moves in the rail body by the opening and closing operation of the door is directly performed in the closed braking device. With one arm type which converts the movement, there are roughly divided into two types.

  However, although the hydraulic door closer described above has excellent performance, it is necessary to reliably seal the oil whose pressure changes, which inevitably complicates the structure, increases the number of parts, and increases the cost. have. Also, as the closing operation, a gear connected to the end of the arm member on the main body side of the closing braking device is rotated at the fulcrum position, so that a very strong spring that is not defeated by hydraulic pressure or the like is necessary, and a high strength that can cope with the above-mentioned strength is required. Strong racks and gears must be built in. Therefore, the entire closed braking device has a considerably large shape, lacks compactness in terms of size, and further, the operation for releasing from the closed state is inevitably heavy. Concealed types that are built in doors and frames that are superior in design and are not exposed to the outside are required to be more compact, more and more precise structures are required, and there are concerns that they will be more expensive. .

  Many door closing devices that do not use hydraulic pressure have been proposed, and Japanese Patent Application Laid-Open No. 2000-45624 and Japanese Patent Application Laid-Open No. 2001-28895 are examples of a structure that pulls the door only by the force of a spring member. It is disclosed. However, when only the spring is used directly as the driving force for the closing operation, the pulling force is stronger as the door is opened larger as the spring characteristic, and the pulling force tends to be smaller when opened only slightly. Yes. Further, when no load is applied at the time of closing, inertia force is also applied from the middle of closing. Accordingly, the speed at the final stage of complete closing varies depending on the degree of opening of the door, and it is unlikely that the speed is functionally satisfactory.

  Therefore, the most important point to be solved is that when closing from a large open state, the speed is too high so that a deceleration operation at the final stage is necessary, and closing from a slightly opened state has a small attraction force. It is considered that a mechanism corresponding to this contradictory phenomenon that does not completely close when having a deceleration operation is required. Therefore, a configuration using a mainspring spring, an equal load spring, or the like in which the load before and after being greatly bent is not significantly changed can be considered as a characteristic of the spring, which is also reported in Japanese Patent Application Laid-Open No. 2005-273199. However, the mainspring spring and the equal load spring need a winding function, and are large in size and expensive in cost, so that it is required to be relatively compact and inexpensively configured. However, there are still problems that are difficult to adopt. Furthermore, even with a mainspring spring or an equal load spring, it is not possible to obtain a reverse phenomenon in which the force is greater when the deflection is small than when the deflection is large.

  Therefore, the inventor further assembled the columnar cam 14, the shaft center 15, the pushing bit 16, and the spring member 17 in the drive case 13 as shown in FIG. A closing device has been proposed in which the tip protrusion of the bit 16 is brought into contact with the outer peripheral surface of the columnar cam 14 while being urged by the spring member 17. A rail device in which a slide member mounted with a rotary damper configured to generate a load due to the rotation of the gear as a speed reduction member is arranged so as to be linearly movable within the rail body provided with the rack is provided. Japanese Laid-Open Patent Publication No. 2006-75055 reported a closed braking device in which a rail device is allocated and arranged on an upper frame of a door and an upper portion of the door and both are connected by a single arm member 3.

  Here, as a feature of the closing device in the above-mentioned JP-A-2006-75055, the shape of the outer peripheral surface of the columnar cam 14 is important, and the distance from the center of the axis 15 to the outer peripheral surface is within a narrow opening angle range. It has a part which is set so that the distance from the center of the shaft center 15 to the outer peripheral surface gradually changes with respect to the part that changes extremely greatly and the same unit opening angle. Since the shaft center 15 and the columnar cam 14 are fixed to the arm member 3 at the same time, as shown in the locus diagram in FIG. 12, the columnar cam 14 is closed together with the arm member 3 by opening the door 19. The pushing bit 16 moves while compressing the spring member 17, and if it is left as it is, the arm member 3 is rotated to return to the original direction. As a result, the door is moved. Nineteen closing actions can be obtained. In other words, it is important to obtain an optimal closing force by appropriately setting the shape of the outer peripheral surface, and it is almost uniform in the range in which the door 19 is opened relatively large, and the opening angle is about 30 degrees. The closing force is gradually increased from the final closing range, and the closing force can be further increased in the range immediately before the complete closing from the opening angle of about 10 degrees. In the rail device disclosed in JP-A-2006-75055, the slide member moves in the rail body, and the gear that is interlocked with the speed reduction member in the final stage of the moving operation is attached to the rack. It is configured to obtain a deceleration operation by engaging.

