Bidirectional buffer structure and bidirectional buffer hinge

Abstract

The utility model discloses a two -way buffer structure and two -way buffer hinge, wherein, two -way buffer structure includes: drive arm, driven arm, damper, linkage arm and mounting seat, drive arm is used for with first fixed part rotatory connection, and mounting seat is used for setting in second fixed part, linkage arm is connected between drive arm and mounting seat, is used for limiting the rotation angle of first fixed part relative to second fixed part, driven arm and damper set up in mounting seat, and the movable end transmission of driven arm and damper is connected, when drive arm stress rotates, drive arm drives driven arm to drive the movable end of damper to stretch out first and then retract, to make first fixed part close or open in second fixed part. When being applied to hinge, through the linkage between drive arm and driven arm, no matter in the process of opening or closing, driven arm controls damper to reset first and then retract, realizes stable two -way buffer, simultaneously, through the cooperation of linkage arm and mounting seat, the hovering of hinge is realized.

Description

Technical Field

[0001] This utility model relates to the field of hinge technology, and in particular to a bidirectional buffer structure and a bidirectional buffer hinge. Background Technology

[0002] Door hinges, as a common connecting component, are widely used in furniture, cabinets, building doors and windows, and various appliance cabinet doors. Because doors and windows generate significant kinetic energy when opening and closing, dampers are installed inside the hinges to provide a damping effect and achieve a buffering effect.

[0003] Currently, hinges on the market that achieve bidirectional buffering when opening and closing using dampers mainly fall into two categories: one type uses two opposing dampers inside the hinge to achieve bidirectional buffering. This method increases the size of the hinge, and if one of them fails, it becomes unusable. The complex internal structure of the hinge also increases the difficulty of repair. The other type uses a combination of dampers and springs inside the hinge to achieve bidirectional buffering. This method also makes the internal structure of the hinge complex, and the spring force is fixed and uncontrollable, and there may be a rebound phenomenon, resulting in poor buffering effect. At the same time, neither of the above two types of hinges has the function of stopping when opened or closed to a specific angle. Utility Model Content

[0004] The main purpose of this invention is to provide a bidirectional buffer structure and hinge to solve the problem that existing door hinges have unstable bidirectional buffering effect and cannot achieve hovering.

[0005] To achieve the above objectives, this utility model proposes a bidirectional buffer structure, comprising: a drive arm, a driven arm, a damper, a linkage arm, and a mounting base; one end of the drive arm is tractively connected to the driven arm, and the other end is rotatably connected to a first fixed member; the mounting base is disposed on a second fixed member, and the driven arm is movably disposed on the mounting base; the linkage arm is connected between the drive arm and the mounting base, such that one end of the linkage arm presses against the mounting base, thereby limiting the rotation angle of the first fixed member relative to the second fixed member; the damper is disposed on the mounting base, and the driven arm is tractively connected to the movable end of the damper; when the drive arm is rotated under force, the drive arm drives the driven arm to extend and then retract the movable end of the damper, thereby causing the first fixed member to close or open on the second fixed member.

[0006] Optionally, the damper includes a cylinder, a piston rod, and a reset member. The reset member is located inside the cylinder, the piston rod is movably located inside the cylinder and can compress the reset member, and the driven arm abuts against the piston rod.

[0007] Optionally, one end of the drive arm is provided with a pushing part, the driven arm is provided with a movable groove, the pushing part is movably disposed in the movable groove, and the end of the driven arm away from the drive arm abuts against the piston rod, so that the pushing part drives the driven arm to release or squeeze the piston rod by pressing against the movable groove.

[0008] Optionally, the movable groove has a first groove wall and a second groove wall disposed opposite to each other, the first groove wall being higher than the second groove wall, the pushing part moving along the first groove wall; the second groove wall bending toward the first groove wall to form a barb, and the pushing part having a recess on the side facing the second groove wall that engages with the barb.

[0009] Optionally, the mounting base also includes a slider, wherein the mounting base has a receiving cavity for mounting the damper, the movable end of the damper is at least partially exposed in the receiving cavity, the slider is movably disposed at the opening of the receiving cavity, and the driven arm abuts against the piston rod through the slider.

[0010] Optionally, the slider includes an end plate and two side plates, the two side plates being spaced apart from the end plate, the mounting base having a sliding groove for the side plates to slide, the sliding groove extending along the extension and retraction direction of the damper, the slider surrounding the opening of the receiving cavity, and the slider releasing or pressing the piston rod along the sliding groove.

[0011] Optionally, it includes two driven arms, which are respectively disposed on opposite sides of the mounting base;

[0012] The side plate is bent at the end away from the end plate to form a push plate, which is pushed by the driven arm.

[0013] Alternatively, a push plate protrudes from the center of the side plate, and the push plate is pushed by the driven arm.

[0014] Optionally, the linkage arm includes a linkage rod and a friction shaft. One end of the linkage rod is rotatably connected to the mounting base, and the other end is rotatably connected to the first fixing member. A rotation groove is provided at one end of the linkage rod on the mounting base. The friction shaft is rotatably disposed in the rotation groove and at least partially protrudes from the rotation groove to frictionally connect with the outer wall of the mounting base.

[0015] This utility model also proposes a bidirectional buffer hinge, including: a hinge cup, a hinge body, and the above-mentioned bidirectional buffer structure. The hinge cup is rotatably connected to one end of the drive arm and one end of the linkage arm, respectively. The mounting seat is disposed on the hinge body. The hinge cup has a closed position and an open position relative to the hinge body.

