Piston drive displacement mechanism

Abstract

The utility model discloses a piston drive displacement mechanism, including main part, piston, elastic reset piece, movable drive part and pivot. The main part is equipped with the accommodation cavity in, and the cavity is equipped with piston and elastic reset piece, movable drive part is connected in the one end of piston orientation pivot, and can be relative to piston axis left and right activity, the pivot sets up the cam, and its profile surface and movable drive part's stress part are abutted. The cam and the main part relative rotation between both when the door leaf opens and closes, and the stress part is pushed through the profile surface, and then drive piston compresses or releases elastic reset piece, movable drive part passes through swing self -adaptation and adjusts the relative position of stress part and cam, makes stress part always be located in the front side of cam rotating direction in the door leaf closing process. The mechanism has optimized the drive stroke of door leaf closing to 5 to 0 interval particularly, effectively prolongs piston action stroke, ensures hydraulic buffer effect, fundamentally solves the overshoot and swing problem of door leaf closing final section, realizes stable closing.

Description

Technical Field

[0001] This utility model relates to the field of door control hardware technology, and in particular to a piston-driven displacement mechanism. Background Technology

[0002] In the field of door control hardware technology, two-way opening and closing products such as buffer glass clamps and hinges commonly employ a cam-driven piston mechanism to achieve automatic closing and buffering of the door leaf. This type of mechanism typically relies on the interaction between the cam and a fixed contact point at one end of the piston: when the door leaf begins to close from a large angle (e.g., 90°), the cam profile effectively drives the piston, causing it to compress an internal elastic reset element (e.g., a spring) and be subjected to hydraulic damping, thereby achieving buffering; however, as shown in the attached... Figure 1 As shown, when the door is closed to a small angle (approximately 5° to 0° for complete closure), the driving stroke of the piston decreases sharply due to the geometric characteristics of the cam profile, causing the buffering effect to almost fail. During this stage, the door has self-closing force and inertial motion, easily leading to overshoot and causing the door to sway left and right at the moment of closing. This not only causes collision noise but also affects the smoothness of closing and the accuracy of locking. The root cause of this problem lies in the fixed relative relationship between the piston drive and the cam in traditional mechanisms, which cannot adapt to the specific requirements of the effective driving stroke at the end of the closing process, thus limiting its overall performance and user experience during bidirectional opening and closing. Therefore, an innovative driving solution is urgently needed to overcome these inherent defects. Utility Model Content

[0003] This invention aims to solve at least one of the technical problems existing in the prior art. To this end, this invention proposes a piston-driven displacement mechanism that optimizes the hydraulic buffer drive stroke in the 5° to 0° range when the door is closed, effectively extending the piston's stroke, ensuring the hydraulic buffering effect, fundamentally solving the problem of overshoot and swaying at the end of the door closing, and achieving smooth closing.

[0004] The technical solution adopted by this utility model to solve its technical problem is: A piston-driven displacement mechanism, including The main body has a receiving cavity inside, and a piston and an elastic reset member for providing a reset force are provided in the receiving cavity. The piston can reciprocate within the receiving cavity. A movable drive component is connected to the end of the piston facing away from the elastic reset component and can move left and right relative to the axis of the piston; A rotating shaft is rotatably disposed with respect to the main body. A cam is disposed on the rotating shaft within the accommodating cavity. The contour surface of the cam abuts against the force-receiving part of the movable drive member. When the door opens and closes, the main body and the rotating shaft rotate relative to each other, causing the piston and the cam to rotate circumferentially. The force-receiving part slides along the contour surface, thereby driving the piston to move and compress or release the elastic reset member. Furthermore, the movable drive member can adaptively adjust the relative position of the force-receiving part and the cam by moving left and right, so that during the closing process of the door, the force-receiving part is always located in front of the cam's rotation direction.