However, even in the above-mentioned closed braking device, there is still a deficiency in the braking operation by the deceleration mechanism on the rail device side, and the degree of deceleration when the door is closed at high speed, especially because the rotary damper was used for the deceleration mechanism And, there is a point that you can not get an extremely large difference in the degree of deceleration when closing at low speed, so if the load of the rotary damper is too large, it will overcome the closing force and stop before the door completely closes The main point is that it is liable to malfunction. Therefore, it is difficult to use a large deceleration force to securely close the door, and there is a phenomenon that the braking effect at the time of sudden closing such as a tilt due to wind becomes small, and there is still room for improvement. Remaining.
JP 2000-45624 A Japanese Patent Laid-Open No. 2001-288156 JP 2005-273199 A JP-A-2006-75055

  The present invention has been made in order to solve the above-mentioned problems, and is based on the premise that the door can be opened up to about 180 degrees on the premise that it can be formed relatively simply and compactly without using a complicated and large hydraulic mechanism. It is an object of the present invention to propose a door closing braking device having an automatic closing mechanism from a position slightly below 90 degrees and having a braking operation by a speed reducing mechanism in a final closing range.

  In the present invention, the following technical means are provided to solve the above problems. First, a closing device, an arm member, and a rail device in which a slide member having a linear motion damper is movably arranged in a linear rail body are provided, and the closing device is provided on the upper part of the door and the upper frame. And a rail device are distributed and mounted, and both are rotatably connected by an arm member to constitute a door closing brake device.

  The closing device is pivotally mounted at the central position in the drive case with the columnar cam and shaft center integrated, and is arranged with two push-in bits facing each other with a plurality of spring members from both the left and right directions. The tip protrusions of the two pushing bits are brought into contact with the outer peripheral surface of the columnar cam in a state of being biased by a spring member. The columnar cam has a columnar shape that is long in the vertical direction, and has an axial center at a central position. The outer peripheral surface of the columnar cam is a portion where the distance from the center of the shaft center to the outer peripheral surface changes extremely in a narrow opening angle range, and the outer periphery from the center of the shaft center for the same unit opening angle. It is formed of a portion set so that the distance to the surface gradually changes and an arc portion where the distance from the center of the axis to the outer peripheral surface does not change.

  In the operation of the double push bit and the columnar cam, when the door is closed, the tip protrusion of the double push bit opens with a small distance from the center of the outer peripheral surface of the columnar cam to the outer peripheral surface. It is in contact with the part that changes extremely in the angle range, and therefore the tip protrusion of both push-in bits is pushed against the outer peripheral surface by the rotation of the columnar cam attached to the arm member at the initial opening stage of the door, and the spring member is When the door is opened while being greatly bent, the spring member is gradually bent while coming into contact with a portion where the distance from the center of the shaft center to the outer peripheral surface gradually increases.

  In addition, if the range in which the distance from the center of the shaft center to the outer peripheral surface gradually changes is set up to a position where the door opening angle is about 85 degrees, the spring member is most bent at that position. Since it is large, a large force is applied to the tangential inclination direction of the outer peripheral surface, and if it is left as it is, the closing operation starts. And since the force of the spring member becomes weaker gradually as the amount of bending decreases, it is better to adjust the degree of inclination of the tangent of the outer peripheral surface so that the closing force does not become extremely small. . In addition, since the inclination of the outer peripheral surface is set to be further increased in the final closing range, the closing force can be increased further from this range. Furthermore, since the degree of inclination of the outer peripheral surface is extremely large in the range immediately before complete closure, it is possible to perform an operation of pulling the door strongly at the end. In order to minimize the difference in force between the initial deflection and the maximum deflection of the spring member, the spring member is arranged in the drive case in a state where the compression spring having a relatively free length is already largely bent, It is further preferable to set so that a certain distance is further compressed from the state by the rotation operation of the columnar cam.