[0016] When the hinge cup moves between the closed position and the open position, the other end of the linkage arm presses against the mounting base to limit the rotation angle of the hinge cup relative to the hinge body;

[0017] When the hinge cup rotates around the drive arm from the closed position to the open position, the drive arm drives the driven arm to cause the movable end of the damper to extend and then retract.

[0018] When the hinge cup rotates around the drive arm from the open position to the closed position, the drive arm drives the driven arm to cause the movable end of the damper to extend and then retract.

[0019] Optionally, it also includes a torsion spring, one end of which is connected to the drive arm and the other end of which is connected to the hinge body; when the hinge cup moves from the closed position to the open position, it passes through at least a first stroke segment and a second stroke segment in sequence; when the hinge cup is in the first stroke segment, the torsion spring can drive the hinge cup into the closed position, and / or, when the hinge cup is in the second stroke segment, the torsion spring can drive the hinge cup into the open position.

[0020] Optionally, when the hinge cup is in the first stroke segment, the range of the movable angle between the hinge cup and the hinge body is 0° to 52°; when the hinge cup is in the second stroke segment, the range of the movable angle between the hinge cup and the hinge body is 52° to 105°.

[0021] In the technical solution of this utility model, the bidirectional buffer structure includes a drive arm, a driven arm, a damper, a linkage arm, and a mounting base. One end of the drive arm is drivenly connected to the driven arm, and the other end is rotatably connected to the first fixed member. The mounting base is mounted on the second fixed member. The damper and the driven arm are mounted on the mounting base, and the linkage arm is connected between the drive arm and the mounting base. When applied to a door hinge, during the process of the door panel rotating around the drive arm to open or close in the cabinet, the linkage between the drive arm and the driven arm drives the driven arm to control the damper to first reset and then retract. Since the damper generates damping force during compression, the damper participates in the work during the opening or closing process, playing a buffering role. This allows bidirectional buffering to be achieved with only one damper, simplifying the hinge structure and providing precise and stable buffering force. At the same time, during the opening or closing process, as the door panel moves, one end of the linkage arm will press against the outer wall of the mounting base to generate dynamic friction, allowing the door panel to hover at a specific angle without relying on other external forces. Attached Figure Description

[0022] To more clearly illustrate the technical solutions in the embodiments of this utility model or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this utility model. For those skilled in the art, other drawings can be obtained based on the structures shown in these drawings without creative effort.

[0023] Figure 1 This is a schematic diagram of the bidirectional buffer structure in one embodiment of the present invention;

[0024] Figure 2 This is a schematic diagram of the bidirectional buffer hinge in one embodiment of the present invention;

[0025] Figure 3 for Figure 2 Exploded view;

[0026] Figure 4a for Figure 2 A cross-sectional view of the hinge cup in the hinged state;

[0027] Figure 4b for Figure 4a A schematic diagram of the damper being compressed;

[0028] Figure 4c for Figure 4a A schematic diagram showing the states of the drive arm, driven arm, and slider;

[0029] Figure 5a for Figure 2 A cross-sectional view of the hinge cup and the hinge body at an angle of θ1;

[0030] Figure 5b for Figure 5a A schematic diagram of the extended (reset) state of the intermediate damper;

[0031] Figure 5c for Figure 5a A schematic diagram showing the states of the drive arm, driven arm, and slider;

[0032] Figure 6a for Figure 2 A cross-sectional view of the hinge cup and the hinge body at an angle of θ2;

[0033] Figure 6b for Figure 6a A schematic diagram of the damper being compressed;

[0034] Figure 6c for Figure 6a A schematic diagram showing the states of the drive arm, driven arm, and slider;

[0035] Figure 7 for Figure 2 A schematic diagram showing the suspension of the hinge cup when the angle between the hinge cup and the hinge body is θ3;

[0036] Figure 8 for Figure 2 A schematic diagram showing the suspension when the angle between the hinge cup and the hinge body is θ4;

[0037] Figure 9 for Figure 2 A schematic diagram showing the suspension when the angle between the hinge cup and the hinge body is θ5;

[0038] Figure 10 This is a schematic diagram of the damper in one embodiment of the present invention;

[0039] Figure 11 This is a schematic diagram of the mounting base mechanism in one embodiment of the present utility model;

[0040] Figure 12 This is a schematic diagram of a slider in one embodiment of the present invention;

[0041] Figure 13 This is a schematic diagram of another structure of the slider in one embodiment of the present invention;

[0042] Figure 14 This is an exploded view of the linkage arm in one embodiment of the present invention.

[0043] Explanation of icon numbers:

[0044]

[0045]

[0046] The realization of the purpose, functional features and advantages of this utility model will be further explained in conjunction with the embodiments and with reference to the accompanying drawings. Detailed Implementation

[0047] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments. Based on the embodiments of the present utility model, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the protection scope of the present utility model.

[0048] It should be noted that all directional indicators (such as up, down, left, right, front, back, etc.) in this utility model embodiment are only used to explain the relative positional relationship and movement of each component in a certain specific posture (as shown in the figure). If the specific posture changes, the directional indicator will also change accordingly.