[0005] According to an embodiment of this utility model, a piston-driven displacement mechanism has at least the following beneficial effects: by introducing a movable drive member connected to the piston end with limited left and right movement, and cooperating with a cam set on the rotating shaft, an adaptive bidirectional drive mechanism is constructed. The core advantage of this design is that when the door leaf enters the closing process after opening to the left or right, the movable drive member can automatically adjust the relative position of its force-bearing part and the cam by virtue of its limited left and right swing function, ensuring that the force-bearing part is always in front of the cam's rotation direction, thereby forming a stable and effective drive relationship. This adaptive characteristic provides greater optimization space for the design of the cam profile, allowing it to be specifically configured to maintain a significant drive stroke on the piston even when the door leaf is closed to the critical small angle range of 5° to 0°. By effectively extending the piston stroke in this stage, the mechanism can continuously provide sufficient hydraulic buffering, completely eliminating the buffering failure problem caused by the sharp reduction of the drive stroke in this stage in traditional designs. Therefore, this utility model fundamentally solves the problem of inertial overshoot and left-right swaying caused by insufficient drive stroke at the end of the closing phase of a two-way door, significantly improving the stability and accuracy of door closure, achieving a gentle and smooth closing experience across the entire angle range, and enhancing the product's versatility and reliability.

[0006] According to some embodiments of the present invention, the movable drive member is provided with a shaft connected to the piston, so that the force-receiving part can swing left and right relative to the axis of the piston.

[0007] The advantages are: by setting a shaft to connect the movable drive component and the piston, the structure is simple and reliable, and it provides a precise rotation axis for the smooth left and right swing of the drive component, ensuring the stability and directional accuracy of power transmission.

[0008] According to some embodiments of the present invention, the piston has a recessed cavity at its end, the movable drive member includes a connecting part housed in the recessed cavity and a force-receiving part exposed in the recessed cavity, and the shaft passes through the connecting part and the piston.

[0009] The advantages are that by housing the connecting part of the movable drive component in the recessed cavity at the end of the piston, the structure becomes more compact, the internal space is effectively utilized, the integrity and stability of the swinging component are enhanced, and the size of the mechanism is reduced.

[0010] According to some embodiments of the present invention, the force-receiving part of the movable drive member is provided with a roller and the two are connected by a pin, and the roller makes rolling contact with the contour surface of the cam.

[0011] The benefits are that by installing rollers in the force-bearing part, the sliding friction between the cam and the drive component is transformed into rolling friction, which significantly reduces wear and operating noise during the movement process, making the transmission more effortless and smooth, and extending the service life.

[0012] According to some embodiments of this utility model, the elastic reset member is a pressure spring.

[0013] The advantage is that using a pressure spring as an elastic reset component provides reliable elastic performance and stable mechanical properties, enabling it to provide a continuous and uniform reset force to the piston, ensuring the consistency and durability of the mechanism's cyclic operation.

[0014] According to some embodiments of the present invention, the profile surface of the cam is a pointed cone shape.

[0015] The advantage is that the cam's profile is designed as a sharp cone, which can create a steeper change in the drive stroke, ensuring that it can still exert a significant driving effect on the piston in the final stage of door closing, effectively eliminating the final buffer blind zone.

[0016] According to some embodiments of the present invention, the accommodating cavity is a hydraulic cylinder, which is filled with hydraulic oil.

[0017] The advantage is that by setting the accommodating cavity as a hydraulic cylinder filled with hydraulic oil, the incompressibility and flow resistance of the liquid provide hydraulic damping for the piston movement, thereby achieving a smooth and controllable buffering effect and absorbing the kinetic energy of the door leaf.

[0018] According to some embodiments of the present invention, a sealing element is provided between the piston and the inner wall of the accommodating cavity, so that the reciprocating motion of the piston is controlled by hydraulic damping.

[0019] The advantages are: by installing a seal between the piston and the inner wall of the hydraulic cylinder, the sealing performance of the hydraulic cylinder is ensured, making the hydraulic damping effect controllable and stable, preventing oil leakage, and ensuring the long-term consistency of the buffering performance.