  Next, in the rail device, a linear motion damper having a predetermined stroke of a mechanism that obtains resistance when the rod rod is submerged as a speed reducing member, and a very large resistance force during a sudden submerging operation, It is preferable to use a characteristic that generates only a small resistance force during a slow sinking operation. By attaching a linear damper to the slide member, when the door is closed, the rod member of the linear damper is submerged in the final closed range due to the movement of the slide member within the main body rail. The braking operation is performed by the resistance force of the dynamic damper.

  Here, the angle range considered to require the braking operation is preferably the final closing range from a position about 30 degrees before the door is completely closed, and therefore, the operation in which the rod rod of the linear damper is submerged starts. It is good to set this from this position. Since the resistance force of the linear motion damper is required continuously until the door is completely closed, the stroke of the linear motion damper is preferably adjusted to this predetermined condition. In addition, there are types of linear motion dampers that have various strengths in terms of resistance force per unit distance when the rod rod is sunk, and if a linear motion damper with extremely large resistance force is used, as described above Since the linear damper is applied with a very large resistance force during a sudden sunk operation, if it is set at a braking operation that decelerates the door suddenly at this stage, the repulsive force will prevail over the rod sunk. There is a risk that the door will bounce off.

  Therefore, a plurality of linear motion dampers with different resistance and resistance to the extent that the door does not bounce are mounted on the slide member, and the rod rods of the linear motion dampers are gradually submerged in the final closing range of the door. It is good to set so that you can get the action you want. Then, after braking for a certain distance with the resistance force of the first linear motion damper, the braking force of the next linear motion damper is also applied, so the more the number of linear motion dampers used, the more smooth and the overall control becomes large. Power can be realized. This is also related to the durability of the linear damper itself, and the entire load required when the door is decelerated is distributed among multiple linear dampers. It also leads to securing.

  Furthermore, a contact member having a plurality of contact surfaces is arranged inside the rail body in a position changeable state, and the rod rods of a plurality of linear motion dampers having different strokes are appropriately attached to the contact surfaces of the contact members. If it sets so that it may collide, the operation | movement in which each linear motion damper will be subdivided further finely will be obtained, and the braking operation | movement of a door will be implemented more finely by the resistance in that case. Moreover, since the force required to close the door varies depending on the weight and size of the door, it is important that the braking force can be adjusted for various doors. Therefore, by setting the position of the abutting member so that it can be changed depending on the type of door, the entire resistance can be adjusted as appropriate, and it becomes possible to deal with various types of doors. Furthermore, when a hinge or pivot hinge with a mechanism that can adjust the position when the door is installed is used, the stroke of the linear motion damper should be left in advance as an adjustable amount in the left-right direction.

  As a speed reducing member, it has a predetermined stroke, and a resistance is obtained when the rod rod is sunk. A very large resistance force is applied during a sudden sunk operation, and a small resistance is applied during a slow sunk operation. By using a linear motion damper that generates only a force, an appropriate braking operation can be obtained in the final closing range of the door. Also, if the diameter of the damper insertion hole formed in the slide member is set to be slightly larger than the diameter of the outer tube, it has the role of a guide when the linear motion damper moves in and out, and the linear motion damper The rod rod can be set so that no force is applied from the side.

  A plurality of linear motion dampers with different strokes are mounted on the slide member, so that the rod rods of the linear motion dampers can be gradually lowered in the final closing range of the door closing operation. If you keep the brakes for a certain distance with the resistance of the linear motion damper that sinks first, the resistance of the next linear motion damper will also be applied, so there will be no rebound and the overall braking force will be large. It becomes possible.

  If a contact member having a plurality of contact surfaces is arranged inside the rail body and the linear motion dampers having different strokes are set so as to collide with the contact surfaces of the contact members as appropriate, An operation in which the rod rod of the dynamic damper is further finely stepped can be set, and the braking operation of the door can be performed more finely. Moreover, by setting the position of the contact member so that it can be changed, the total resistance can be adjusted as appropriate, and it is possible to easily cope with various types of doors having different sizes and weights.