[0049] It should be noted that existing hinges used in doors or other similar switching structures are mainly divided into three categories: single-force hinges, two-force hinges, and three-force hinges. Taking cabinet doors as an example, a single-force hinge is a simple product combining a torsion spring and a damper. This type of damper only generates damping force when the door is closed (45° to 0°), thus providing a buffering effect when closing the door. When the door is opened to a small angle (such as 10° or 20°) from the closed state, if the external force is removed and the opening is stopped, the damper exits its resistance state, and the door panel will close quickly, causing a collision and generating noise. When the door continues to open (52° to 105°), the damper does not provide resistance, and the door opens quickly without resistance only under the force of the torsion spring, causing the door to spring back. This type of hinge causes significant damage to the cabinet and the door itself, and may even injure the user. The difference between a two-stage hinge and a one-stage hinge lies in the change in the position and structure of the torsion spring. Its advantage is that it provides a buffering effect during the 15° to 45° closing process and can automatically close. However, with this type, once the door is opened to 45°, the torsion spring and damper are inactive; the area between 45° and 105° requires manual opening and closing, which is a powerless process, and the door will still spring back when opened. A three-stage hinge adds a hinge-based opening and closing mechanism between 45° and 105°. The structure of the rotating shafts incorporates plastic components, creating frictional resistance between the shafts to prevent springback and door wobbling. However, with prolonged use, the components are prone to damage due to friction, resulting in a shorter product lifespan. Furthermore, this type of friction-based resistance requires high precision in component manufacturing and assembly, increasing production costs. The angles described above are merely examples for ease of understanding; specific implementation depends on the actual situation. Based on existing technology, it is understandable that because door hinges are usually used in small cabinets, their overall volume and internal space are small. Unlike large hinges (such as large hinges used in ovens), they cannot have complex internal mechanisms or multiple dampers to achieve bidirectional buffering. Therefore, most of these door hinges can only have one damper inside, thus only achieving unidirectional buffering when the door is closed. Hinges that can achieve bidirectional buffering have problems such as high production costs and poor applicability due to their complex internal structure.

[0050] See Figures 1 to 14As shown, in one embodiment of this utility model, a bidirectional buffer structure 100 includes: a drive arm 110, a driven arm 120, a damper 130, a linkage arm 140, and a mounting base 160; one end of the drive arm 110 is operatively connected to the driven arm 120, and the other end is rotatably connected to a first fixed member; the mounting base 160 is disposed on a second fixed member, and the driven arm 120 is movably disposed on the mounting base 160; the linkage arm 140 is connected between the drive arm 110 and the mounting base 160, so that one end of the linkage arm 140 is pressed against the mounting base 160, thereby limiting the rotation angle of the first fixed member relative to the second fixed member; the damper 130 is disposed on the mounting base 160, and the driven arm 120 is operatively connected to the movable end of the damper 130; when the drive arm 110 is subjected to force and rotates, the drive arm 110 drives the driven arm 120 to extend and then retract the movable end of the damper 130, thereby causing the first fixed member to close or open on the second fixed member.

[0051] Specifically, in this embodiment, one end of the linkage arm 140 is connected to one end of the drive arm 110 via a transmission connection. Preferably, in this embodiment, the drive arm 110 and the linkage arm 140 are connected by a U-shaped connecting rod 150. The drive arm 110 and the linkage arm 140 are rotatably connected to the two connecting rods of the U-shaped connecting rod 150, respectively. Further, one end of the drive arm 110 and one end of the linkage arm 140 are rotatably connected to the first fixed member via the U-shaped connecting rod 150. The other end of the drive arm 110 is rotatably connected to the second fixed member via the motion shaft (A). The other end of the driven arm 120, the mounting base 160, and the linkage arm 140 are rotatably connected to the second fixed member in sequence via the motion shaft (B). It can be understood that the drive arm 110, the driven arm 120, and the linkage arm 140 form a linkage structure, so that when the first fixed member rotates around one end of the drive arm 110, due to the linkage structure, during the process of the first fixed member opening or closing to the second fixed member, the drive arm 110 rotates clockwise and counterclockwise in sequence. It should be noted that in this embodiment, the damper 130 is mounted on the mounting base 160. The damper 130 can be a buffer with a self-resetting function or a shock absorber without a self-resetting function. It can be understood that when the damper 130 has a self-resetting function, the driven arm 120 and the movable end of the damper 130 are connected by contact, meaning there is no direct fixed mechanical connection between them. The driven arm 120 pushes the movable end of the damper 130 to retract it, and when the thrust is removed, the damper 130 retracts and extends itself. When the damper 130 does not have a self-resetting function, the extension of the movable end of the damper 130 depends on the driven arm 120. Therefore, the driven arm 120 and the movable end of the damper 130 are connected by a direct or indirect mechanical connection. The driven arm 120 pushes the movable end of the damper 130 to retract it, and pulls the movable end of the damper 130 to extend and reset it. This embodiment is not limited to this; all of the above are within the protection scope of this utility model.

[0052] The following uses a damper 130 with self-resetting function as an example to explain in detail the working principle of the bidirectional buffer structure 100 in this embodiment: See Figures 4a to 4c The first fixing member is initially closed to the second fixing member. At this time, the piston rod 132 (i.e., the moving end of the damper 130) is in the contracted state; see also Figures 5a to 5c When opened, the first fixed member rotates around one end of the drive arm 110 in a direction away from the second fixed member. During the opening process of the first fixed member from 0° to θ1, the drive arm 110 rotates clockwise around the motion axis (A), simultaneously driving the driven arm 120 to rotate counterclockwise around the motion axis (B). The driven arm 120 no longer applies force to the piston rod 132. Since the damper 130 has an automatic reset function, the piston rod 132 resets and extends out of the cylinder 131. It can be understood that at this time, the horizontal movement direction of the driven arm 120 is consistent with the extension direction of the piston rod 132; see also Figures 6a to 6c During the opening process of the first fixed member θ1~θ2, the drive arm 110 rotates counterclockwise around the motion axis (A) and simultaneously drives the driven arm 120 to rotate clockwise around the motion axis (B). The driven arm 120 drives the piston rod 132 and pushes the piston rod 132 into the cylinder 131. It can be understood that at this time, the horizontal movement direction of the driven arm 120 is consistent with the retraction direction of the piston rod 132. Since the cylinder 131 is equipped with a reset member 133, a buffer can be formed, so that the first fixed member opens slowly during the opening process of θ1~θ2.