[0020] According to some embodiments of the present invention, the mechanism is integrated into a floor spring, a buffer glass clamp, or a top and bottom hinge.

[0021] The benefits are that integrating this mechanism into common door control products such as floor springs, buffer glass clamps, or top and bottom hinges can directly improve the closing performance of these products, giving them bidirectional smooth buffering capabilities and broadening their application scenarios.

[0022] Additional aspects and advantages of this invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

[0023] To more clearly illustrate the technical solutions of 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 these drawings without creative effort.

[0024] Figure 1 A schematic diagram of the piston's drive stroke in the 5° to 0° range when the door is closed in existing technology; Figure 2 This is a schematic diagram of an embodiment of the present utility model; Figure 3 for Figure 2 A schematic diagram of the decomposition process; Figure 4 This is a schematic diagram of the piston's drive stroke in the 5° to 0° range when the door leaf is closed according to this utility model; Figure 5 for Figure 4 A diagram showing the door opening to the other side after it has been closed to 0°.

[0025] Reference numerals: main body 100, accommodating cavity 110, piston 120, elastic reset component 130, movable drive component 140, cam 150, force-receiving part 160, shaft 170, cavity 180, connecting part 190, roller 200, rotating shaft 210, pin 220. Detailed Implementation The embodiments of this utility model are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain this utility model, and should not be construed as limiting this utility model.

[0026] In the description of this utility model, it should be understood that the directional descriptions, such as up, down, front, back, left, right, etc., indicate the directional or positional relationship based on the directional or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this utility model.

[0027] In the description of this utility model, "several" means one or more, "multiple" means two or more, "greater than," "less than," and "exceeding" are understood to exclude the stated number, while "above," "below," and "within" are understood to include the stated number. If "first" and "second" are mentioned, it is only for the purpose of distinguishing technical features and should not be construed as indicating or implying relative importance or implicitly indicating the number of indicated technical features or the order of the indicated technical features.

[0028] In the description of this utility model, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation, connection, and linkage" should be interpreted broadly. For example, they can refer to fixed connections, detachable connections, or integral connections; they can refer to mechanical connections or electrical connections; they can refer to direct connections or indirect connections through an intermediate medium; and they can refer to the internal communication between two components. Those skilled in the art can understand the specific meaning of the above terms in this utility model based on the specific circumstances.

[0029] The following is for reference. Figures 1-5 A piston-driven displacement mechanism is described in detail with reference to a specific embodiment. It is to be understood that the following description is merely illustrative and not intended to limit the scope of the invention.

[0030] like Figures 2-3As shown, this application proposes a piston-driven displacement mechanism, mainly comprising three key components: a main body 100, a movable drive member 140, and a rotating shaft 210. The main body 100 has a receiving cavity 110, within which a piston 120 and an elastic reset member 130 providing a reset force are disposed. The piston 120 can reciprocate within the receiving cavity 110. The movable drive member 140 is connected to the piston 120 via a shaft 170. The force-bearing portion 160 of the movable drive member 140 can freely swing left and right relative to the axis of the piston 120 in a restricted swing plane. The rotating shaft 210 is rotatably mounted to the main body 100. A cam 150 is provided within the receiving cavity 110 on the rotating shaft 210, and its profile surface maintains continuous contact with the force-bearing portion 160 of the movable drive member 140. The unique feature of this structural design is that when the door is opened or closed, the rotation of the cam 150 pushes the force-bearing part 160 through the contour surface, thereby driving the piston 120 to compress or release the elastic reset member 130. At the same time, the movable drive member 140 can adaptively adjust the relative position of the force-bearing part 160 and the cam 150 through its own swing.