  When using hinges or pivot hinges that have a mechanism that allows the installation position to be adjusted after the door is hung, set the rail body longer by the left-right adjustment to ensure the range of movement of the slide member. The stroke of the linear motion damper is preferably left in advance as an adjustable amount in the left-right direction, and the installation position of the door can be adjusted as it is after the closing brake device is mounted.

Embodiments of a door closing brake device according to the present invention will be described below with reference to the drawings. FIG. 1 is a perspective view when the closing brake device of the present invention is mounted in the upper frame 18 of the door and the upper part of the door 19 and the door 19 is opened about 30 degrees, and FIG. FIG. First, in the present invention, as shown in FIG. 1, a rail having a closing device a on the lower inner surface of the upper frame 18 and a rail body 1, a slide member 2, and a linear damper 4 as main members on the upper thickness direction surface of the door 19. The device b is arranged in an embedded state, and the closing device a and the slide member 2 are connected by the arm member 3. Next, FIG. 3 is a front sectional view showing the closed state of the door 19 with the same configuration, and the arm member 3 is arranged in a gap portion between the upper frame 18 and the upper surface of the door 19.

  FIG. 4 shows the position of the slide member 2 in the rail body 1 by opening and closing the door 19 from the closed state to the open state of 180 degrees and the rotation trajectory of the arm member 3 in the open state of the door 19 every 15 degrees. FIG. Since the arm member 3 has a fixed length as shown in FIG. 4, the arm member 3 rotates in the horizontal direction while the slide member 2 linearly moves in the rail body 1 as the door 19 is opened and closed. Become. At this time, when the door 19 is closed, the slide member 2 is disposed at a position closest to the door tip side in the rail body 1, and the slide member 2 moves through the rail body 1 as the door 19 opens. It moves to the direction and it becomes the operation | movement which moves to the door butt side most in the position which the door 19 released 180 degree | times.

  Next, FIG. 5 is a perspective view of the slide member 2, and FIG. 6 is a perspective view of the linear motion damper 4. The slide member 2 is formed so as to be able to move smoothly in the rail body 1 and is provided with a deep damper insertion hole 5 from one direction so that a plurality of linear motion dampers 4 can be mounted. 6 is formed. In FIG. 5, three damper insertion holes 5 are provided so that three linear motion dampers 4 can be inserted as an example, but the number of linear motion dampers 4 to be used is arbitrary. Further, as shown in FIG. 6, the linear damper 4 is configured such that a rod rod 8 having a piston moves in the outer tube 7, and a cap 9 is attached to the tip of the rod rod 8. Here, as a basic function of the linear motion damper 4, a relatively viscous oil is enclosed in the outer tube 7, and there is a mechanism for generating a load when the oil moves through the orifice. There are various types of configurations, but in this door closing brake device, it is preferable that the outer tube 7 is as thin as possible in size and compact as a whole. Therefore, it is preferable that the linear motion damper 4 is selected and used as the optimum one from among commercially available standard products. As for the operation, a very large resistance force is applied when the rod rod 8 is suddenly submerged when a large load is applied, and when the rod rod 8 is gently submerged when a small load is applied. Only a very small resistance force is generated, and the difference between the two is excellent in terms of condition.

  As shown in FIG. 7, the cap 9 portion of the linear motion damper 4 may be inserted into the damper insertion hole 5 of the slide member 2 from the cap 9 side, and the cap 9 portion may be fixed to the slide member 2. FIG. 7 shows a state in which the cap 9 part is fixed from the lateral direction of the slide member 2 with a hexagonal socket screw. At this time, the direction in which the linear motion damper 4 is inserted can be reversed, but it is very important that the linear motion damper 4 be used so that no force is applied to the rod rod 8 from the lateral direction when it is retracted. . Therefore, if the diameter of the damper insertion hole 5 is set to be slightly larger than the diameter of the outer tube 7, the damper insertion hole 5 can also serve as a guide in the direction shown in FIG. Furthermore, the rod rod 8 that appears and disappears should not be exposed to dust as much as possible. In this direction, the rod rod 8 is always hidden in the damper insertion hole 5 of the slide member 2, and the diameter of the outer tube 7 and the damper It is preferable to set the diameter of the insertion hole 5 to an optimum condition that does not allow dust, dust, or the like to enter as long as it does not interfere with each other's operation.

