JP4117276B2 - Door brake system - Google Patents

Description

  The present invention relates to a door braking device.

  Most conventional door braking devices utilize hydraulic pressure or air pressure as the basic mechanism. As the mechanism, a spring and a piston are inserted into the cylinder, the pinion is rotated by the rotation of the arm interlocked with the opening and closing of the door, and the piston is linearly moved by the movement of the rack engaged with the pinion. In many cases, the oil and air filled in the cylinder flow between the two chambers separated by the flow through the orifice to apply a load. The feature of this mechanism is that when the door is closed, it can be surely decelerated to a low speed and then slowly closed to the end. However, a similar closing action can be obtained. It also has a mechanism that can change the flow rate of flowing through the orifice when the door is opened and closed, so that a light load is obtained when the door is opened and a large load is obtained when the door is closed.

  In these conventional types, the brake device main body is attached to the door, the two arms are connected in a folded state, one end of the two connected arms is attached to the upper frame, and the other end is attached to the brake device main body. A structure that converts the movement of the angle of the arm with opening and closing of the arm into a moving movement of the piston, and a single arm that has one end of the brake device body mounted on the door so as to be rotatable in the horizontal direction, and the tip is connected to the piston There are roughly two types: a structure in which the end of the frame is pivotably mounted on a frame body, and the arm moves with a piston in a straight tube cylinder as the door is opened and closed. Many improvements on the basis of the type corresponding to the former are disclosed in JP 2000-192726 A and JP 2001-303847 A, and the type corresponding to the latter is disclosed in JP 2003-193740 A and the like. Are disclosed in large numbers.

Many door closing devices that do not use hydraulic pressure, air pressure, etc. have been proposed. Japanese Patent Application Laid-Open Nos. 2000-45624 and 2001-288156 disclose examples of a structure that pulls the door only by the force of a spring. Is disclosed.
JP 2000-192726 A JP 2001-303847 A JP 2003-193740 A JP 2000-45624 A JP 2001-288156 A

  However, although the hydraulic type described above has excellent performance, it is necessary to securely 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 very strong spring is required to rotate the pinion connected to the arm end on the brake device body side at the fulcrum position, and a high-strength rack or pinion that can handle the above strength is also required. Must be built in. As a result, the brake device as a whole has a considerably large shape, lacks compactness in size, and is not preferable in terms of design. Therefore, recently, there is a concern that it is difficult to adapt to a conshield type that is built in a door or a frame and is not exposed to the outside.

  In addition, although the mechanism itself using air pressure can be slightly simplified as compared with a hydraulic type, the noise during the movement of air always remains a problem that is difficult to completely eliminate. Furthermore, since air that is easily compressed is used, the cross-sectional area of the cylinder is required more than the hydraulic type, and the condition is further worse in terms of compactness. Therefore, it is assumed that the structure built in the thickness direction of the upper frame or the door is almost impossible. In addition, many of these pneumatic types use only one arm as described above, and when they are externally attached (impositioned), the maximum opening angle of the door can be opened only to a degree slightly exceeding 90 degrees. At present, it is not used so much because it does not meet the requirement of opening up to about 165 degrees without reducing the opening size of the frame itself in the current indoor door or the like.

  Here, when a spring is used 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 the door is opened only slightly. . Further, when no load is applied at the time of closing, inertia force is also applied from the middle of closing. Accordingly, most of the braking devices that do not use hydraulic pressure or air pressure described above change the speed at the final stage of complete closing depending on the degree of door opening. As a result, it is an ideal door opening and closing operation, regardless of the closing speed of the door body, always decelerating to a very slow speed one step before the complete closing, and then slowly closing to the end without stopping. It is difficult to think that it is functionally satisfactory. The most important point to be solved here is that the closing speed is too high when closing from a wide open state, so a deceleration operation at the final stage is necessary, and the closing force from a slightly open state is small. If it has a decelerating action, it will stop without stopping, and it will be necessary to have a mechanism that can handle this conflicting phenomenon.

  Also, the door braking device configured to fold the two arms basically has left and right sides, and it can be used for both left and right by performing a plurality of operations such as removing the arm and inverting the braking device body. . In addition, a brake system that can handle double doors with a central suspension such as a floor hinge is not yet available as a simple type with an arm system that is attached to the upper part of the door, and can be used for a double door for indoor use that is excellent for wheelchairs. Realization of a braking device is also desired.

  The present invention has been made to solve the above-mentioned problems, and is based on the premise that it can be formed in a relatively simple and compact manner without using a complicated hydraulic or pneumatic mechanism. Proportionally stepless deceleration amount can be obtained, and at the final stage of closing, it is always decelerated once to a predetermined low speed, and it can be moved slowly and completely without stopping and opened up to about 180 degrees. Provided is a door braking device that has a function, and can be completely used for both left and right, and can be mounted on a double-opening type door so that the same braking operation can be obtained regardless of which direction it is opened. With the goal.

  In the present invention, the following technical means are provided to solve the above problems. First, a linear inner arm and an outer arm are provided, a rack is placed on one of the two arms, and the speed reduction member is linked to the gear on the other arm and a constant load is applied when the gear rotates. Install in the state assembled to the member. Then, the inner arm is inserted so as to expand and contract by linearly moving in the outer arm, and the closing spring is always biased in a direction in which both arms overlap. An attachment member is attached to the end portion of the arms that do not overlap, and the attachment members of both arms are distributed to the upper frame or the upper part of the door and attached rotatably. Then, both arms are expanded and contracted while rotating by the door opening / closing operation. In this operation, when the door is closed, both arms are overlapped with each other so that the total length is the shortest, and both arms are extended as the door is opened.

  Any mechanism for generating a constant load by rotating the gear of the speed reduction member may be used, but a plurality of disc spring washers are formed by a washer-like member made of a material having excellent wear resistance. A structure such as a torque hinge (swivel hinge) that applies a load during rotation using the pressing force and frictional force of the spring, which is assembled so as to rotate in conjunction with the gear, A high silicon oil and blade-shaped member is housed and sealed with a 0-ring. When the gear rotates, the blade-shaped member rotates in conjunction with it, and a rotary is applied by rotating while pushing away the oil. A configuration like a damper is suitable. When this rotary damper is used, it may be the simplest and cheapest that applies the same load regardless of which direction it is rotated.

  Here, as the braking operation at the time of closing, the speed of the door is reduced by the load generated at the time when the rack and the gear are meshed, but two configurations are possible from the above similar form. The first configuration is described below. First, when the gear is mounted in the arm together with the case member, the arm is set so that it can move in the width direction of the rack only for a certain distance, and the gear and the rack are brought close to each other at the latter half position when the door is closed. The position of both is set in advance. Then, an engaging means for forcibly moving the gear to the rack side and meshing with the rack at a predetermined angular position during the door closing operation is provided. Further, a disengagement means for disengaging the gear from the rack at a stage where the door is continuously closed while being decelerated by the load of the deceleration member and reaches a predetermined low speed is provided. Here, the engaging means and the disengaging means are collectively referred to as engaging / disengaging operation. Further, when the door is opened from the closed state, the gear and the rack are not engaged with each other, and the load due to the speed reduction member is not generated.

  In the first configuration, the engagement / disengagement operation having the engagement means and the disengagement device is very important. However, since the engagement / disengagement operation can be obtained by various means, the main configuration will be described below. To do. First, as a first configuration, a rotating member having a protruding portion is provided, and is rotatably assembled to the case member with a rotating shaft. At this time, the gear and the speed reduction member are incorporated on one side of the rotating member with the rotation shaft interposed therebetween, and the protruding portion is formed on the opposite side. Next, a detaching spring is inserted between the case member and the rotating member so that the force is always applied in the direction in which the gear is separated from the rack. Then, a case member is attached to one arm, a rack is attached to the other arm, and a protruding contact portion is attached to a position slightly ahead of the rack.

  At this time, if the axis of the gear is up and down and the rack is placed sideways, the gear and the rack are positioned on the same horizontal plane, and the movement operation of the gear is a rotation operation on the same horizontal plane. Then, the case member and the rack position move due to the expansion and contraction movement of the arm in conjunction with the closing operation of the door, the contact member and the protruding portion of the rotation member abut at a predetermined angular position, the rotation member rotates, and the gear rotates with the rack. When engaged and further moved, both are separated by the release spring. Also, the gear axis is sideways and the rack is arranged vertically, the gear and the rack are arranged in the vertical position on the same plane parallel to the door surface, and the gear and rack are rotated by the rotation of the rotating member on the plane parallel to the door. The structure which engages / disengages may be sufficient.