[0031] In practical implementation, the structural design of the accommodating cavity 110 has several options. Depending on the actual application requirements, the accommodating cavity 110 can adopt a cylindrical or square structure, and its inner wall can be provided with guide grooves to precisely limit the movement trajectory of the piston 120. The choice of the elastic reset component 130 is also relatively flexible; it can be a coil spring, a disc spring, or a rubber elastomer, among which a pressure spring is the preferred option due to its stable performance and moderate cost. As the core moving component, the piston 120 is usually made of metal or high-strength plastic, and the sealing ring between it and the inner wall of the accommodating cavity 110 ensures sealing performance during movement. The swing plane of the movable drive component 140 can be designed to be perpendicular to the axis of the piston 120 or at a certain angle to it, depending on the spatial layout requirements. This flexibility allows the mechanism to adapt to different installation environments.

[0032] The connection between the movable drive component 140 and the piston 120 is carefully designed. The shaft 170, acting as a connecting element, has its axis perpendicular to the reciprocating motion direction of the piston 120. This arrangement ensures that the movable drive component 140 can swing freely around this axis in the swing plane. The shaft 170 can be made of solid or hollow metal material, such as stainless steel or carbon steel, to ensure sufficient rigidity and wear resistance. In practical applications, the diameter and length of the shaft 170 can be optimized and adjusted according to load requirements and space constraints. For example, a thicker shaft 170 design can be used in applications with high load requirements. This connection method is not only simple and reliable in structure, but also provides a precise axis of rotation for the smooth swing of the drive component, ensuring the stability and directional accuracy of power transmission.

[0033] The recessed cavity 180 at the end of the piston 120 further optimizes the mechanism's performance. As a concave structure located at the end of the piston 120, the cavity 180's shape matches the connecting portion 190 of the movable drive member 140, achieving stable accommodation of the connecting portion 190. The angle of the left-right swing of the force-bearing part 160 is precisely limited by the sidewall of the cavity 180 abutting against the connecting portion 190, or by the stepped surface of the force-bearing part abutting against the piston end face. The connecting portion 190 can adopt a cylindrical, prismatic, or cuboid geometric shape, while the shaft 170 can be implemented using a metal pin, needle roller bearing, or polymer bushing, with its diameter forming a precise fit with the shaft hole of the connecting portion 190. This structural design precisely restricts the movement trajectory of the swinging component within a limited space, improving the overall rigidity of the mechanism.

[0034] The cuboid design of the connecting part 190 brings significant performance improvements. When the connecting part 190 adopts a cuboid design, it swings left or right during operation, abutting against the side wall of one side of the cavity 180. This precisely limits the left and right swing angle of the force-bearing part 160, achieving a stable offset angle. This allows the piston to move according to the most effective lifting stroke of the cam, solving the problem of insufficient cam lift at the end of the closing phase, which fails to effectively drive the piston to generate hydraulic buffer closing. The connecting part 190 can be made of metal or high-strength engineering plastic, and its outer dimensions maintain an appropriate clearance fit with the inner cavity of the cavity 180 at the end of the piston 120. The shaft 170 can be made of stainless steel pin, and its diameter forms a precise transition fit with the through hole of the cylindrical shaft. To further optimize performance, annular grooves can be provided at both ends of the cylinder for installing retaining rings, effectively preventing axial movement of the shaft 170. This ensures the mechanism's high sensitivity to small angle changes.

[0035] The design of the roller 200 in the force-bearing section 160 is another important innovation. The roller 200 can employ a bearing structure, such as a deep groove ball bearing or a needle roller bearing, to minimize rotational resistance. The wear-resistant material layer, such as polyurethane or nylon, covering the outer edge of the roller 200 effectively reduces operating noise and extends service life. The axis of the roller 200 is perpendicular to the swing plane of the movable drive component 140, ensuring that the contact line with the profile surface of the cam 150 is always in the optimal force direction. The roller 200 is mounted in the U-shaped groove of the force-bearing section 160 via a pin 220. Snap rings at both ends of the pin 220 ensure free rotation of the roller 200 while preventing axial movement. This design, which converts sliding friction into rolling friction, significantly improves the operating efficiency of the mechanism.