  FIG. 7 shows a state in which two types of linear motion dampers 4 having different strokes are used and a slide member 2 having a long stroke and a short stroke is mounted on the slide member 2. FIG. 7A shows a state in which both of the linear motion dampers 4 are projected most, and FIG. 7B shows a state in which both of the linear motion dampers 4 are most sunk. Accordingly, when the depth of the damper insertion hole 5 is set so that the portion of the outer tube 7 does not protrude from the damper insertion hole 5 with the linear motion damper 4 protruding most as shown in FIG. good. 7 shows the slide member 2 as viewed from the side, so that only two linear motion dampers are shown, but the slide member 2 in FIG. 5 has three damper insertion holes 5. May have a configuration in which another linear motion damper 4 with a longer stroke is mounted, or a configuration in which another linear motion damper 4 with a shorter stroke is mounted, and the stroke is different. A configuration in which the third type of linear motion damper 4 is mounted is also possible, and the number, type, and size of the linear motion dampers 4 to be used are arbitrary.

  Next, the configuration of the closing device a will be described. The closing device a used in the present invention may be configured in accordance with what is reported in JP-A-2006-75055 described in the background art. FIG. 11 is a perspective view of the closing device a, in which the columnar cam 14 and the shaft center 15 are mounted at the center position of the drive case 13 so as to be smoothly rotatable, and two pushing bits 16 are provided on the left and right sides thereof. And a plurality of spring members 17 are assembled. The columnar cam 14 is fixed to the shaft 15 in a non-rotatable state, and is urged by a plurality of spring members 17 with the ends of both pushing bits 16 opposed to the outer peripheral surface of the columnar cam 14. Then, the arm member 3 is fixed to the shaft center 15, and the columnar cam 14 is rotated together with the arm member 3 in accordance with the operation of opening the door 19. Further, the outer peripheral shape of the columnar cam 14 is important for the closing operation, and the distance from the center of the axis 15 to the outer peripheral surface is gradually increased with respect to the same unit opening angle. In the final closing range from the open position of about 30 degrees, the difference in the distance from the center of the shaft center 15 to the outer peripheral surface with respect to the unit opening angle is set gradually large so that the resistance force of the linear motion damper 4 is not lost. Maintaining the closing force, and in the range immediately before the complete closing from about 10 degrees open position, by setting the difference of the distance from the center of the axis 15 to the outer peripheral surface with respect to the unit opening angle to be extremely large, a stronger force The door 19 can be completely closed. Further, by forming an arc-shaped portion from the axial center 15 on the outer peripheral surface of the upper and lower constant thickness portions of the columnar cam 14, the distance from the center of the axial center 15 is constant for an opening angle of 85 degrees or more. Thus, it is preferable to set so that the closing force is not generated in this range.

FIG. 12 sequentially shows the rotation operation of the arm member 3 and the columnar cam 14 with respect to the closing device a. FIG. 12A shows a state in which the door 19 is completely closed, and the tip of the pushing bit 16 is the outer periphery of the columnar cam 14. It is in contact with the surface. Then, when the door 19 is opened from this state, the columnar cam 14 rotates together with the arm member 3 as shown in FIG. 12B, and the tip of the pushing bit 16 is pushed against the outer peripheral surface of the columnar cam 14, and the spring member 17 is compressed. Therefore, a stronger force is applied in the direction of returning as the door is opened more widely. Accordingly, when the opening operation of the door 19 is stopped and freed at the position shown in FIG. 12 (c) that has been largely released to about 85 degrees, the urging force of the spring member 17 causes the tangential inclination of the contact point on the outer peripheral surface thereof. A force is applied to rotate the arm member 3 in a direction to return the arm member 3 to the original strength, that is, an operation of closing the door 19 is obtained.