  As the next configuration to obtain the engagement / disengagement operation, the gear and the projecting portion are arranged separately on both sides of the seesaw incorporated in the case member, the gear axis is vertically and the rack is lateral, and the gear and rack are vertically A configuration is possible in which the gear is moved up and down by the seesaw operation by the contact between the contact member and the projecting member, and is engaged with and disengaged from the rack. As another configuration, a configuration in which the moving pieces having a plurality of inclined surfaces are pressed against each other by the contact between the contact member and the protruding portion to move the gear in the vertical direction is also possible.

  The above is a configuration in which the engagement operation is obtained starting from the contact between the contact member and the protruding portion. However, as another means, the magnet and the metal piece attracted by the magnet are arranged in the vicinity of the gear and the gear. It is also very simple to use an operation that is first arranged in the vicinity of the rack end position facing the surface and attracted by a magnet. The gear moving operation at this time may be a linear moving operation in the mutual attracting direction, but using each moving operation by the rotating member described above, the starting operation is not the contact between the contact member and the protruding portion, but the magnet is attracted. It is also possible to implement with force. The configuration using this magnet is advantageous in that it does not require a protruding portion and a contact member, and is less likely to generate a collision sound or vibration.

  As the detaching means, in the case of using a rotating member, a detaching spring is attached between the rotating member and the case member, and the gear is always urged in the direction of detaching from the rack, or on both sides with the rotating shaft of the rotating member interposed therebetween. A configuration using a dropping operation by its own weight in a weight balance is preferable. In the disengagement means when the seesaw operation or the moving piece having a plurality of inclined surfaces is used for the engagement / disengagement operation, it is preferable to use a drop operation due to the weight of the gear portion. Even when a magnet is used, the operation of dropping by the weight of the gear portion at the stage where the magnet and the metal piece are separated by the subsequent movement of the slide member and the attractive force is reduced is simple. Further, the dropping operation by the weight of the gear and the detaching spring may be used in combination as appropriate.

  Next, the braking operation by opening and closing the door in the first configuration having the engagement / disengagement mechanism will be described. First, when the door is closed from a state where it is largely opened, the door is attracted by the closing spring and is closed at a stretch to a predetermined angle, and the protruding portion of the rotating member comes into contact with the contact member at a predetermined angle position so that the gear rotates. The operation is to rotate to the rack side and engage with the rack. As a result, the rack and gears mesh with each other, and the speed of the door is reduced relatively abruptly by the load of the speed reduction member. Further, at the initial stage of deceleration, when the distance is further moved, the protruding portion is detached from the contact member, and thereafter, a force to remove the gear from the rack is applied by the detaching means. However, in this engaged state, a frictional force for deceleration acts on the contact point between the gear and the rack, and this frictional force becomes stronger as the door speed and inertial force are larger, and becomes weaker as the speed becomes slower. Go. Therefore, even during the deceleration operation, when the door speed or inertia force is still high, the gear does not separate from the rack due to the frictional force between the gear and the rack, and the door closing speed is reduced, which occurs at the contact between the gear and the rack. When the frictional force becomes smaller than the force of the separating means, the gear and the rack are detached, and the deceleration operation is finished.

  By arbitrarily setting the conditions for separating the gear and the rack, it is possible to obtain an operation in which the door is once decelerated to a relatively slow predetermined speed and then gently closed as it is. In other words, when the door speed is very high, the distance between the gear and the rack becomes longer, and the overall deceleration amount increases accordingly. Conversely, when the door speed is slow, the distance between the gear and the rack becomes shorter. This is because the overall deceleration amount is also reduced. Therefore, the amount of deceleration proportional to the size of the closing speed can be obtained, the speed at the final stage of closing can be made constant regardless of the closing condition, and the door closing operation is very excellent. It can be realized.

  Further, when the door is closed, the rack and the gear are surely in the detached state, so that the load on the speed reduction member is not applied at the first stage of opening the door. The projecting portion abuts against the abutting member in the middle of opening, and the rotating member rotates once. However, the position of the case member at this time is the position that has already passed through the rack, so that the engaging operation is not performed. That is, in the opening operation, no load is applied by the speed reduction member. Therefore, as described above, the speed reduction member may be simple and inexpensive that generates the same load regardless of which direction the interlocked gear rotates.

  Next, a second configuration in the same similar form will be described. Since the first configuration is an operation of decelerating to some extent within a limited predetermined angle range in the second half of the closing, the length of the rack may be relatively short, whereas in the second configuration, the rail member A long continuous rack is mounted inside, and the gear and the speed reducer are directly fixed to the slide member. Here, the mechanism of the speed reducer may be the same as described above. Then, the gear and the rack are arranged so that the gear and the rack are always engaged at a wide angle almost in the entire range where the door opens and closes, and the closing spring tries to close the door due to the load generated by the speed reduction member when the gear rotates. Set so that it is always slightly smaller than the force. By configuring in this way, the operation of closing the door to the end at a low speed without stopping in the middle while suppressing the inertial force that gradually increases when closing the door with the deceleration member is obtained. It is done. In other words, even when the door is wide open, the door is slowly and gradually closed to the end.

  In this second configuration, if the speed reducing member that applies the same load in both directions of rotation described above is used, the gear rotates when the door is opened and a load is generated, which may increase the opening operation. Is done. Therefore, a gear is used to generate a load in the direction of rotation due to the engagement with the rack when closing the door, using a speed reducing member that generates a load when rotating in only one direction and free when rotating in the reverse direction. It is good to comprise so that a load may not generate | occur | produce by rotation in the reverse direction by arrangement | positioning a rack and engaging with the rack at the time of opening a door.

  Next, the expansion / contraction operation of both arms accompanying the opening / closing of the door and the movement distance per unit angle will be described. The angle during which the door opens up to 90 degrees is set, for example, every 15 degrees, and when the movement distance of both arms per unit angle is measured, the overall tendency is that the movement distance of expansion and contraction increases as the opening angle increases. Although the degree gradually increases, the degree of change changes finely, and the expansion / contraction movement is performed by substantially the same distance from the 90 degree open state to 45 degrees. Thereafter, the expansion / contraction distance per unit angle gradually decreases, 15 The moving distance from the degree to the complete closing is very small. Further, when the door is held by a hanging metal fitting such as a hinge, the moving distance becomes extremely small at the final closing angle, and both arms hardly expand and contract.

  The expansion and contraction movement characteristics of both arms are very important, and it is necessary to take into account the balance with the closing spring used. Usually, the closing spring is generally a coil spring or a mainspring spring, and the conditions for pulling the door at the mounting position vary considerably. However, as a characteristic of the spring, the force is strong when it is greatly extended, and the force is weak when the extended distance is small. As for the mounting position, it is common to incorporate a closing spring in both arms and pull it, but it is placed at a position different from the braking device that pulls the hanging surface of the door against the vertical frame on the hanging side. It is also possible to configure.

  Therefore, in the configuration having the engagement / disengagement mechanism in the first configuration, it is necessary to make the load of the deceleration member relatively large in order to decelerate rapidly with a short movement distance of both arms in the second half of closing, and as a whole operation The operation is such that the vehicle suddenly decelerates one step before it is completely closed and then slowly closes completely. However, at the final closing stage after the end of deceleration, it is assumed that the force of the closing spring is weakened, and it is better to use a structure that increases the closing force of this final part in order to reliably close to the end under various conditions Good. In the second configuration, the deceleration operation is continued with a weak force. When the force of the widely opened closing spring is strong, the extension movement distance is long, the overall deceleration amount becomes large, and the closing spring force becomes weak. In the second half of the closing stage, the extension / contraction movement distance of both arms tends to be short and the overall deceleration amount tends to be small, so that a slow closing operation at a relatively same speed can be obtained. However, at the final closing stage, the angle of both arms and the door angle become very small, and the force applied in the closing direction is extremely weakened. Therefore, it is assumed that a configuration that increases the closing force of the same final part is still necessary. .

  As means for increasing the closing force in the latter half of the closing stage, first, an attachment member at one of the arm ends is formed as a substantially rectangular interlocking piece, and the interlocking piece is set to rotate as the door is opened and closed. Further, a closing force enhancing case is provided, and a pushing member with a flat front surface and a final closing force enhancing spring are inserted, and the pushing member is urged to be pressed against the interlocking piece by the final closing force enhancing spring to thereby provide a final closing force enhancing device. Constitute. Then, the interlocking piece tip surface and the front surface of the push-in member can be held at a position where the door is closed, and when the door is opened, the corner of the interlocking piece pushes the push-in member to compress the final closing force enhancing spring. It is possible to increase the closing force of the door.

  In general, it is ideal that the door for the room partition can be opened up to 180 degrees, and at least it can be opened up to about 165 degrees without interfering with the inner dimension between the left and right doors which is the maximum opening dimension. . Therefore, a 180 degree opening case with a long hole is provided, and the attachment member of the arm end is connected to the 180 degree opening case through the long hole with a connecting pin, and the connecting pin is further drawn toward the door end side. The pulling spring is biased to form a 180 degree opening device. At this time, the urging force of the connecting pin pulling spring is set to be stronger than the urging force when the closing spring is extended to the maximum. Then, when the door is further opened beyond the 90 ° opening position, the connecting pin moves along with the arm to the suspension side while extending the connecting pin pulling spring along the long hole, and the door is opened to 180 °. It becomes possible to do.