[0036] The profile of cam 150 has been specially optimized. The conical profile refers to the tapered geometry of the surface of cam 150 in contact with the force-bearing part 160 of movable drive member 140. Its cross-sectional profile is composed of two obliquely intersecting line segments, forming a pointed structure. The tip of the conical profile has a small rounded transition, effectively avoiding stress concentration. This specially designed profile allows for a larger piston 120 drive stroke when the door is closed to a small angle, ensuring continuous hydraulic damping.

[0037] The hydraulic system design further enhances the cushioning performance. When the receiving cavity 110 is used as a hydraulic cylinder, it is filled with hydraulic oil with appropriate viscosity and temperature stability. Seals, such as rubber O-rings, polyurethane sealing rings, or metal piston rings, are installed in the annular groove on the outer edge of the piston 120, forming a dynamic seal with the inner wall of the hydraulic cylinder. When the piston 120 moves, the hydraulic oil generates flow resistance through the gap between the piston 120 and the cylinder body or through a specially designed damping orifice, creating a controllable hydraulic damping effect. The hydraulic cylinder can be equipped with an adjustable damping valve, which precisely controls the oil flow rate by changing the valve opening, achieving precise adaptation to different cushioning force requirements. This hydraulic damping mechanism effectively solves the performance limitations of traditional purely mechanical cushioning mechanisms.

[0038] The integrated application of this mechanism demonstrates broad applicability. The piston 120-driven displacement mechanism can be perfectly integrated into common door control products such as floor springs, soft-close glass clamps, or hinges with top and bottom pivots. In floor spring applications, the floor spring housing serves as the main body 100, with the receiving cavity 110 located within the floor spring housing, and the piston 120 linked to the floor spring's drive shaft. In soft-close glass clamp applications, the clamping component is fixedly connected to the door leaf, and the cam 150 is located at the pivot of the clamping component. In hinges with top and bottom pivots, the upper or lower pivot serves as the mounting position for the cam 150, and the rotation of the door leaf causes the main body 100 to rotate relative to the cam 150. These integrated solutions fully utilize the structural space of existing products, achieving a hydraulic buffering effect throughout the entire door closing process without significantly increasing the volume.

[0039] When the door begins to close, the door rotates, causing the main body 100 and the rotating shaft 210 to rotate relative to each other. This causes the piston 120 and the cam 150 to rotate circumferentially relative to each other. The contour surface of the cam 150 pushes the force-receiving part 160 of the movable drive member 140, driving the piston 120 to move within the receiving cavity 110. During this process, the movable drive member 140 automatically adjusts the relative position of the force-receiving part 160 and the cam 150 through its own oscillation, ensuring that the force-receiving part 160 is always located in front of the cam 150 in the direction of rotation. Figure 4As shown. The movement of piston 120 simultaneously compresses the elastic reset element 130 and pushes the hydraulic oil to generate a damping effect, converting the kinetic energy of the door leaf into elastic potential energy. When the door leaf is closed to a small angle range of 5° to 0°, the special profile design of cam 150 ensures that piston 120 can still maintain an effective stroke, continuously providing a cushioning effect. Figure 5 As shown, when the door opens alternately to the left and right, it turns from closing in the original direction to opening in the other direction. The geometric characteristics of the cam 150 profile result in a slight lift when it rotates, which pushes the piston forward and generates very little hydraulic resistance, having minimal impact on the opening of the door. When the door opens, the elastic reset member 130 releases the stored energy, pushing the piston 120 to reset, preparing for the next closing process.