[0053] Similarly, during closure, the first fixed member rotates around one end of the drive arm 110 toward the second fixed member. During the closure process of the first fixed member from θ2 to θ1, the drive arm 110 rotates clockwise around the motion axis (A) and simultaneously drives the driven arm 120 to rotate counterclockwise around the motion axis (B), and the damper 130 resets. During the closure process from θ1 to 0°, the drive arm 110 rotates counterclockwise around the motion axis (A) and simultaneously drives the driven arm 120 to rotate clockwise around the motion axis (B). The driven arm 120 drives the piston rod 132 and presses it into the cylinder 131, thereby forming a buffer, so that the first fixed member closes slowly during the closure process from θ1 to 0°. During the closing process, the action of the damper 130 is the same as that during the opening process, and will not be described again here.

[0054] The following explains how hovering works: See Figures 7 to 9When the first fixing member opens or closes to the second fixing member, due to the limited and relatively fixed spatial position, as it rotates, the first fixing member pushes the linkage arm 140 towards the mounting base 160, thereby keeping one end of the linkage arm 140 pressed against the mounting base 160 to generate friction with the outer wall of the mounting base 160. When the first fixing member rotates to θ3, θ4, and θ5, the pressure of the linkage arm 140 on the mounting base 160 is at its maximum. At this time, the friction generated between the linkage arm 140 and the mounting base 160 allows the first fixing member to hover at that angle. Preferably, θ3 is 13°, θ4 is 30°, and θ5 is 60°. It can be understood that the hovering angle includes the above angle ±5° range of motion. The hovering angle is determined by the friction contact surface between the linkage arm 140 and the mounting base 160. As long as the friction between the two is sufficient to make the first fixing member hover, the angles θ3, θ4, and θ5 described in this embodiment are only examples. Furthermore, in this embodiment, a protrusion is provided at the end of the linkage arm 140 that abuts against the mounting base 160. With this configuration, friction is generated between the protrusion and the mounting base 160, which enables the linkage arm 140 to be suspended without affecting its own rotation. Of course, the protrusion can also be provided on the mounting base 160. This embodiment is not limited to this. All of the above are within the protection scope of this utility model.

[0055] It is understandable that when the damper 130 is a shock absorber without self-resetting function, the active principle and hovering principle of the bidirectional buffer are the same as those of the case with self-resetting function. The difference lies in the connection method between the damper 130 and the driven arm. When the active end of the damper 130 extends and resets, it is pulled out through the driven arm 120, which will not be elaborated here.

[0056] In the technical solution of this utility model, the bidirectional buffer structure 100 includes a drive arm 110, a driven arm 120, a damper 130, a linkage arm 140, and a mounting base 160. One end of the drive arm 110 is connected to the driven arm 120 for transmission, and the other end is used for rotatable connection with the first fixed member. The mounting base 160 is used to be disposed on the second fixed member. The damper 130 and the driven arm 120 are disposed on the mounting base 160. The linkage arm 140 is connected between the drive arm 110 and the mounting base 160. When applied to door hinges, during the process of the door panel rotating around the drive arm 110 to open or close within the cabinet, the linkage between the drive arm 110 and the driven arm 120 drives the driven arm 120 to control the damper 130 to first reset and then retract. Since the damper 130 generates damping force during compression, it participates in the opening or closing process, playing a buffering role. This allows for bidirectional buffering with only one damper 130, simplifying the hinge structure and providing precise and stable buffering force. At the same time, during opening or closing, as the door panel moves, one end of the linkage arm 140 presses against the outer wall of the mounting base 160 to generate dynamic friction, allowing the door panel to hover at a specific angle or within a certain angle range without relying on other external forces.

[0057] See Figures 1 to 14As shown, in one embodiment of the present invention, the damper 130 includes a cylinder 131, a piston rod 132 and a reset member 133. The reset member 133 is disposed inside the cylinder 131, and the piston rod 132 is movably disposed inside the cylinder 131 and can compress the reset member 133. The driven arm 120 abuts against the piston rod 132. It should be noted that the damper 130 in this embodiment is a self-resetting buffer, preferably a spring-type reset damper. The reset member 133 is a spring. The end of the piston rod 132 away from the reset member 133 protrudes at least partially from the cylinder body 131 and abuts against the driven arm 120. The driven arm 120 can directly drive or drive the piston rod 132 through other media. When the driving arm 110 drives the driven arm 120 to push the piston rod 132 back towards the cylinder body 131, the spring is compressed and generates a force opposite to the pushing direction, thereby generating a buffering force. Since the damper 130 has a self-resetting function, when the driving arm 110 drives the driven arm 120 to move to remove the force applied to the piston rod 132, the spring is released and pushes the piston rod 132 so that the piston rod 132 extends out of the cylinder body 131, completing the self-resetting. Of course, the reset component 133 can also be an elastomer such as polyurethane or rubber; it can also be a shape memory alloy, which can restore its original shape after being compressed by relying on the alloy properties to achieve self-reset; or it can be achieved by setting permanent magnets or electromagnets on the cylinder 131 and piston rod 132 respectively, using the principle of magnetic pole repulsion to achieve buffering and self-reset; the above are only some preferred methods. In this embodiment, the damper 130 can achieve self-reset as long as it can achieve self-reset. This embodiment is not limited to this. All of the above are within the protection scope of this utility model.