And it is very important to combine this closing operation with the deceleration operation in the linear damper 4 from the stage where it is closed to a predetermined position. As an ideal condition, in the notation of the locus in FIG. In the range where the opening position of 19 is less than about 85 degrees, the closing operation is started with a closing force exceeding the frictional force such as a hinge necessary for closing the door 19, and the closing operation is started in the final closing range from about 30 degrees. The deceleration operation by the resistance force of the dynamic damper 4 may be started. And as the subsequent closing operation, when the door 19 is suddenly closed and inertial force is applied, the closing operation is received, and the braking operation is required to decelerate to a low speed and then close gently. At the same time, even if there is no inertial force that causes the door 19 to close very slowly, it is assumed that it is necessary to securely close the linear damper 4 while immersing it. Therefore, it is effective to use the linear motion damper 4 having a configuration in which a very large resistance force is generated when the rod rod 8 is suddenly submerged, and only a small resistance force is generated when the rod rod 8 is extremely submerged. Thus, an excellent braking operation can be obtained as a whole of the closing operation.

Another important point here is the movement distance of the slide member 2 per unit angle when the door 19 is closed on the trajectory of this configuration. FIG. 8 is a top view showing the distance of movement of the slide member 2 in the rail body 1 when the door 19 is closed from 90 degrees when the door 19 is opened and closed at every 15 degrees when the door 19 is opened and closed. is there. That is, when the slide member 2 is closed from 90 degrees to 75 degrees, the slide member 2 moves a distance h-g. As a characteristic of the trajectory of the configuration of the present invention, in the movement distance of every 15 degrees, gf from 75 degrees to 60 degrees and fe from 60 degrees to 45 degrees are the largest, followed by Are slightly h-g from 90 degrees to 75 degrees and ed from 45 degrees to 30 degrees. Then, dc from 30 degrees to 15 degrees within the final closing range has a slightly shorter moving distance, and ca from 15 degrees to 0 degrees including immediately before complete closure is considerably shortened. Even in the range from 15 degrees to 0 degrees, when viewed in 5 degree increments, 10 degrees to 5 degrees is smaller than 15 degrees to 10 degrees, and further, in ba of 5 degrees to 0 degrees The travel distance becomes extremely small as indicated by the additional position where the opening angle is 5 degrees.

  This is important in the braking operation by the linear motion damper 4, and in the final closed range, the moving distance of the slide member 2 becomes smaller as the door 19 is closed. The distance at which the sunk will be reduced as well. Further, it can be seen that the moving distance per unit angle of the slide member 2 is still relatively large at the position where the opening angle of the door 19 for starting braking is about 30 degrees. Accordingly, if the linear motion damper 4 with extremely large resistance force is used to suddenly decelerate at the start of braking at the 30-degree open position, the door 19 will be undesirably moved back. In addition, such a phenomenon is not good in durability because the direct acting damper 4 itself is subjected to a sudden load. Further, in the above case, naturally, the door 19 needs to be continuously closed without stopping after that, so that it is necessary to set the closing force by the closing device a in this state to be stronger, and in this case, the slide is now performed. Immediately before the complete closing when the moving distance of the member 2 is small, a strong closing operation such as closing with a bang is performed.

That is, it is necessary to set the movement distance per unit angle of the slide member 2, the closing force of the closing device a at that time, and the braking force by the linear motion damper 4 in a well-balanced manner. Therefore, it is important to combine the resistance force of the linear motion damper 4 with the closing force of the closing device when the resistance force is generated. In the case where only one linear motion damper 4 is used, the final closing range is narrowed. Rather than applying a sudden resistance force with a short stroke, it is suitable to use a medium resistance force with a relatively long stroke and make the final closing range as wide as possible and close it while gradually applying the resistance force. ing. Further, as a means which is assumed to be more effective, as shown in FIG. 7, a plurality of linear motion dampers 4 having different strokes are arranged on the slide member 2, and a plurality of abutments are provided at positions where the braking operation in the rail body 1 is started. A contact member 10 having a surface may be disposed. FIG. 9 shows an example of the contact member 10, which has a shape having a first contact surface 11 and a second contact surface 12. FIG. 10 shows a state in which the contact member 10 is arranged in the rail body 1, and the first contact surface 11 and the second contact surface 12 are formed at different positions in the rail body 1. ing.