  In addition, since the expansion / contraction movement operation of both arms is a linear movement, the braking device itself does not have a left / right hand. Therefore, it is possible to adapt to a double-open door that can be opened 90 degrees in both directions of the indoor / outdoor direction, in which the door is suspended at the center position with respect to the frame. In addition, the built-in type or door that digs into either the upper frame or the upper part of the door and incorporates both arms, and the door surface or the upper frame surface is flush with the side of the arm when the door is closed. It can be used for both the imposition type that is exposed and attached to the surface of the upper frame.

  Since the closing spring is always urged in the closing direction of the door, the gear and the rack are engaged in the latter half of the closing to obtain a deceleration operation, and the engagement / disengagement mechanism is provided to release after the deceleration to a predetermined speed. By arbitrarily setting the position at which this deceleration operation starts and the speed at which it is disengaged, a deceleration amount proportional to the magnitude of the closing speed can be obtained, and as a result, the door is set to a relatively slow predetermined speed under any closing conditions. It is possible to realize an ideal closing operation that once decelerates to a gradual time and then gently closes as it is.

  Further, when the door is closed, the rack and the gear are surely separated from each other. In the opening operation, the gear and the rack are not engaged with each other, so that the speed reduction member is not loaded. Therefore, the door can be opened with a light force. In addition, it is possible to use a simple and inexpensive speed reducing member that generates the same load regardless of which direction the gear rotates.

  According to the ninth and tenth aspects of the present invention, the load generated by the speed reduction member when the gear rotates is set so as to be always slightly smaller than the force of the closing spring member, and the gear is set at a wide angle over almost the entire region where the door opens and closes. Since the rack always engages, the inertial force that gradually increases when the door is closed is suppressed by the deceleration member, and it is comparatively from the beginning to the end without stopping halfway. The operation of closing the door at a low speed is obtained.

  The position where the gears in both arms engage with the rack and the load is generated by the speed reduction member is far away from the door suspension side to the door end side, and the gear engages with the rack. In this state, since the vehicle gradually decelerates while moving a certain distance, the load at the time of deceleration will be distributed and received at a certain moving distance, and the load per unit rotation angle required by the deceleration member is so strong It is possible even if it is not a thing.

  In addition, since a closing force reinforcement device was installed to attach an approximately rectangular interlocking piece to the end of the arm and urged the pushing member against the interlocking piece with the final closing force enhancing spring, the corner of the interlocking piece when the door was opened This pushes the push-in member and compresses the final closing force-enhancing spring, thereby increasing the force for pulling the door at the closing stage and holding the door in the closed state.

  A 180-degree opening case with a long hole is provided, one end of the arm is connected to the 180-degree opening case with a connecting pin through the long hole, and the connecting pin pulling spring is urged to pull the connecting pin further When the 180 degree opening device is used together, when the door is further opened from the 90 degree opening position, the connecting pin moves together with the arm toward the suspension side while extending the connecting pin pulling spring along the long hole. As a result, the door can be opened to 90 degrees or more and further to 180 degrees.

  Since the expansion / contraction movement operation of both arms is a linear motion, the braking device itself is used for both right and left. Therefore, in the case of imposition, it is possible to perform construction completely for both left and right. The digging type can also be installed on double doors that can be opened 90 degrees in both directions outside the indoor room where the door is suspended at the center of the frame. In this case, the door can be opened on either side. The same closing action will be obtained.

  It has a simple configuration with only two arm members, a case member incorporating a speed reduction member having a gear and a rotating member, and a closing spring, and can be provided at low cost with a small number of parts. In addition, if the size of the deceleration member is made more compact with a certain load secured, the arm itself can be made very thin, and the design can be improved even when it is faced to the door. . Therefore, it can be used not only for doors but also for all open doors such as casement windows, storage boxes and furniture doors. In the built-in type, when the door is closed, the door surface and the upper frame surface are flush with the front of the arm, and the design can be further improved.

  Embodiments of a door braking device according to the present invention will be described below with reference to the drawings. 1 to 25 show a first embodiment of the present invention. FIG. 1 digs an upper part of an upper frame 31 of a door, and attaches a mounting member 14 at one end of a braking device a to the upper frame 31 of a door 32. It is the accommodation type accommodation perspective view which shows the state which attached the attachment member 14 of the other end to the upper part rotatably, and opened the door 32. FIG. Accordingly, the braking device a rotates and moves in the horizontal direction while expanding and contracting at the upper part of the door by opening and closing the door 32. Further, an imposition type in which the braking device a is attached to the front of the upper frame 31 and the upper part of the door 32 without digging into the door 32 and the upper frame 31 is possible. Exactly the same.

  As shown in FIG. 2, the braking device a is composed of two elongated outer arms 1 and inner arms 2 having a C-shaped cross section or a square pipe shape, and the inner arm 2 is inserted into the outer arm 1. Make sure that it can be stretched and retracted. Then, both arms are connected by a closing spring 3 and are set so as to be always biased in a direction of overlapping and contracting. Next, the rack 4 is mounted on one side surface of the inner arm 2, and the contact member 5 is further mounted at a position separated from the end of the rack 4 by a certain distance. A reduction member 8 that generates a load in conjunction with the rotation of the gear 7, a rotation member 9, and an engagement / disengagement device b in which a release spring 10 is incorporated in a box-shaped case member 11 is mounted inside the outer arm 1. To do. FIG. 2 shows a state in which both arms are extended to the maximum, and a stopper is provided so as not to extend further and come off.

  3 is a top view of the engagement / disengagement device b, and FIG. 4 is a side view. As shown in FIG. 3 and FIG. 4, the speed reduction member 8 interlocked with the gear 7 is fitted and fixed so that the gear 7 protrudes from the top surface of the rotation member 9 on one side of the rotation shaft 13 of the rotation member 9. A protruding portion 12 is formed on the opposite side. The rotating member 9 is mounted on the rotating shaft 13 in a state where the rotating member 9 can rotate in the horizontal direction with respect to the case member 11, and the protruding portion 12 always protrudes from the case member 11 and the gear 7 is connected to the case member 11. Energize in the direction to be stored inside. FIG. 5 is a perspective view showing a state in which the gear 7 and the speed reduction member 8 are assembled into the rotating member 9. As shown in FIG. 5, the speed reduction member 8 and the gear 7 that are already assembled may be used. It is easy to fit the rotary member 9 as it is and fix it.

  Any mechanism may be used for generating a load by rotating the gear 7 of the speed reduction member 8, but a washer-shaped material having excellent wear resistance as shown in FIG. A mechanism such as a torque hinge or a swivel hinge configured to sandwich a plurality of disc spring washers and rotate in conjunction with the gear 7 and apply a load during rotation using the pressing force and friction force of the spring. Or a highly viscous silicone oil and a blade-like member inserted into the housing as shown in FIG. 5 (b) and sealed with an O-ring, and when the gear 7 rotates, this blade-like member A rotary damper that applies a load by rotating while pushing away the oil is suitable. Some of these oil-type rotary dampers have a high-grade type in which oil flows through an orifice, but this time the braking device a is the simplest and cheapest that applies the same load regardless of the direction of rotation. Good.

  6 is a top view of the inner arm 2, and FIG. 7 is a side sectional view. As shown in FIG. 7, the inner arm 2 has a mounting member 14 having a C-shaped cross section and a mounting hole at one end, and the rack 4 is disposed sideways on the inner surface on the mounting member 14 side. The abutting member 5 is arranged at a position spaced apart from 4 by a certain distance. 8 is a top view of the outer arm 1 with the engagement / disengagement device b attached thereto, and FIG. 9 is a side sectional view of the same. As shown in FIG. 9, the outer arm 1 is in the shape of a square pipe and has an attachment member 14 at one end, and the engagement / disengagement device b is fixed on the opposite side of the attachment member 14. Then, as shown in FIG. 2, the inner arm 2 is inserted into the outer arm 1 to prevent it from coming off, and the closing spring 3 is mounted in a state of being biased in the direction in which both arms are contracted.

  The closing spring 3 may be any kind of spring. However, when a long coiled spring is incorporated in both arms as the closing spring 3 as shown in FIG. 2, a considerable space is required. FIG. 10 is a side sectional view of the vicinity of the engaging / disengaging device b in a state where both arms are inserted. The contact member 5, the protruding portion 12 of the rotating member 9, and the rack 4 are arranged at the upper part of both arms, and the closing spring 3 Is inserted below, the coil-like closing spring 3 can be incorporated in a relatively compact manner. However, the pulling strength of the coil-like closing spring 3 varies considerably between the start of pulling and the state of being greatly extended. Accordingly, a mainspring spring or a coupling spring (equal load spring) having a relatively constant force is more suitable in terms of conditions, and FIG. 11 shows the braking device a when a coupling spring is used as the closing spring 3. It is a perspective view.