[0058] See Figures 1 to 14As shown, in one embodiment of the present invention, one end of the drive arm 110 is provided with a push part 111, and the driven arm 120 is provided with a movable groove 121. The push part 111 is movably disposed in the movable groove 121. The end of the driven arm 120 away from the drive arm 110 abuts against the piston rod 132, so that the push part 111 drives the driven arm 120 to release or squeeze the piston rod 132 by pressing against the movable groove 121. It should be noted that in this embodiment, the driving arm 110 and the driven arm 120 are similar to two L-shaped arms. The driven arm 120 has a U-shaped movable groove 121 on one side and a contact part 122 protruding on the other side. The contact part 122 is used to directly or through a medium abut against the piston rod 132. One end of the driving arm 110 is provided with a pushing part 111. Preferably, the shape of the pushing part 111 fits the movable groove 121. When the driving arm 110 rotates, the pushing part 111 moves along the groove wall of the movable groove 121. Due to the connection relationship, when the driving arm 110 rotates, the pushing part 111 can apply force to the groove wall of the movable groove 121, thereby driving the driven arm 120 to rotate in the opposite direction to the movement direction of the driving arm 110, so that the contact part 122 presses against or releases the piston rod 132. Of course, the pusher 111 and the driven arm 120 can also be configured as gears. When the drive arm 110 rotates, the pusher 111 and the driven arm 120 mesh and rotate. As long as the drive arm 110 and the driven arm 120 can move in opposite directions, this embodiment is not limited to this. All of the above are within the protection scope of this utility model.

[0059] See Figures 1 to 14 As shown, in one embodiment of the present invention, the movable groove 121 has a first groove wall 1211 and a second groove wall 1212 disposed opposite to each other. The first groove wall 1211 is higher than the second groove wall 1212, and the pushing part moves along the first groove wall 1211. The second groove wall 1212 bends toward the first groove wall 1211 to form a barb, and the pushing part has a recess on the side facing the second groove wall 1212 that cooperates with the barb. It should be noted that the movable groove 121 in this embodiment is a U-shaped groove, wherein the first groove wall 1211 is relatively close to the damper 130, and the first groove wall 1211 is higher than the second groove wall 1212. The second groove wall 1212 is formed with a barb-shaped structure. Correspondingly, the side of the pushing part 111 that contacts the barb is formed with a recess, so that the pushing part 111 can be engaged in the movable groove 121. Specifically, as an example, referring to Figures 4 to 6, during the process of the first fixing member opening in the second fixing member, as the driving arm 110 and the driven arm 120 rotate, the recess of the pushing part 111 will gradually approach the barb of the second groove wall 1212, and finally the two will engage with each other. With this configuration, the pushing part 111 can be confined in the movable groove 121, so that the pushing part 111 will not disengage from the movable groove 121 when the driving arm 110 rotates, and at the same time, it can also guide the rotation of the pushing part 111.

[0060] See Figures 1 to 14 As shown, in one embodiment of the present invention, a slider 170 is further included. The mounting base 160 is provided with a receiving cavity for mounting the damper 130. The movable end of the damper 130 is at least partially exposed in the receiving cavity. The driven arm 120 is rotatably connected to the mounting base 160. The slider 170 is movably disposed at the opening of the receiving cavity. The driven arm 120 abuts against the piston rod 132 through the slider 170. It should be noted that in this embodiment, the driven arm 120 and the linkage arm 140 are rotatably connected to the mounting base 160 via the motion shaft (B) to form a whole, thereby increasing the stability of the mechanism. The damper 130 is installed in the receiving cavity of the mounting base 160. Preferably, the inner wall of the receiving cavity fits the shape of the damper 130 so that it does not shift or loosen during operation, and at the same time, it protects the damper 130. The piston rod 132 protrudes from the receiving cavity. Preferably, the end face of the cylinder 131 is flush with the opening of the receiving cavity to avoid insufficient compression of the reset piece 133 by the piston rod 132, which would affect the buffering effect. The slider 170 is slidably positioned at the opening of the receiving cavity along the direction of movement of the piston rod 132. One side of the slider 170 abuts against the piston rod 132, and the area of ​​the abutting surface of the slider 170 should be larger than the contact surface of the piston rod 132. The piston rod 132 is compressed by the driven arm 120 pressing against the slider 170. It should be noted that the slider 170 can be a structural component of any shape, such as rectangular, cylindrical, or other polygonal shapes, as long as it can compress the piston rod 132 through sliding. This embodiment is not limited to this, and all of the above are within the protection scope of this utility model. By setting the slider 170 to push the piston rod 132, the force-bearing area is increased, avoiding the piston rod 132 from shifting or even being damaged due to uneven force during compression, thus affecting the buffering effect.