  As a specific example of giving the resistance force by the plurality of linear motion dampers 4 in a stepwise manner in order to obtain an optimum braking operation, the linear motion damper 4, the first contact surface 11, and the second one with two different strokes are used. Assuming the case where the abutting member 10 having the abutting surface 12 is used, as shown in FIG. 10, the door 19 is opened from the state shown in FIG. 10 (b) because the slide member 2 moves and the movement distance of the slide member 2 is still relatively large and the resistance force of the linear motion damper 4 is easily obtained when braking is started at the release stage of about 30 degrees. As shown in FIG. 10 (c), only the linear motion damper 4 with the larger stroke is set so as to sunk against the first contact surface 11 and braked for a certain distance, as shown in FIG. 10 (c). The linear damper 4 also has a second contact surface 12. It should be set so that it struck down. When the moving distance of the slide member 2 per unit of angle becomes small, braking is performed by both linear motion dampers 4, and the slide member 2 moves per unit angle immediately before complete closing. Since the amount is very small, at this stage, the closing force by the closing device a is won while receiving the resistance force of the linear motion damper 4, and the door 19 continues to be closed slowly, as shown in FIG. 10 (d). The door 19 is completely closed in a state in which the linear motion damper 4 is fully stroked.

In addition to the configuration using two linear motion dampers 4 as shown in FIG. 10, a configuration in which three linear motion dampers 4 can be attached to the slide member 2 shown in FIG. 5, and more linear motion dampers 4. The contact members 10 are arranged in a larger number, and the plurality of linear motion dampers 4 are sequentially brought into contact with the plurality of contact surfaces so that the linear motion dampers 4 are further finely stepped. May be obtained. Then, the resistance force can be applied in a stepwise manner, and the door braking operation can be performed more precisely. By setting in this way, even in the doors 19 having different sizes and weights, a sufficient braking operation can be obtained even when the door 19 is suddenly closed by appropriately setting the braking conditions by the linear motion damper 4. In addition, it is possible to provide a braking device with a closing mechanism that closes the door 19 slowly and surely after decelerating to an extremely low speed.

  In addition, when a hinge or a pivot hinge having a mechanism capable of adjusting the position when the door is installed is used, the movement range of the slide member 2 is increased by the adjustable amount in the left-right direction. Can be mentioned. Then, in the setting using the strokes of the two linear dampers 4 in FIG. 10 to the maximum, that is, in the state where the door 19 is completely closed, as shown in FIG. If it is set to do, a phenomenon occurs in which the stroke becomes maximum before the door 19 is completely closed when the door 19 is installed and adjusted on the suspending side. Therefore, it is set in a state where the stroke of the linear motion damper 4 is left extra, that is, when the door 19 is completely closed, the stroke of the linear motion damper 4 is not submerged by an adjustable amount such as a hinge. Well, there is no particular problem even if the installation adjustment in the left-right direction is carried out after construction.

  Further, not only the extra stroke is left for the adjustment of the installation, but the entire stroke of the linear motion damper 4 is set not to be used from the beginning in the standard state, and at the same time, the abutting member 10 itself in the rail body 1 is set. A configuration in which means capable of arbitrarily adjusting the mounting position is also assumed. As the means, as shown in FIG. 9, a configuration in which a plurality of mounting locations are provided on the mounting surface of the abutting member 10 and it can be gradually shifted and fixed in the rail body 1 or, although not shown, one side is an elongated hole is arbitrary. The method that can be fixed at the position is simple. Then, by moving the position of the contact surface of the contact member 10, the use width of the stroke for generating the resistance force can be adjusted, and a more optimal closing operation can be obtained.