  Next, as shown in FIG. 1, when the attachment members 14 at both ends of the braking device a are distributed and attached to the door 32 and the upper frame 31, the braking device a is expanded and contracted while the angle of the braking device a is changed according to the opening and closing of the door 32. become. At this time, the door 32 is set in a closed state when both arms are contracted the most, and is set so as to extend the longest when the door 32 is opened 90 degrees. Therefore, the closing spring 3 has a role of closing the door 32 by the action of pulling both arms. Here, in the first embodiment, the expansion / contraction movement distance of both arms per unit angle when the door 32 opens and closes is important, and the locus is shown in FIG. 12 as a schematic diagram.

  FIG. 12 shows the position of the braking device a every 15 degrees from the closed state of the door 32 to the opened state of 90 degrees. Here, when the length of the braking device a according to the opening / closing angle of the door 32 with 15 degrees as one unit is displayed as A to G from the most contracted state, the expansion / contraction movement distance per unit angle is B− from the smaller opening angle. A to G-F can be calculated, and this distance is largest in F-E and gradually decreases toward B-A. The reason why G-F is slightly smaller than F-E is that the hinge axis which is the center of rotation of the door 32 is taken out as shown in FIG. 12, and B-A is extremely small. This also has an effect.

  Therefore, when the door 32 is opened and closed, both arms expand and contract along the trajectory of FIG. 12, and the operation of the engaging / disengaging device b of the braking device a and the rack 4 and the contact member 5 at that time will be described in order with reference to FIG. To do. In FIG. 13, the closing spring 3, the upper frame 31, and the door 32 of the braking device a are excluded in order to make the drawing easier to understand. FIG. 13A shows a state in which both arms are most extended when the door 32 is opened 90 degrees, and the engagement / disengagement device b, the contact member 5 and the rack 4 are arranged far apart. At this time, the rotating member 9 of the engagement / disengagement device b is biased by the detaching spring 10 so that the gear 7 is submerged in the case member 11, and the protruding portion 12 protrudes from the case member 11. When the door 32 is freed from this state, both arms are drawn and contracted by the closing spring 3 and simultaneously the door 32 is closed. In the initial closing operation from the 90 degree open state, no load is applied, and the engaging / disengaging device b of the outer arm 1 approaches the rack 4 of the inner arm 2 and the abutting member 5 at the front side thereof.

  Then, the protruding portion 12 of the engagement / disengagement device b comes into contact with the contact member 5 at the position shown in FIG. 13B, and the rotating member 9 is pushed to forcibly rotate against the detachment spring 10. Then, as shown in FIG. 13C, the gear 7 is engaged with the rack 4, and the speed reduction operation is started by the rotation of the gear 7. Here, in order to reduce the collision sound between the contact member 5 and the protruding portion 12, it is preferable to apply a soft material such as rubber or elastomer to one of the contact surfaces 6 to reduce the impact. Further, a setting is made so that the deceleration operation by the engagement of the gear 7 and the rack 4 has already started at the final position where the contact surface 6 of the contact member 5 and the protruding portion 12 are in contact with each other as shown in FIG. Keep it. That is, the gear 7 and the rack 4 are always engaged once regardless of the opening angle of the door 32 and the closing speed.

  At the stage of FIG. 13 (c), a frictional force is generated at the contact point between the gear 7 and the rack 4 due to the load of the speed reduction member 8, and this frictional force is applied in a direction to further rotate the rotating member 9 in the same direction. Thereafter, when the door 32 is further closed at a minute angle, the engaging / disengaging device b is also moved by a minute distance, and the protruding portion 12 is separated from the contact surface 6 of the contact member 5. Then, from this stage, force is applied to the rotating member 9 in the direction in which the gear 7 is detached from the rack 4 by the separating spring 10. However, a frictional force is acting on the contact point between the gear 7 and the rack 4, and this frictional force becomes stronger as the closing speed and inertial force of the door 32 are larger, and becomes weaker as the speed and inertial force become smaller. Therefore, even if the speed is reduced to some extent, the gear 7 does not detach from the rack 4 due to frictional force when the closing speed of the door 32, that is, the moving speed of the engaging / disengaging device b is still high. Then, as shown in FIG. 13 (d), the door 32 is further closed while being decelerated, and the friction force generated in the gear 7 and the rack 4 becomes smaller than the urging force of the separation spring 10 at a predetermined low speed. Then, as shown in FIG. 13E, the gear 7 is detached from the rack 4 and the deceleration operation is completed. Even at this stage, the door 32 is still closed gradually, and the pulling force by the closing spring 3 is still applied, so that the door 32 continues to be completely closed thereafter as shown in FIG.

  That is, when the door 32 is opened wide and then closed, the closing speed is high and inertial force is applied. Therefore, the distance between the gear 7 and the rack 4 is increased, and the overall deceleration amount is also increased. When the door 32 is closed after being slightly opened, the closing speed and the inertial force are low, and the friction between the gear 7 and the rack 4 is weak, so that they are separated immediately after the engagement, and the overall deceleration amount becomes small. Therefore, the amount of deceleration corresponding to the speed of the door 32 is obtained, and it is possible to realize the operation of decelerating to a predetermined low speed regardless of the opening angle, and then slowly and completely closing. Further, by appropriately setting the position of the contact member 5 and the length of the rack 4, the deceleration start angle of the door 32 can be changed, and further, by changing the strength of the detaching spring 10, the gear can be changed. It is also possible to arbitrarily set the speed at which 7 and the rack 4 are separated, that is, the closing speed at the final stage of the door 32.

  Next, the opening operation of the door 32 from the closed state will be described. In the closed state shown in FIG. 13 (f), the rack 4 and the gear 7 are surely separated from each other. Therefore, when the door 32 is opened, the load on the speed reduction member 8 is not applied. However, in the vicinity of FIG. 13C in the initial stage of opening, the opposite surface of the protruding portion 12 comes into contact with the contact member 5 and the rotating member 9 rotates. However, the position of the engagement / disengagement device b at this time is the position that has already passed through the rack 4, and the engagement operation is performed only at the extreme moment in FIG. 13C, and the deceleration operation is not performed as it is. Further, if it is desired to eliminate even the engagement only at this moment, although not shown, the contact member 5 is configured to be slidable with an extremely light force only in the direction opposite to the rack 4 side. The contact member 5 is moved at the stage where the opposite surface of the protruding portion 12 contacts when opened, and the rotation member 9 rotates at a position where the gear 7 has completely passed the rack 4, and then the contact member 5 reaches the reference position. It is configured so that it returns naturally, or the contact member 5 is tilted only in one direction, and it does not fall in the contact operation at the time of closing, but it is tilted only at the time of opening and the gear 7 and the rack 4 are engaged. It is advisable to add a configuration that avoids the operation.

  By configuring as described above, it is possible to prevent the speed reduction member 8 from being loaded during the opening operation. Accordingly, the speed reduction member 8 can be a simple and inexpensive one that generates the same load regardless of which direction the gear 7 rotates. In this initial stage of opening, as described with reference to FIG. 12, the extension and movement distance of both arms per unit opening angle is very short, and the force applied to the initial stage is small even in general spring characteristics. The force to open the door 32 while extending the closing spring 3 is very light.

  In other words, in the configuration of the first embodiment, it is most important to use the engagement / disengagement mechanism of the gear 7 and the rack 4. In the above description, the rotation operation of the rotating member 9 is used for the engagement / disengagement mechanism. The detaching spring 10 was used as the urging force for this purpose. However, this engagement / disengagement mechanism may have any other configuration. Next, the other engagement / disengagement mechanisms will be described with reference to FIGS. FIG. 14 shows the rotation direction of the rotary member 9 in the case member 11 set in the vertical direction (on a plane parallel to the surface of the door 32). Even in this configuration, the detaching spring 10 may be used as the detaching means as described above. However, since the rotating operation of the rotating member 9 is in the vertical direction, the protruding portion 12 sandwiching the rotating shaft 13 as shown in FIG. A heavy weight member 15 is mounted on the side, the weight balance on both sides of the rotating member 9 across the rotating shaft 13 is set so that the protruding portion 12 side is much heavier, and the detaching means is dropped and rotated by its own weight. It is also possible to implement by operation. This difference in the rotation direction of the rotating member 9 does not affect the deceleration operation. However, the horizontal rotation operation of the rotating member 9 requires a certain width in the rotating direction, and thus has an influence on the size. Yes, in the case of imposing the braking device a on the front surface of the door 32, it is better to design the structure in which the rotation direction of the rotary member 9 is set up and down and the width in the vertical direction is larger than the shape having the width in the horizontal direction. Is considered advantageous.