[0040] This invention effectively solves the technical problem of insufficient drive stroke in the final stage of door closing in traditional mechanisms by utilizing the swing-adaptive characteristics of the movable drive component 140 and the special profile design of the cam 150. The mechanism can provide stable and uniform hydraulic cushioning throughout the entire door closing process, especially in the small angle range of 5° to 0°. The drive stroke of the piston 120 is... Figure 1 The increase from 0.14mm to Figure 5 With a 0.76mm reduction in piston stroke, the mechanism effectively extends the piston stroke during this stage, continuously providing sufficient hydraulic cushioning. This completely eliminates the cushioning failure problem caused by the sharp reduction in drive stroke during this stage in traditional designs, thus completely eliminating door overshoot and swaying. The innovative rolling contact design significantly reduces wear and operating noise, extending service life. The modular structural design allows for flexible integration into various door control products, greatly improving product performance and reliability. This mechanism boasts outstanding advantages such as compact structure, sensitive response, and stable cushioning effect, providing an ideal technical solution for bidirectional door control products.

[0041] In the description of this specification, references to terms such as "an embodiment," "some embodiments," "illustrative embodiments," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the present invention. In this specification, illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0042] The embodiments of the present utility model have been described in detail above with reference to the accompanying drawings. However, the present utility model is not limited to the above embodiments. Within the scope of knowledge possessed by those skilled in the art, various changes can be made without departing from the spirit of the present utility model.

Claims

1. A piston-driven displacement mechanism, characterized in that, include The main body (100) has a receiving cavity (110) inside, and a piston (120) and an elastic reset member (130) for providing a reset force are provided in the receiving cavity (110). The piston (120) can reciprocate in the receiving cavity (110). A movable drive member (140) is connected to one end of the piston (120) facing away from the elastic reset member (130) and can move left and right relative to the axis of the piston (120); A rotating shaft (210) is rotatably disposed with the main body (100). The rotating shaft (210) is provided with a cam (150) in the accommodating cavity (110). The contour surface of the cam abuts against the force-receiving part (160) of the movable drive member (140). When the door is opened and closed, the main body (100) and the rotating shaft (210) rotate relative to each other, driving the piston (120) and the cam (150) to rotate circumferentially. The force-receiving part (160) slides along the contour surface, thereby driving the piston (120) to move, compressing or releasing the elastic reset member (130). Furthermore, the movable drive member (140) can adaptively adjust the relative position of the force-receiving part (160) and the cam (150) by moving left and right, so that during the closing process of the door, the force-receiving part (160) is always located in front of the rotation direction of the cam (150).

2. The piston-driven displacement mechanism according to claim 1, characterized in that, The movable drive member (140) is provided with a shaft (170) connected to the piston (120), so that the force-receiving part (160) can swing left and right relative to the axis of the piston (120).

3. The piston-driven displacement mechanism according to claim 2, characterized in that, The piston (120) has a cavity (180) at its end. The movable drive member (140) includes a connecting part (190) housed in the cavity (180) and a force-receiving part (160) exposed in the cavity (180). The shaft (170) passes between the connecting part (190) and the piston (120).

4. The piston-driven displacement mechanism according to claim 1, characterized in that, The force-receiving part (160) of the movable drive member (140) is provided with a roller (200) and the two are connected by a pin (220). The roller (200) makes rolling contact with the profile surface of the cam (150).

5. A piston-driven displacement mechanism according to claim 1, characterized in that, The elastic reset element (130) is a pressure spring.

6. The piston-driven displacement mechanism according to claim 1, characterized in that, The profile surface of the cam (150) is conical.

7. A piston-driven displacement mechanism according to claim 1, characterized in that, The accommodating cavity (110) is a hydraulic cylinder, which is filled with hydraulic oil.

8. A piston-driven displacement mechanism according to claim 7, characterized in that, A sealing element is provided between the piston (120) and the inner wall of the accommodating cavity (110), so that the reciprocating motion of the piston (120) is controlled by hydraulic damping.

9. The piston-driven displacement mechanism according to any one of claims 1 to 8, characterized in that, The mechanism is integrated into a floor spring, a buffer glass clamp, or a top and bottom hinge.

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