[0061] See Figures 1 to 14As shown, in one embodiment of the present invention, the slider 170 includes an end plate 171 and two side plates 172. The two side plates 172 are spaced apart from the end plate 171. The mounting base 160 has grooves 161 on both sides for sliding the side plates 172. The grooves 161 extend along the extension and retraction direction of the damper 130. The slider 170 surrounds the opening of the receiving cavity. The slider 170 releases or squeezes the piston rod 132 along the grooves 161. It should be noted that the slider 170 in this embodiment is a concave part, with the concave portion facing the damper 130, forming a space with the receiving cavity. The size of this space changes as the slider 170 moves. Both sides of the mounting base 160 are provided with grooves 161 extending to a certain depth along the extension and retraction direction of the piston rod 132. The two side plates 172 of the slider 170 are respectively mounted on the two grooves 161. When the side plates 172 slide along the grooves 161 toward the damper 130, the end plates 171 compress the piston rod 132. By setting the grooves 161, the slider 170 can slide directionally along the grooves 161, improving the stability of the slider 170 during movement. At the same time, it limits the stroke of the slider 170, so that when the first fixing member is fully opened or closed to the second fixing member, while the piston rod 132 is compressed, the side plates 172 can abut against the groove wall of the groove 161, so that part of the force it receives is unloaded onto the mounting base 160, thereby improving the service life of the damper 130. It is understandable that the depth of the slide groove 161 should be determined according to the stroke of the piston rod 132, and is not limited here.

[0062] See Figures 1 to 14 As shown, further, in one embodiment of this utility model, two driven arms 120 are included. The two driven arms 120 are respectively disposed on opposite sides of the mounting base 160. The end of the side plate 172 away from the end plate 171 is bent to form a push plate 1721, which is pushed by the driven arms 120. It should be noted that in this embodiment, two driven arms 120 are symmetrically arranged on both sides of the mounting base 160. Correspondingly, the drive arm 110 has two push parts 111 spaced apart. Each push part 111 controls the movement of one driven arm 120. Of course, it is also possible to control the movement of both driven arms 120 simultaneously by only one push part 111 in conjunction with a rotating shaft, push block, etc. This embodiment is not limited to this, and all of the above are within the protection scope of this utility model. See also Figure 12 One end of each of the two side plates 172 is bent outward to form a push plate 1721. The contact portion 122 of each of the two driven arms 120 abuts against a push plate 1721. By setting two driven arms 120 to drive the slider 170, the slider 170 is subjected to a balanced force when sliding, thereby improving the stability of the mechanism during operation.

[0063] Or see Figure 13As a preferred embodiment, a push plate 1721 protrudes from the center of the side plate 172, and the push plate 1721 is pushed by the driven arm 120. With the push plate 1721 located at one end of the end plate 171, the force point would be concentrated at one end of the slider 170. When the slider 170 is pushed, the other end might tilt up. Therefore, by placing the push plate 1721 in the center of the side plate 172, the force point is concentrated in the middle, which can prevent the slider 170 from tilting up when pushed, further improving the stability of the mechanism during operation.

[0064] See Figures 1 to 14 As shown, in one embodiment of the present invention, the linkage arm 140 includes a linkage rod 141 and a friction shaft 142. One end of the linkage rod 141 is rotatably connected to the mounting base 160, and the other end is rotatably connected to the first fixing member. A rotation groove 1411 is provided at one end of the linkage rod 141 located in the mounting base 160. The friction shaft 142 is rotatably located in the rotation groove 1411 and at least partially protrudes from the rotation groove 1411 to frictionally connect with the outer wall of the mounting base 160. It should be noted that when the first fixing member is open or closed to the second fixing member, the linkage rod 141 rotates with the first fixing member. At this time, the friction shaft 142 rotates within the rotation groove 1411 and presses against the outer wall of the mounting base 160 as the linkage rod 141 rotates, i.e., it rolls along the outer wall of the mounting base 160 to generate friction. When the first fixing member rotates to θ3, θ4 and θ5, the pressure of the friction shaft 142 on the mounting base 160 is the greatest. The friction shaft 142 presses against the outer wall of the mounting base 160, thus suspending the first fixing member. It is understandable that if the linkage rod 141 and the friction shaft 142 are set as an integral structure, due to the limitations of stamping or other processing techniques, it is difficult to make the surface of the workpiece flat, which will cause great damage to the parts during friction. In this embodiment, the linkage rod 141 and the friction shaft 142 are separate structures, which allows the friction shaft 142 to rotate during the movement, avoiding direct hard friction with the mounting base 160, reducing the wear of the parts, and when the parts are damaged, only the friction shaft 142 needs to be replaced, reducing maintenance costs.

[0065] This embodiment provides a bidirectional buffer hinge 1000, including: a hinge cup 200, a hinge body 300, and the aforementioned bidirectional buffer structure 100. One end of the drive arm 110 is throttlely connected to the driven arm 120, and the other end is rotatably connected to the hinge cup 200. A damper 130 is disposed on the hinge body 300. The hinge cup 200 has a closed position and an open position relative to the hinge body 300. When the hinge cup moves between the closed position and the open position, the other end of the linkage arm presses against the mounting seat to limit the rotation angle of the hinge cup relative to the hinge body. When the hinge cup 200 rotates around the drive arm 110 from the closed position to the open position, the drive arm 110 drives the driven arm 120 to extend and then retract the movable end of the damper 130. When the hinge cup 200 rotates around the drive arm 110 from the open position to the closed position, the drive arm 110 drives the driven arm 120 to extend and then retract the movable end of the damper 130.