  As another engagement / disengagement mechanism, the gear 7 is horizontally arranged such that the axis is in the vertical direction, the rack 4 is mounted sideways, and the rack 4 and the gear 7 are shifted vertically in the detached state. Both are arranged so that A configuration is possible in which the gear 7 moves up and down and engages with the rack 4 by the contact between the protruding portion 12 and the contact member 5. An example of a configuration for moving the gear 7 up and down is shown in FIG. 15. A moving piece 17 having a plurality of inclined surfaces 16 is arranged face to face, and one of the moving pieces 17 has a protruding portion 12. Is provided. Then, as shown in FIG. 15A, when the projecting portion 12 is arranged so as to contact the contact member 5 by the movement of both arms, the projecting portion 12 and the contact member as shown in FIG. 5, the inclined surfaces 16 of the movable pieces 17 are pressed against each other and interlocked to move the movable piece 17 equipped with the gear 7 up and down. Although not shown, the gear 7 and the protruding portion 12 are provided at both ends of the seesaw. Similarly, the axis of the gear 7 is arranged vertically and the rack 4 is arranged sideways, and the gear 7 and the rack 4 are slightly separated in the vertical direction. The gear 7 may be moved up and down by the seesaw operation by the contact between the contact member 5 and the projecting portion 12 to be engaged with and disengaged from the rack 4.

  16 and 17 show still another engagement / disengagement mechanism. This engagement / disengagement mechanism is characterized by using a magnet 18 and a metal piece 19 attracted by the magnet 18, and in the vicinity of the gear 7 and the rack 4. The magnet 18 and the metal piece 19 are separately attached to the positions, and when they approach each other, they are attracted and engaged with each other by a magnetic force. Therefore, the abutting member 5 and the protruding portion 12 are not necessary, and it is excellent in that the collision noise and impact at the time of abutting can be eliminated. FIG. 16 is a perspective view of the engagement / disengagement device b in this configuration. A metal piece 19 is attached to the upper surface of the gear 7 and only inserted so as to move up and down in the case member 11 together with the speed reduction member 8. .

  FIG. 17 is a schematic diagram showing the operation of the engagement / disengagement mechanism using the magnet 18 and the metal piece 19. FIG. 17A shows a state in which the metal piece 19 on the upper surface of the gear 7 approaches the magnet 18 with the movement of the engagement / disengagement device b, and when both approach each other to some extent, the gear 7 is attracted directly upward, and FIG. The gear 7 and the rack 4 can be meshed as shown in FIG. The disengagement means in this engagement / disengagement mechanism can be implemented by a simple drop operation due to the weight of the gear 7 and the speed reduction member 8, and the disengagement force due to gravity is applied from the stage where the magnetic force is weakened at a position slightly moved from FIG. . The relationship between the separation force and the frictional force between the gear 7 and the rack 4 is the same as described above. If the weight of the gear 7 or the speed reduction member 8 is increased in order to adjust the speed of the door 32 at the end of the speed reduction operation, naturally Although the detachment force increases, it is preferable to increase the attractive force for the engaging operation by increasing the magnetic force accordingly. By doing so, a reliable engagement operation can always be obtained. Further, the engaging means using this magnetic force may be used for the structure of each engaging / disengaging mechanism such as the rotating operation and the seesaw operation of the rotating member 9 described above, and further, it may be used in combination with the urging force by the detaching spring 10. You may combine.

  Next, the operation when the braking device a according to the first embodiment of the present invention is mounted in a state where it is dug in front of the upper frame 31 will be described first in terms of opening and closing the door 32 up to 90 degrees. FIG. 18 is a top view of the housing, and shows a configuration in which a coil-like tension spring is incorporated in both arms as the closing spring 3 and the door 32 is closed by an operation of pulling them together. In FIG. 19, the closing spring 3 is not incorporated in both arms, and the closing spring 3 is attached to the hanging side of the vertical frame 30 and the hanging side of the door 32, which is different from the braking device a, and the door 32 is attached. The drawing structure is shown. In the structure shown in FIG. 19, the expansion and contraction of the closing spring 3 is relatively small, the door 32 can be pulled regardless of the braking device a, and a force that can be sufficiently pulled even from a small opening angle immediately before completely closing. It is an important feature that it can be obtained. Therefore, it is considered that it is easy to completely close the opening portion of the door 32 that remains slightly after the gear 7 and the rack 4 are detached. However, it is troublesome to attach the closing spring 3 separately in a location different from the braking device a, and considering simplification in terms of construction, the closing spring 3 is incorporated in both arms. Such a configuration is desirable.

  However, in the pulling operation by the closing spring 3 in the configuration shown in FIG. 18, the opening angle between the braking device a and the door 32 is very large when the door 32 is considerably closed as shown in the locus diagram of FIG. Even if the inner arm 2 is further pulled to the door tip side from this state, the force is not so much applied in the direction of closing the door 32, and the speed of the door 32 at the time of detachment by the engagement / disengagement mechanism is very slow. In the case of setting, it may not stop completely after that and may stop halfway. Furthermore, since the closing condition changes depending on the weight of the door 32 and friction such as a hinge when opening and closing, the configuration in which the closing spring 3 is incorporated in both arms shown in FIG. It is assumed that it is more certain to strengthen by force.

  Therefore, it is preferable to provide a closing force increasing device c that increases the pulling force at the final closing stage. FIG. 20 is a top view of a state in which the closing force enhancing device c is interlocked with the attachment member 14 of the outer arm 1, and FIG. 21 is a perspective view of the closing force enhancing device c. First, as shown in FIG. 21, a box-shaped closing force enhancing case 20 is provided, the tip of the attachment member 14 of the inner arm 2 is formed as a substantially rectangular interlocking piece 23, and an attachment hole is provided in the central portion to provide a shaft. It is connected with the closing force enhancing case 20 by a heart so as to be rotatable. Then, the interlocking piece 23 also rotates together with the braking device a by the opening / closing operation of the door 32. Further, a closing force enhancing spring 22 having a very strong urging force and a U-shaped pushing member 21 having a front portion or a flat surface are arranged inside the closing force enhancing case 20, and the pushing member is pushed by the closing force enhancing spring 22. 21 is assembled so that the interlocking piece 23 is always pressed, and the closing force increasing device c is configured.

  The interlocking piece 23 is provided with an interlocking piece front end surface 24 and interlocking piece corners 25 on both sides thereof. Then, as shown in FIG. 20, in the state in which the door 32 is completely closed, the interlocking piece front end surface 24 and the flat surface of the pushing member 21 face each other in close contact with each other. When the door 32 is opened from this state, the interlocking piece corner 25 rotates with the pushing member 21 together with the outer arm, and the closing force enhancing spring 22 is compressed. The degree of compression can be set by the rotation angle of the braking device a and the interlocking piece 23 and the size of the interlocking piece tip surface 24. Here, as can be seen from the locus diagram of FIG. 12 described above, the angle of the braking device a gradually increases until the door 32 opens about 45 degrees, but when it exceeds 45 degrees, the angle is almost 90 degrees. Will not change. In other words, the closing force increasing spring 22 is compressed up to about 45 degrees, and in the subsequent opening, it can be opened without increasing the compression force. Accordingly, when the door 32 is opened, the closing spring 3 requires a larger force in the second half angle range that is largely opened, but the closing force enhancing device c is lighter in the second half opening angle range. The force required for opening can be made relatively uniform over the entire angular range.

  Further, as shown in FIG. 20, the force for closing the door 32 of the closing force increasing spring 22 is always applied in the entire range where the door 32 is opened up to 90 degrees. Therefore, the closing force increasing device c is used. In such a case, the closing spring 3 may have a weaker force. Furthermore, the smaller the angle between the axis of rotation of the interlocking piece 23 and the interlocking piece corner 25, the greater the proportion of the force applied by the closing force enhancing spring 22 that biases the door 32 in the closing direction. The closing force at the final stage of closing, which is difficult to obtain with the closing spring 3 arranged in both arms, can be secured, and as a result, the closing force is very well balanced as a whole. Will be obtained.

  That is, in the conventional closing device for the door 32 in which the two arms are pulled together by the closing spring 3, a pulling force of a certain level or more is required even in the final closing stage. In spite of the fact that the force for closing from the open state is not so strong, it is necessary to use the closing spring 3 which is quite strong. However, in the configuration in which the closing force increasing device c in the braking device a according to the present invention is used together, the closing spring 3 is relatively weak because it can be carried out in a state in which the attractive force is properly allocated to the required angular range. If the closing force increasing spring 22 is set strongly, the overall configuration can be made very efficient. However, since the distance between the axial center position of the interlocking piece 23 and the interlocking piece corner 25 is not so large, if the closing force enhancing spring 22 is strengthened, a large force is applied to this portion, and the closing force enhancing device c It is important to increase the strength of itself.