  Further, as an advanced form of the mechanism for moving the contact surface to an arbitrary position as described above, although not shown, the contact member 10 is formed by two inclined members, and the inclined surfaces face each other. It is arranged in the rail body 1 in a state, a contact surface is formed on one inclined member, an internal thread portion is provided on the other inclined member, and it is moved up and down by an operation of turning a screw from the upper surface of the rail body 1. It is considered that a configuration in which the inclined member having the contact surface is moved in the lateral direction is effective by setting and moving the inclined surfaces by the vertical movement. In this configuration, after the construction is completed, the position of the contact surface of the contact member 10 can be moved from the upper part of the door 19 by the operation of the driver, and the resistance force as a whole is further improved so as to achieve an optimal closing operation. It becomes possible to adjust.

  Further, in the above, the linear motion damper 4 is mounted on the slide member 2 and is set so as to move in the rail body 1 together with the slide member 2 at the time of opening / closing. The same braking operation can be obtained even in a configuration in which a plurality of linear motion dampers 4 having different strokes are arranged and the end portion of the slide member 2 is formed as a contact surface. Further, in the above description, the closing device a is disposed on the upper frame 18 and the rail device b is disposed on the upper portion of the door. However, the reverse arrangement is also possible, and the same braking operation can be performed. In the above description, both the closing device a and the rail device b have been dug in the upper frame 18 and the upper part of the door 19. However, a configuration in which the upper frame 18 and the door 19 are faced is also possible. Operations can be performed.

It is the accommodation perspective view of the closing brake device for doors of the present invention. It is the accommodation top view of the closing brake device for doors of the present invention. It is the accommodation front sectional view of the closing brake device for doors of the present invention. It is an upper surface locus | trajectory figure for every fixed angle of the door and arm member in the opening / closing operation | movement of the closing brake device for doors of this invention. It is a perspective view of a slide member of the closing brake device for doors of the present invention. It is a perspective view of the linear motion damper of the closing brake device for doors of this invention. It is a top view of the state which mounted | wore the sliding member with the linear motion damper of the closing brake device for doors of this invention. It is a top view which shows the movement state per unit closing angle of the slide member in the rail main body of the closing brake device for doors of this invention. It is a perspective view of the contact member of the closing brake device for doors of the present invention. It is a locus diagram which shows the braking operation | movement by the linear motion damper and the contact member of the closing brake device for doors of this invention. It is a perspective view of the closing device of the conventional closing brake device for doors. It is an operation | movement locus | trajectory figure of the closing device of the conventional closing brake device for doors.

a closing device b rail device 1 rail body 2 slide member 3 arm member 4 linear motion damper 5 damper insertion hole 6 arm connecting portion 7 outer tube 8 rod rod 9 cap 10 abutting member 11 first abutting surface 12 second abutting Surface 13 Drive case 14 Columnar cam 15 Axle 16 Push-in bit 17 Spring member 18 Upper frame 19 Door

Claims (2)

The rail device is configured so that the slide member is movably arranged in the linear rail body, the arm member, and the driving force for rotating the arm member, so that the door can be closed. consists of a closure device and closure device and Le - Le device is mounted by distributing the door and the frame, both a - a closed braking apparatus for doors of concatenated composed arm member, a rod bar A slide member equipped with a plurality of linear motion dampers with different strokes, which is configured to provide resistance when submerged, is arranged in the rail body, and the arm connecting part of the closing device and the slide member is connected by the arm member In this configuration, a plurality of linear motion dampers move in the rail body together with the slide member when the door is opened and closed.In the final closing range of the door closing operation, the linear motion dampers have different strokes. Misaligned state Operation is obtained submerged, doors for closing braking system braking action of the door have a resistance force applied in stages at that time, characterized in that it is implemented. A contact member having a plurality of contact surfaces is arranged in the rail body so that the position can be changed, and a slide member having a plurality of linear motion dampers having different strokes is arranged in the rail body at the same time. In the final closing range of the closing operation of the door, a plurality of linear motion dampers sequentially contact the contact surface of the contact member to obtain a motion in which the linear motion dampers are further subdivided step by step. 2. The door closing brake device according to claim 1, wherein the door braking operation can be performed more precisely with a given resistance force.