[0066] It should be noted that in this embodiment, the hinge cup 200 is the first fixing member, and the hinge body 300 is the second fixing member. When applied to cabinet door hinges, the hinge cup 200 is used to install on the door panel, and the hinge body 300 is used to install on the cabinet body. Of course, the bidirectional buffer structure 100 of this utility model can also be applied to products that require buffering when opening and closing in both directions, such as flip-up drawers, flip-up beds, boxes, and toilet seats. This embodiment is not limited to this, and all of the above are within the protection scope of this utility model. Specifically, one end of the drive arm 110, one end of the linkage arm 140, the driven arm 120, and the mounting base 160 are all riveted to the hinge body 300 by a pivot. The other ends of the drive arm 110 and the linkage arm 140 are installed on the hinge cup 200 by a U-shaped connecting rod 150. Referring to Figures 4 to 6, when the hinge cup 200 rotates from the closed position to the open position, it sequentially passes through 0° to θ1 and θ1 to θ2, where θ2 is the fully open angle of the hinge cup 200. During this process, the drive arm 110 drives the driven arm 120 to extend and then retract the piston rod 132, causing the hinge cup 200 to open slowly during the opening process from θ1 to θ2. When the hinge cup 200 rotates from the open position to the closed position, it sequentially passes through θ2 to θ1 and θ1 to 0°. During this process, the drive arm 110 drives the driven arm 120 to extend and then retract the piston rod 132, causing the hinge cup 200 to close slowly during the closing process from θ1° to 0°. See Figures 7 to 9As shown, during the rotation of the hinge cup 200 relative to the hinge body 300 from the closed position to the open position or from the open position to the closed position, when passing through θ3, θ4, and θ5, due to the frictional force generated between the linkage arm 140 and the mounting base 160, the hinge cup 200 can be suspended at the aforementioned angles, enabling the door panel to be suspended at a specific angle. Preferably, θ3 is 13°, θ4 is 30°, and θ5 is 60°. It can be understood that the suspension angle includes the above angles ±5° of the range of motion. The suspension angle is determined by the frictional contact surface between the linkage arm 140 and the mounting base 160. As long as the frictional force between the two is sufficient to allow the hinge cup 200 to be suspended, it is acceptable. The angles θ3, θ4, and θ5 described in this embodiment are only examples. In this way, the usage scenarios of the cabinet door can be enriched to meet the needs of users. The above working principle is the same as that of the aforementioned bidirectional buffer structure 100, and will not be repeated here. Furthermore, an adjustable hinge seat 400 is also installed on the hinge body 300. The hinge body 300 and the hinge seat 400 are provided with multiple mounting slots, including slots that extend longitudinally and laterally. By providing multiple mounting slots, the position of the hinge mounted on the cabinet through the hinge seat 400 can be adjusted, thereby improving the applicability of the two-way buffer hinge 1000. In this embodiment of the bidirectional buffer hinge 1000, due to the linkage between the drive arm 110 and the driven arm 120, during the opening or closing of the hinge cup 200 into or out of the hinge body 300, the damper 130 is first reset and then compressed. This allows for slow closing and opening with only one internal damper 130, preventing the door panel from closing too quickly and injuring the user or causing noise, and preventing the door panel from rebounding too quickly when opening. The buffering effect is achieved solely by the damper 130, which is more stable than existing methods that rely on springs or friction between workpieces. Simultaneously, the friction between the linkage arm 140 and the mounting base 160 allows for a specific angle of suspension, enabling the door to remain open at a certain angle for easy access to items, meeting user needs. The bidirectional buffer hinge 1000 of this embodiment has a simple internal structure, resulting in a compact overall size, suitable for environments with limited installation space, low requirements for workpiece machining precision, and easy maintenance, effectively reducing production costs.

[0067] See Figures 1 to 14As shown, in one embodiment of the present invention, a torsion spring 500 is further included. One end of the torsion spring 500 is connected to the drive arm 110 and the other end is connected to the hinge body 300. When the hinge cup 200 moves from the closed position to the open position, it passes through at least the first stroke segment and the second stroke segment in sequence. When the hinge cup 200 is in the first stroke segment, the torsion spring 500 can drive the hinge cup 200 into the closed position, and / or, when the hinge cup 200 is in the second stroke segment, the torsion spring 500 can drive the hinge cup 200 into the open position. It should be noted that in this embodiment, the torsion spring 500 is rotatably mounted on the drive arm 110 via the motion shaft (A). One end of the torsion spring 500 presses against the drive arm 110, and the other end presses against the hinge body 300. Taking the hinge cup 200 opening from the hinge body 300 as an example, when the hinge cup 200 opens from the closed state (the angle between it and the hinge body 300 is 0°), the torsion spring 500 is compressed and deformed. When the hinge cup 200 opens to a small angle, the external force is removed, and the torsion spring 500 automatically resets, driving the hinge cup 200 back to the closed state, thus achieving automatic closing at a small angle. When the hinge cup 200 opens to a large angle, the external force is removed, and the torsion spring 500 resets and releases its elastic force, so that it automatically opens to the maximum opening angle at a large angle. As an example, the above-mentioned large angle is the angle between the hinge cup 200 and the hinge body 300, which is 52° to 105°, and the small angle is the angle between the hinge cup 200 and the hinge body 300, which is 10° to 45°. It is understood that the angles of automatic closing and automatic opening are determined by the included angle (preload angle and reset angle) between the two torsion arms of the torsion spring 500 and the installation position of the torsion spring 500. Therefore, the above-mentioned large angle and small angle can be adjusted according to the actual use to meet different use scenarios. This embodiment is not limited to this, and all of the above are within the protection scope of this utility model.

[0068] See Figures 1 to 14 As shown, further, in one embodiment of the present invention, when the hinge cup 200 is in the first stroke segment, the range of the movable angle between the hinge cup 200 and the hinge body 300 is 0° to 52°; when the hinge cup 200 is in the second stroke segment, the range of the movable angle between the hinge cup 200 and the hinge body 300 is 52° to 105°. It should be noted that in this embodiment, θ1 is preferably 52° and θ2 is preferably 105°. It can be understood that when the hinge cup 200 opens from 0° to 52° relative to the hinge body 300, the damper 130 resets, and when it opens from 52° to 105°, the damper 130 is compressed; when the hinge cup 200 closes from 105° to 52° relative to the hinge body 300, the damper 130 resets, and when it closes from 52° to 0°, the damper 130 is compressed, thereby achieving slow opening and slow closing. The specific values ​​of θ1 and θ2 are adjusted according to the application scenario of the hinge, and this embodiment is not limited to this. All of the above are within the protection scope of this utility model.

