Category: Patents

LeiYan Gas Springs having patents for various gas spring products and production equipments.

 

Posted by: | on January 12, 2025

Double-Cylinder Temperature Compensation Gas Spring

Patent No.:CN208778566U Date:2018-09-11

Google Patent: https://patents.google.com/patent/CN208778566U/en?oq=CN208778566U

China Patent: http://epub.cnipa.gov.cn/

Abstract

The present utility model provides a double-cylinder temperature compensation gas spring, comprising: a piston rod, an outer cylinder, a guide sealing device, a piston, an inert gas, a rear plug, a spring, a floating piston, and an inner cylinder. During use, the inert gas is filled into the chamber under high pressure, and the pressure of the gas acts on the floating piston. The spring connected to the floating piston generates a corresponding amount of compression. Since the pressure of the inert gas varies with temperature, the compression of the floating piston changes accordingly. When the temperature rises and the pressure of the inert gas increases, the floating piston is further compressed. Conversely, when the temperature drops and the pressure of the inert gas decreases, the floating piston is further extended. This way, the overall volume of the inert gas is adjusted through the change in the position of the floating piston, mitigating the effect of temperature changes on the pressure of the inert gas in the chamber and ensuring the relatively stable force output of the gas spring.

Description
A Double-Cylinder Temperature Compensation Gas Spring

Technical Field
The present utility model relates to the technical field of gas springs, and more particularly to a double-cylinder temperature compensation gas spring.

Background Technology
The gas spring operates by the pressure differential formed by the gas pressure on both sides of the gas spring piston. Since the pressure difference is determined by the area difference on both sides of the piston, the elastic force output by the gas spring is completely determined by the pressure of the gas inside it. As gas pressure is easily affected by temperature, mitigating the effect of temperature changes on the elastic force output of gas springs has become an urgent technical problem to be solved in this field.

Utility Model Content
The purpose of this utility model is to propose a double-cylinder temperature compensation gas spring that can mitigate the effect of temperature changes on the internal pressure of the gas spring.

This utility model provides a double-cylinder temperature compensation gas spring, which includes: a piston rod, an outer cylinder, a guide sealing device, a piston, an inert gas, a rear plug, a spring, a floating piston, and an inner cylinder. The guide sealing device is connected to the front-end opening of the outer cylinder, and the rear plug is connected to the rear-end opening of the outer cylinder. The outer cylinder, guide sealing device, and rear plug form the overall chamber of the gas spring. Inside the chamber, a coaxial inner cylinder is placed between the rear plug and the guide sealing device. The inner cylinder divides the chamber into an inner cavity and an outer cavity, which are connected through vent holes on the sidewall of the inner cylinder. The piston is slidably connected in the inner cavity. One end of the piston rod is connected to the piston, while the other end extends out of the outer cylinder through the guide sealing device. The diameter of the piston is slightly smaller than the inner cylinder’s diameter, and the diameter of the piston rod is slightly smaller than the inner cylinder’s diameter. Both the piston and the piston rod are coaxial with the outer cylinder. The floating piston is slidably connected in the outer cavity and is annular, with its outer ring’s diameter slightly smaller than the inner diameter of the outer cylinder and its inner ring’s diameter slightly larger than the outer diameter of the inner cylinder. The spring is installed in the outer cavity between the floating piston and the guide sealing device. Both the inner cavity and the outer cavity part of the floating piston are filled with inert gas.

During use, the inert gas is filled into the chamber under high pressure, acting on both sides of the piston. Since the piston rod and piston are riveted together, the pressure areas on both sides of the piston are different, generating an outward extension force on the piston. The internal pressure of the chamber also acts on one side of the floating piston. The floating piston is compressed by the mechanical spring corresponding to this pressure. When the unit volume of the inert gas changes due to temperature variations, the pressure changes accordingly, causing the floating piston to displace due to the pressure difference. When the temperature rises, the increased pressure of the inert gas causes the floating piston to compress further towards the auxiliary spring direction. When the temperature decreases, the floating piston displaces towards the gas chamber under the action of the auxiliary spring. This compensates for the pressure inside the gas chamber due to the changes in the total volume of inert gas caused by temperature variations, thereby reducing the effect of temperature changes on the internal pressure of the inert gas inside the chamber and ensuring the relatively stable output force of the gas spring.