  In the above description, the opening operation of the door 32 up to 90 degrees has been described. However, an indoor partition door or the like often needs to be opened up to 180 degrees. Therefore, the brake device a according to the present invention also needs to have a configuration capable of opening 180 degrees. As the means, it is simple to make the length of both arms in the most extended state, and if both arms are not fully extended at the time of opening 90 degrees, the door exceeds 90 degrees as it is. 32 can be opened. However, with this means, the braking device a itself becomes extremely long, and it is not considered to be so effective in terms of design and cost. Therefore, it is preferable that the braking device a is set to a size that can be opened up to 90 degrees and a 180-degree opening device d is separately attached.

  FIG. 22 shows the configuration of only the braking device a shown in FIG. 18 in which the closing force increasing device c is interlocked with the mounting member 14 of the outer arm 1 and the 180-degree opening device d is interlocked with the mounting member 14 of the inner arm 2. FIG. 23 is a top perspective view showing the configuration, and FIG. 23 is a perspective view of a state in which the door having the same configuration as FIG. 22 is opened. The 180-degree opening device d includes a 180-degree opening case 26 having a linear long hole 27, a connecting pin 28, and a connecting pin pulling spring 29, and the attachment member 14 of the inner arm 2 is elongated by the connecting pin 28. 27 is attached to the case 26 for opening 180 degrees and is mounted in a state of being dug in the upper part of the door 32. Further, the connecting pin pulling spring 29 is assembled in the 180 degree opening case 26 in such an arrangement that the connecting pin 28 is always pulled toward the door end side. The strength of the connecting pin pulling spring 29 is set to be stronger than the pulling force of the closing spring 3 when it is opened 90 degrees.

  When the door 32 is opened from the above configuration, when the door is opened up to 90 degrees, the operation is the same as in FIG. FIG. 24 is a top view showing the operation of the braking device a and the 180 ° opening device d when the door 32 is opened from 90 ° to 180 °. When the door 32 is further opened from the 90 ° open position, the attachment member 14 of the inner arm 2 moves to the suspension side while extending the connecting pin pulling spring 29 along the elongated hole 27 together with the connecting pin 28, 32 can be opened up to 180 degrees. Therefore, when it is opened 90 degrees or more, the braking device a always holds the most extended state. Further, in the stage where the door 32 is closed from the stage where it is opened 90 degrees or more, the braking device a tries to contract by the closing spring 3, but the force of the connecting pin pulling spring 29 from the closing spring 3 as described above. Therefore, the operation of moving the attachment member 14 of the inner arm 2 and the connecting pin 28 in the direction of returning along the long hole 27 by the connecting pin pulling spring 29 is performed first, and the door 32 is moved. Until it closes to the 90 degree position, the braking device a will not be retracted. Therefore, it can be closed by an operation completely opposite to the operation at the time of opening, and a malfunction can be prevented.

  Further, in the first embodiment, the operation of both arms of the braking device a is a linear expansion / contraction movement, and there is no problem even if the braking device a rotates in any direction from the state in which the door 32 is closed. There is no right or left hand in a itself. Further, if the interlocking force enhancing device c is configured so that the interlocking piece 23 can rotate in both the left and right directions with respect to the closing force enhancing case 20, and the interlocking piece corner 25 is arranged symmetrically at two left and right sides, the right and left hand is eliminated. Furthermore, the 180-degree opening device d is also left-right symmetric, so that the entire braking device a including the closing force increasing device c and the 180-degree opening device d can be completely used for both left and right. Moreover, since the 180 degree | times opening apparatus d needs a certain amount of length as shown in FIG. 22, it is disadvantageous in terms of cost, and it is also troublesome to dig up the upper part of the door 32. Therefore, the 180 degree opening device d should be set to be used only when the door can be opened 180 degrees due to the door.

  In the above, as shown in FIG. 23, the closing force increasing device c connected to the outer arm 1 is attached to the upper frame 31, and the 180 degree opening device d connected to the inner arm 2 is dug into the upper portion of the door 32. In the above description, the brake device a is fitted into the digging portion of the upper frame 31 when the door 32 is closed, and the brake device a is flush with the front surface of the upper frame 31. Although not shown here, there is no particular problem even if the brake device a fits into the upper portion of the door 32 without digging the upper frame 31, and the same braking operation can be obtained. In the above description, as shown in FIG. 12, the braking device a and the door 32 are connected at a position close to the suspension side, and the braking device a and the upper frame 31 are connected at a position far from the suspension side. As the connection arrangement of the device a, the braking device a and the upper frame 31 are connected at a position close to the suspension side opposite to FIG. 12, and the braking device a and the door 32 are connected at a position far from the suspension side. An arrangement as shown in FIG. 25 is also possible.

  FIG. 25 is a schematic diagram showing the trajectory of the door 32 and the braking device a in the above-described arrangement. When the door is opened and closed, the trajectory is different from the above-mentioned trajectory that expands and contracts while the braking device a largely rotates so as to follow the door 32. . However, also in the arrangement shown in FIG. 25, the operation in which both arms extend and contract in conjunction with the opening operation of the door 32 is almost the same as described above. Here, the difference is that if the movement distance per unit angle is A to G as in FIG. 12, there is a slight difference in the movement distance in the final stage of closing of C-B or B-A. The feature is that the expansion / contraction distance from the initial stage to the opening of about 30 degrees can be made slightly larger than the arrangement shown in FIG. Therefore, although the arrangement shown in FIG. 25 is a little, the gear 7 can be engaged with the rack 4 at a relatively long distance in the final closing stage to gradually decelerate. Here, it is optional in selecting whether to engage with a short moving distance and decelerate relatively rapidly, or to engage with a long distance and decelerate moderately to some extent, and to start the deceleration operation Since the angle of 32 can be freely set according to the length of the rack 4, the closing operation may be set by appropriately using these characteristics.

  Next, a second embodiment of the present invention will be described with reference to FIGS. FIG. 26 is a top plan view of the second embodiment. In the second embodiment as well, the braking device a comprises an inner arm 2 and an outer arm 1, and a closing spring 3 is incorporated in both arms and biased in the direction in which both are pulled, and the rack 4 and gear 7 are engaged. Thus, a deceleration operation is obtained. In addition, the configuration in which the attachment member 14 at both arm ends is attached to the upper part of the door 32 and the upper frame 31 while being connected to the closing force increasing device c or the 180 degree opening device d is exactly the same as in the first embodiment. is there. However, in the second embodiment, the greatest feature is that the mechanism in both arms of the braking device a is greatly different from the operation at the time of deceleration, and no engaging / disengaging mechanism is required. The reduction gear used at this time may have the same configuration as that of the first embodiment, but the load generated with respect to the unit rotation angle of the gear 7 is set much weaker than that of the first embodiment.

  FIG. 27 is a top view of the inner arm 2 in the second embodiment, and FIG. 28 is a top view of the outer arm 1. In the second embodiment, as shown in FIG. 27, a long continuous rack 4 is mounted on almost the entire inner surface of the inner arm 2, and the contact member 5 is not required. As shown in FIG. 28, the gear 7 and the speed reduction member 8 are directly fixed so as not to move in the outer arm 1. Then, the inner arm 2 is inserted into the outer arm 1, and the gear 7 is always engaged over the entire area of the rack 4 when both are extended and contracted.

  FIG. 29 is a trajectory diagram sequentially showing the operation of both arms of the braking device a by opening and closing the door 32 in the second embodiment, and the closing spring 3, the upper frame 31, and the door 32 are shown for easy understanding. Excluded and displayed. FIG. 29A shows a 90-degree open state in which both arms are most extended, and the gear 7 and the rack 4 are greatly separated. FIG. 29 (e) shows a state in which the door 32 is completely closed and both arms are contracted most. When the door 32 is freely opened from the state where the door 32 shown in FIG. 29 (a) is largely opened, the closing operation is started by the force of the closing spring 3, and both arms are slightly contracted as shown in FIG. 29 (b). At the stage, the rack 4 and the gear 7 are engaged, and the deceleration operation is started. Further, when the door 32 is further closed, the door 32 shown in FIG. 29 (e) is completely closed through the closing state shown in FIGS. 29 (c) and 29 (d). That is, in the second embodiment, the gear 7 and the rack 4 are always engaged with each other over a very wide angle range when the door 32 is opened to perform the deceleration operation, and the door 32 is closed by the closing spring 3. This is the biggest feature.