[0069] The above description is only an optional embodiment of the present utility model and does not limit the patent scope of the present utility model. All equivalent structural transformations made under the inventive concept of the present utility model using the contents of the present utility model specification and drawings, or direct / indirect applications in other related technical fields, are included within the patent protection scope of the present utility model.

Claims

1. A bidirectional buffer structure, characterized in that, include: The system comprises a drive arm, a driven arm, a damper, a linkage arm, and a mounting base. One end of the drive arm is tractively connected to the driven arm, and the other end is rotatably connected to a first fixed member. The mounting base is disposed on a second fixed member, and the driven arm is movably disposed on the mounting base. The linkage arm is connected between the drive arm and the mounting base, such that one end of the linkage arm presses against the mounting base, thereby limiting the rotation angle of the first fixed member relative to the second fixed member. The damper is disposed on the mounting base, and the driven arm is tractively connected to the movable end of the damper. When the drive arm is rotated under force, the drive arm drives the driven arm to extend and then retract the movable end of the damper, thereby causing the first fixed member to close or open on the second fixed member.

2. The bidirectional buffer structure as described in claim 1, characterized in that, The damper includes a cylinder, a piston rod, and a reset member. The reset member is located inside the cylinder. The piston rod is movably located inside the cylinder and can compress the reset member. The driven arm abuts against the piston rod.

3. The bidirectional buffer structure as described in claim 2, characterized in that, One end of the drive arm is provided with a pushing part, and the driven arm is provided with a movable groove. The pushing part is movably disposed in the movable groove. The end of the driven arm away from the drive arm abuts against the piston rod, so that the pushing part drives the driven arm to release or squeeze the piston rod by pressing against the movable groove.

4. The bidirectional buffer structure as described in claim 3, characterized in that, The movable groove has a first groove wall and a second groove wall arranged opposite to each other. The first groove wall is higher than the second groove wall. The pushing part moves along the first groove wall. The second groove wall bends toward the first groove wall to form a barb. The pushing part has a recess on the side facing the second groove wall that cooperates with the barb.

5. The bidirectional buffer structure as described in claim 2, characterized in that, It also includes a slider, the mounting base has a receiving cavity for mounting the damper, the movable end of the damper is at least partially exposed in the receiving cavity, the slider is movably disposed at the opening of the receiving cavity, and the driven arm abuts against the piston rod through the slider.

6. The bidirectional buffer structure as described in claim 5, characterized in that, The slider includes an end plate and two side plates, which are spaced apart from the end plate. The mounting base has a sliding groove for the side plates to slide. The sliding groove extends along the extension and retraction direction of the damper. The slider surrounds the opening of the receiving cavity. The slider releases or presses the piston rod along the sliding groove.

7. The bidirectional buffer structure as described in claim 6, characterized in that, It includes two driven arms, which are respectively located on opposite sides of the mounting base; The side plate is bent at the end away from the end plate to form a push plate, which is pushed by the driven arm. Alternatively, a push plate protrudes from the center of the side plate, and the push plate is pushed by the driven arm.

8. The bidirectional buffer structure as described in any one of claims 1 to 7, characterized in that, The linkage arm includes a linkage rod and a friction shaft. One end of the linkage rod is rotatably connected to the mounting base, and the other end is rotatably connected to the first fixing member. A rotation groove is provided at one end of the linkage rod on the mounting base. The friction shaft is rotatably disposed in the rotation groove and at least partially protrudes from the rotation groove to frictionally connect with the outer wall of the mounting base.

9. A bidirectional buffer hinge, characterized in that, The invention includes a hinge cup, a hinge body, and a bidirectional buffer structure as described in any one of claims 1 to 8, wherein the hinge cup is rotatably connected to one end of the drive arm and one end of the linkage arm, the mounting base is disposed on the hinge body, and the hinge cup has a closed position and an open position relative to the hinge body. When the hinge cup moves between the closed position and the open position, the other end of the linkage arm presses against the mounting base to limit the rotation angle of the hinge cup relative to the hinge body; When the hinge cup rotates around the drive arm from the closed position to the open position, the drive arm drives the driven arm to cause the movable end of the damper to extend and then retract. When the hinge cup rotates around the drive arm from the open position to the closed position, the drive arm drives the driven arm to cause the movable end of the damper to extend and then retract.

10. The bidirectional buffer hinge as described in claim 9, characterized in that, It also includes a torsion spring, one end of which is connected to the drive arm and the other end of which is connected to the hinge body; when the hinge cup moves from the closed position to the open position, it passes through at least the first stroke segment and the second stroke segment in sequence; when the hinge cup is in the first stroke segment, the torsion spring can drive the hinge cup into the closed position, and / or, when the hinge cup is in the second stroke segment, the torsion spring can drive the hinge cup into the open position.

11. The bidirectional buffer hinge as described in claim 10, characterized in that, When the hinge cup is in the first stroke segment, the range of the movable angle between the hinge cup and the hinge body is 0° to 52°; when the hinge cup is in the second stroke segment, the range of the movable angle between the hinge cup and the hinge body is 52° to 105°.

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