Further, the vent hole is arranged on the inner wall of the inner cylinder near the rear plug.
Further, a sealing ring is arranged between the guide sealing device and the outer cylinder.
Further, a sealing ring is arranged between the guide sealing device and the inner cylinder.
Further, a sealing ring is arranged between the piston and the inner cylinder.
Further, a sealing ring is arranged between the floating piston and the inner cylinder.
Further, a sealing ring is arranged between the floating piston and the outer cylinder.

Additional aspects and advantages of the present utility model will be partially given in the description below, partially apparent from the description below, or learned through the practice of the present utility model.

Brief Description of the Drawings
Figure 1 is a schematic structural diagram of a double-cylinder temperature compensation gas spring according to an embodiment of the present utility model.
The marks in the attached drawings are as follows:
Piston rod
Outer cylinder
Guide sealing device
Piston
Inert gas
Rear plug
Spring
Floating piston
Vent hole
Inner cylinder
Inner cavity
Outer cavity
Sealing ring

Detailed Description of Preferred Embodiments
The embodiments of the present utility model will be described in detail below. The exemplary embodiments are shown in the drawings, wherein identical or similar reference numerals indicate identical or similar elements or elements having the same or similar functions throughout the drawings. The embodiments described below with reference to the accompanying drawings are illustrative and are intended to explain the present utility model, but should not be construed as limiting the present utility model.

An embodiment of the present utility model provides a double-cylinder temperature compensation gas spring, as shown in Figure 1, which includes: the piston rod 1, the outer cylinder 2, the guide sealing device 3, the piston 4, the inert gas 5, the rear plug 6, the spring 7, the floating piston 8, and the inner cylinder 10. The guide sealing device 3 is connected to the front-end opening of the outer cylinder 2, and the rear plug 6 is connected to the rear-end opening of the outer cylinder 2. The outer cylinder 2, guide sealing device 3, and rear plug 6 form the chamber of the gas spring. Additionally, a coaxial inner cylinder 10 is designed between the rear plug 6 and the guide sealing device 3, dividing the chamber into an inner cavity 11 and an outer cavity 12. The inner cavity 11 and the outer cavity 12 are connected through a vent hole 9 arranged on the sidewall of the inner cylinder 10. The piston 4 is slidably connected in the inner cavity 11. One end of the piston rod 1 is connected to the piston 4, and the other end extends out of the outer cylinder 2 through the guide sealing device 3. The diameter of the piston 4 is equal to that of the inner cylinder 10, and the diameter of the piston rod 1 is smaller than that of the inner cylinder 10. Both the piston 4 and the piston rod 1 are coaxial with the outer cylinder 2. The floating piston 8 is slidably connected in the outer cavity 12. The floating piston 8 is annular, with its outer ring surface tightly attached to the inner surface of the outer cylinder 2, and its inner ring surface tightly attached to the outer surface of the inner cylinder 10. The spring 7 is connected in the outer cavity 12 between the floating piston 8 and the guide sealing device 3. The entire inner cavity 11 and the outer cavity 12 part of the floating piston are filled with the inert gas. Here, the outer cavity on the side opposite the spring with respect to the floating piston is meant.

During use, the inert gas is filled into the chamber of the gas spring under high pressure, acting on both sides of the piston. Due to the close connection between the piston rod and the piston, the pressure areas on both sides of the piston are different, creating an outward extension force on the piston. Meanwhile, the pressure inside the chamber also acts on the floating piston, and the spring connected to it generates a corresponding amount of compression. Since the pressure of the inert gas varies with temperature changes, the displacement amount of the floating piston due to the pressure also varies. When the temperature increases and the pressure of the inert gas rises, the floating piston will further displace towards the auxiliary spring. Conversely, when the temperature decreases and the pressure of the inert gas drops, the floating piston will further displace towards the gas chamber under the action of the auxiliary spring. This compensates for the change in the total volume of the inert gas within the gas chamber, thereby reducing the effect of temperature changes on the pressure of the inert gas within the chamber and ensuring the relatively stable force output of the gas spring.

In one aspect of the embodiment of this utility model, sealing rings 13 are arranged between the guide sealing device 3 and the outer cylinder 2, between the guide sealing device 3 and the inner cylinder 10, between the piston 4 and the inner cylinder 10, between the floating piston 8 and the inner cylinder 10, and between the floating piston 8 and the outer cylinder 2. The arrangement of sealing rings ensures the air-tightness between the contact surfaces of each component, improving the performance of the gas spring.