  Accordingly, in the configuration of the second embodiment, after the door 32 is released, in order to obtain the operation of completely closing without stopping only by the force of the closing spring 3, the reduction member 8 is used at all opening angles of the door 32. It is necessary to set the generated load so that it is always slightly smaller than the force for closing the closing spring 3. Here, the amount of deceleration per unit closing angle is determined by the load of the speed reducing member 8 per unit rotation of the gear 7 and the rotational movement distance. In addition, the extension / contraction movement distance of both arms per unit closing angle of the door 32 shown in FIG. 12 is large in the angle range where the force of the closing spring 3 is relatively large and the door 32 is opened, and the opening angle is small. In the range, the force of the closing spring 3 is slightly weakened, but the expansion / contraction movement distance of both arms at this time is extremely reduced.

  In addition to the locus described above, the ratio of the force applied in the closing direction out of the urging force of the closing spring 3 becomes important. The ratio of the force actually applied in the closing direction changes depending on the angle between the door 32 and the braking device a, and this ratio changes so much from the 90 degree open state to the 45 degree open position as shown in FIG. After that, the force decreases with a relatively small change up to about 15 degrees, and the angle between the door 32 and the braking device a becomes extremely small at the stage of closing until the end after that, so the closing force is extremely small. Weaken. Accordingly, in the closing operation up to about the 30 ° opening position, the attractive force and the deceleration amount are proportional to some extent, and can be closed relatively slowly without stopping in the middle. In the final stage after that, the closing force becomes very weak, but the expansion and contraction movement distances of both arms at this time are extremely small, so the conditions will be met, and it can be barely closed as it is. It is supposed to be possible. However, since the conditions vary depending on the friction during rotation of the hinges and pivot hinges and the weight of the door 32, it is difficult to reliably close to the end under all conditions. Therefore, as shown in FIG. 26, a closing force enhancing device c similar to that of the first embodiment may be provided together. Then, the closing force at the final closing stage where the closing force is weakened most can be increased, and the closing can be more surely performed. As a result, it is possible to obtain an operation of always closing the door 32 at a relatively low speed from the state where the door 32 is largely opened, and closing it to the end without stopping on the way.

  That is, the configuration in the second embodiment is based on the inertia force of the door 32 that is gradually increased by the closing operation attracted by the closing spring 3, and the rack 4 and the gear 7 are weakly applied over almost the entire opening angle. The most important feature is that it is closed at a speed that does not stop while restrained by being always engaged. Furthermore, in the second embodiment, as shown in FIG. 26, the door 32 can be similarly opened to 180 degrees by mounting the 180 degree opening device d together. FIG. 26 shows the braking device a in the arrangement shown in FIG. 12, but in the second embodiment, the braking device a can be installed in the arrangement shown in FIG. 25 as in the first embodiment. is there.

  In the second embodiment, there is no mechanism for engaging and disengaging the rack 4 and the gear 7, and the speed reduction operation is always performed in a wide range of angles. Therefore, when the speed reduction member 8 that applies the same load by the rotation in both directions is used, the door Also when opening 32, the gear 7 rotates in the reverse direction and a load is generated, and there is a concern that the opening operation becomes heavy accordingly. Therefore, the reduction member 8 having the same configuration uses a one-way lock type in which a load is generated when rotating in only one direction and is free when rotating in the opposite direction, and the relationship between the gear 7 and the rack 4 when the door 32 is closed. It is preferable to set so that a load is generated only in the rotation direction due to the combination, and a load is not generated in the reverse rotation due to the engagement with the rack 4 when the door 32 is opened. In addition, if a reduction gear of a type in which the same load is applied by rotation in both directions is used, for example, a means is provided so that the linear movement route of the gear 7 in both arms can be shifted in the width direction and back. It is preferable that the gear 7 is configured to be engaged with the rack 4 only when moving in the direction of contracting both arms, and not to be engaged with the rack 4 when moving in the extending direction.

  Next, a third embodiment of the present invention will be described with reference to FIG. Both the first embodiment and the second embodiment have been described with the setting where the door 32 is attached to a door that opens and closes in only one direction. However, as described above, the door 32 can be completely used as a left and right. The double door that is hung at the center position relative to the body and can be opened in both the indoor and outdoor directions can be used as it is. In that case, the upper frame 31 on which the braking device a is arranged may be dug in a front-rear direction and mounted so that the braking device a can rotate in both directions from the closed state. FIG. 30 is a top view of a configuration in which the brake device a of the first embodiment is dug into a center-hung double door, and both arms extend and retract when the door 32 is opened and closed from the closed state. The same braking action can be obtained when closed.

  Normally, this type of double door is set so that it can be opened by 90 degrees in both directions. Therefore, it is not necessary to install the 180 degree opening device d. In addition, since a conventional door with a free hinge cannot be attached to a normal door stop, it is difficult to stop and hold the door 32 in the closed position. In the configuration shown in FIG. 30, the final closing force is not only increased, but the door 32 is also held in the closed position, and the door 32 can be stopped more securely in the closed position. Can be mentioned. In FIG. 30, the brake device a according to the first embodiment is indicated, but the brake device a according to the second embodiment can be adapted to the double door type according to the third embodiment.

  Next, an imposition type configuration in which the braking device of the present invention is attached to the front surface of the door 32 and the front surface of the upper frame 31 will be described as a fourth embodiment and a fifth embodiment with reference to FIGS. Although the braking device a in FIGS. 31 to 34 is shown in the configuration of the first embodiment having an engagement / disengagement mechanism, there is no problem even if the braking device a in the second embodiment is used. Here, in the case of the imposition type, there are a case where the door is attached to the door contact side position and a case where the door is attached to the opposite side, and the brake device a according to the present invention can both. Therefore, a configuration in which the braking device a is mounted on the door stop side is described as a fourth embodiment, and will be described with reference to FIGS. 31 and 32. Moreover, the structure which mounts | wears with the braking device a on the opposite side to a door stop is made into 5th embodiment, and it demonstrates with FIG. 33 and FIG.

  FIG. 31 is a perspective view of the fourth embodiment with the door 32 opened, and FIG. 32 is a top view of the same state. In the fourth embodiment, as shown in FIG. 31, the attachment member 14 of the inner arm 2 or the 180-degree opening device d is attached to the position slightly lowered from the upper part of the door 32 by imposition, and the attachment member 14 of the outer arm 1 is attached. Alternatively, the closing force increasing device c is taken out further from the lower surface of the upper frame 31 and mounted, so that when the door 32 is closed, the braking device a is parallel and horizontal with a slight gap from the door surface. Deploy. Also in the fourth embodiment, the deceleration operation of the braking device a by opening and closing the door 32 is exactly the same as in the first embodiment. However, in the fourth embodiment, even when the 180-degree opening device d is mounted, both arms of the braking device a have a trajectory that rotates at a position lower than the upper end of the door 32. At the stage, the side surface of the inner arm 2 and the door surface come into contact with each other. As a result, the maximum opening angle is limited to about 165 degrees.

  FIG. 33 is a perspective view of the fifth embodiment with the door 32 opened, and FIG. 34 is a top view of the same state. In the fifth embodiment, as shown in FIG. 33, the mounting member 14 of the inner arm 2 or the 180-degree opening device d is mounted so as to be flush with the upper end of the door 32, and the mounting member 14 of the outer arm 1 or the closing force When the reinforcing device c is mounted on the front surface of the upper frame 31 and the door 32 is closed, the vertical position of the braking device a is slightly above the upper end of the door 32 and has a slight gap with the door surface. Place them so that they are parallel and horizontal. Also in the fifth embodiment, the deceleration operation of the braking device a by opening and closing the door 32 is exactly the same as in the first embodiment. Further, in the fifth embodiment, as shown in FIG. 34, the braking device a becomes a trajectory that rotates further above the upper end of the door 32. Therefore, when the 180 degree opening device d is installed, the door is completely up to 180 degrees. 32 can be opened.

It is a perspective view of the state where the brake device of the first embodiment of the present invention was attached to the door. 1 is a perspective view of a braking device having a configuration in which a tension spring is used as a closing spring according to a first embodiment of the present invention. It is a top view of the engaging / disengaging device of the first embodiment of the present invention. It is a side view of the engagement / disengagement device of the first embodiment of the present invention. It is a perspective view of a rotation member, a reduction member, and a gear of a first embodiment of the present invention. It is a top view of the inner arm of the first embodiment of the present invention. It is side surface sectional drawing of the inner arm of 1st embodiment of this invention. It is a top view of an outer arm of a first embodiment of the present invention. It is side surface sectional drawing of the outer arm of 1st embodiment of this invention. It is side surface sectional drawing of the state which inserted the inner arm in the outer arm of 1st embodiment of this invention. 1 is a perspective view of a braking device having a configuration in which a coupling spring is used as a closing spring according to a first embodiment of the present invention. It is a schematic diagram which shows the locus | trajectory of the expansion-contraction movement by opening / closing of the door of the braking device of this invention. It is a locus | trajectory figure which shows the engagement / disengagement operation | movement of the rack and a gear by the expansion-contraction movement of both arms of 1st embodiment of this invention in order. It is a perspective view of the engagement / disengagement apparatus which has another engagement / disengagement mechanism of 1st embodiment of this invention. It is a schematic diagram which shows the engagement operation | movement of the engagement / disengagement apparatus which has another engagement / disengagement mechanism of 1st embodiment of this invention. It is a perspective view of the engagement / disengagement apparatus of the first embodiment of this invention of the structure which used the magnet for the engagement / disengagement mechanism. It is a schematic diagram which shows the engagement operation | movement of the engagement / disengagement apparatus using the magnet of 1st embodiment of this invention. It is a top view of the state which equipped the brake device of 1st embodiment of this invention with the door. It is a top view of the structure which has arrange | positioned the spring for closure of the braking device of this invention in the door bottom surface and vertical frame of the door. It is the accommodation top view of the closure power increase device of a first embodiment of the present invention. It is a perspective view of a closure power increase device of a first embodiment of the present invention. It is a top view of the state which mounted | wore the brake device, the closing force increase apparatus, and the 180 degree | times opening apparatus of 1st embodiment of this invention. 1 is a perspective view of a first embodiment of the present invention in a state in which a braking device, a closing force enhancing device, and a 180-degree opening device are mounted on a door. It is an upper surface locus diagram which shows operation | movement of the 180 degree | times opening apparatus of 1st embodiment of this invention. It is a schematic diagram which shows the locus | trajectory of the expansion-contraction movement by opening / closing of the door in another arrangement | positioning of the braking device of this invention. It is a top view of the state which mounted | wore the door with the braking device of 2nd embodiment of this invention. It is a top view of an inner arm of a second embodiment of the present invention. It is a top view of an outer arm of a second embodiment of the present invention. It is a locus | trajectory figure which shows the engagement operation | movement of the rack and gearwheel by the expansion-contraction movement of both arms of 2nd embodiment of this invention in order. It is a top surface locus diagram of a third embodiment of the present invention. It is the accommodation perspective view of 4th embodiment of this invention. It is the accommodation top view of 4th embodiment of this invention. It is the accommodation perspective view of 5th embodiment of this invention. It is the accommodation top view of 5th embodiment of this invention.

Explanation of symbols

a braking device b engaging / disengaging device c closing force increasing device d 180-degree opening device 1 outer arm 2 inner arm 3 closing spring 4 rack 5 abutting member 6 abutting surface 7 gear 8 deceleration member 9 rotating member 10 detaching spring 11 Case member 12 Protruding portion 13 Rotating shaft 14 Mounting member 15 Weight member 16 Inclined surface 17 Moving piece 18 Magnet 19 Metal piece 20 Closing force increasing case 21 Pushing member 22 Closing force enhancing spring 23 Linking piece 24 Linking piece tip surface 25 Linking piece corner 26 180 degree opening case 27 long hole 28 connecting pin 29 connecting pin pulling spring 30 vertical frame 31 upper frame 32 door

Claims (11)

A device that brakes the speed when closing a door, and has a linear outer arm and an inner arm, a rack is arranged on one of both arms, and a gear and a speed reduction member are mounted on the other. The load is applied by the speed reduction member by the engagement between the gear and the rack, the inner arm is inserted into the outer arm, and a closing spring is attached so that a force is applied in the door closing direction. Attached to the upper frame or the upper part of the door, the mounting members at the ends of both arms are attached to the upper frame and can be freely rotated. Engaging means for forcibly moving the gear to the rack side and engaging with the rack, and detaching means for releasing the gear from the rack when the door closes further while being decelerated by the load of the speed reducing member and reaches a predetermined low speed. An engagement / disengagement mechanism having In operation of opening the door et door braking device characterized by comprising means for gear and rack does not engage. The engagement / disengagement mechanism having the engagement means and the disengagement means includes a rotation member and a case member, a gear and a speed reduction member are incorporated on one side across the rotation shaft of the rotation member, and a protruding portion is formed on the opposite side. An engagement / disengagement device in which a rotation member is rotatably attached to a case member with a disengagement means that applies force in a direction in which the gear always leaves from the side is disposed in one arm, Furthermore, a contact member is disposed at a position spaced apart from the end of the rack mounted in the other arm, and the contact member and the protruding portion are brought into contact with each other at a predetermined position by the expansion and contraction of both arms when the door is closed. The gears are forcibly rotated toward the rack side and meshed with each other to obtain a deceleration operation. After the protruding part passes through the contact member position, the frictional force generated at the contact point between the rack and the gear When the gear becomes smaller, the gear Door braking device according to claim 1, wherein the obtaining operation to leave from. The arrangement of the gear and rack of the engagement / disengagement mechanism and the movement operation of the gear are such that the axis of the gear is vertically oriented and the rack is arranged horizontally, the gear and the rack are located on the same horizontal plane, The rotating member is rotated and moved on a horizontal plane by contact with the protruding portion, and the gear is engaged with or disengaged from the rack, or the gear and the rack are arranged at the upper and lower positions on the same plane parallel to the door surface. The door brake according to claim 1, wherein the door is horizontally oriented and the rack is vertically arranged, and is engaged and disengaged by rotating the rotating member on the same plane parallel to the door. apparatus. The arrangement of the gear and rack of the engagement / disengagement mechanism and the movement of the gear are such that the gear shaft is positioned vertically and the rack is positioned horizontally, and the gear and rack are positioned slightly apart in the vertical direction. A structure in which a plurality of moving pieces having inclined surfaces press against each other by abutting between the contact member and the projecting member to move the gear in the vertical direction, or the gears on both sides sandwiching the fulcrum of the seesaw member that moves up and down 3. The structure according to claim 1 or 2, wherein the projecting portions are arranged separately and the gears are seesawed in the vertical direction by the contact between the contact member and the projecting member, and are engaged with and disengaged from the rack. The door brake device described in 1. The detaching means has a configuration in which a detaching spring is arranged to constantly urge the gear in a direction to leave the rack, or a configuration in which the gear and the speed reduction member use a natural fall action due to their own weight, or a combination of both. The door braking device according to any one of claims 1 to 4, wherein the door braking device is configured as described above. The engaging means of the engagement / disengagement mechanism distributes and arranges the magnet and the metal piece attracted by the magnet in the vicinity of the gear and the position facing the gear of the rack first and when the magnet and the metal piece approach each other. 2. The door according to claim 1, wherein the gear and the rack are engaged with each other, and the detaching means is a dropping operation due to the weight of the gear and the speed reduction member after the magnet and the metal piece are separated from each other. Braking device. From the open state, the door closes at a predetermined angle by the pulling force of the closing spring, and the load of the deceleration member by the engaging means is generated at the predetermined angle position, and the door is decelerated to the predetermined speed regardless of the closing speed. 7. A series of operations in which the rack and the gear are separated by the disengagement means at the stage where the speed is reduced to a predetermined low speed and are completely closed to the end without being stopped. The door brake device according to claim 1. The gear and the speed reducer are directly fixed in one arm, a long rack is mounted in the other arm, and both are arranged so that the gear and the rack engage in a wide angle range where the door opens and closes. The load of the speed reduction member generated when the rack is engaged is set so that it is always slightly smaller than the closing force of the closing spring, and the inertial force that gradually increases during the closing operation is suppressed while suppressing the inertial force from the beginning to the end. The door braking device according to claim 1, wherein the door is always closed at a low speed. The speed reduction member is configured to generate a load only in one direction of rotation of the gear, and is arranged so that a load is generated in the rotation direction by engagement with the rack when closing the door, and the rack when opening the door; The door braking device according to claim 1, wherein a load is not generated when the gear rotates in the reverse direction due to the engagement. The attachment member at one end of the arm is formed as a substantially rectangular interlocking piece, a pushing member with a flat front surface and a closing force enhancing spring are inserted into the closing force enhancing case, and the pushing member is pressed against the interlocking piece with the closing force enhancing spring. In this state, the interlocking piece and the closing force increasing case are pivotally connected to form a closing force increasing device, and the interlocking piece rotates together with the arm when the door is opened. By pushing the pushing member and compressing the closing force increasing spring, the closing force at the final stage of the door is increased, and the door is stopped and held at the position where the front surface of the interlocking piece faces the front surface of the pushing member. The door brake device according to any one of claims 1 to 9, wherein A 180 ° opening case with a long hole is provided, and the attachment member at one end of the arm is connected to the 180 ° opening case through the long hole with a connecting pin, and the connecting pin pulling spring is urged to open 180 °. The device is configured so that when the door opens further from the 90 degree open position, the connecting pin moves along with the arm to the suspension side while extending the connecting pin pulling spring along the elongated hole, and the door is moved 180 degrees. The door braking device according to any one of claims 1 to 10, wherein the door braking device can be opened to a maximum.

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