Although the embodiments of the present utility model have been shown and described above, it is understood that these embodiments are illustrative and not restrictive. Those skilled in the art can make variations, modifications, substitutions, and alterations within the scope of the present utility model.

Claims – Double-Cylinder Temperature Compensation Gas Spring, invented by LeiYan Gas Spring, a pioneer Chinese Gas Spring Manufacture

  1. A double-cylinder temperature compensation gas spring, characterized by comprising:
    A piston rod, an outer cylinder, a guide sealing device, a piston, an inert gas, a rear plug, a spring, a floating piston, and an inner cylinder;
    The guide sealing device is connected to the front-end opening of the outer cylinder, the rear plug is fixed and sealed at the rear-end opening of the outer cylinder, and the outer cylinder, guide sealing device, and rear plug form the overall chamber of the gas spring. A coaxial inner cylinder is arranged between the rear plug and the guide sealing device, dividing the chamber into an inner cavity and an outer cavity, which are connected through a vent hole arranged on the sidewall of the inner cylinder;
    The piston is slidably connected in the inner cavity, one end of the piston rod is connected to the piston, and the other end extends out of the outer cylinder through the guide sealing device. The diameter of the piston is equal to that of the inner cylinder, the diameter of the piston rod is smaller than that of the inner cylinder, and both the piston and piston rod are coaxial with the outer cylinder;
    The floating piston is slidably connected in the outer cavity. The floating piston is annular, with its outer ring surface tightly attached to the inner surface of the outer cylinder and its inner ring surface tightly attached to the outer surface of the inner cylinder, serving a bidirectional dynamic sealing role. The spring is connected in the outer cavity between the floating piston and the guide sealing device;
    The entire inner cavity and the outer cavity part of the floating piston are filled with the inert gas.
  2. The double-cylinder temperature compensation gas spring according to claim 1, characterized in that the vent hole is arranged on the inner wall of the inner cylinder near the rear plug.
  3. The double-cylinder temperature compensation gas spring according to claim 1, characterized in that a sealing ring is arranged between the guide sealing device and the outer cylinder.
  4. The double-cylinder temperature compensation gas spring according to claim 1, characterized in that a sealing ring is arranged between the guide sealing device and the inner cylinder.
  5. The double-cylinder temperature compensation gas spring according to claim 1, characterized in that a sealing ring is arranged between the piston and the inner cylinder.
  6. The double-cylinder temperature compensation gas spring according to claim 1, characterized in that a sealing ring is arranged between the floating piston and the inner cylinder.
  7. The double-cylinder temperature compensation gas spring according to claim 1, characterized in that a sealing ring is arranged between the floating piston and the outer cylinder.

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Posted by: | on January 10, 2025

A Window Damper with Buffering Assistance during Compression

Patent No.:CN208858845U Date:2018-09-11

Google Patent: https://patents.google.com/patent/CN208858845U/en?oq=CN208858845U

China Patent: http://epub.cnipa.gov.cn/

Abstract

This utility model provides a window damper with buffering and assisting force during compression, including: a hollow piston rod assembly rod, a guide sleeve, a cylinder, a movable locking rod, a return spring, a locking block, a locking block rubber sleeve, and a positioning clamp sleeve. Using this utility model, when the car window is opened, the damper extends, at which point the return spring is in a reset state. When the locking block rubber sleeve enters the narrow cavity part of the cylinder from the wide cavity part of the cylinder, it generates a certain amount of friction with the inner wall of the narrow cavity part of the cylinder, allowing the window to stop at any angle; after the window is fully opened, if the wind blows the window, the damper will enter a compressed state. At this point, the return spring is first compressed, and the elliptical ball-shaped part on the movable locking rod moves, entering the narrow cavity part of the locking block from the wide cavity part, causing the locking block to expand outward, further increasing the friction between the locking block rubber sleeve and the narrow cavity part of the cylinder. This ensures that the opened window is not easily closed by the wind, providing a buffering and assisting force.

Description – A Window Damper with Buffering Assistance during Compression

Technical Field

This utility model belongs to the technical field of dampers, particularly to a window damper with buffering and assisting force during compression.

Background Technology

When operating windows, it’s often necessary to connect a positioning component to maintain the window’s stable state. In existing technology, the components generally used are linkage mechanisms, which, when the window is propped open, can easily be blown back by the wind, failing to effectively maintain the window’s stable open state.

Summary of the Utility Model

The objective of this utility model is to propose a damper with different damping forces during stretching and compression processes, making it easy to open the window, while preventing the window from closing at will when encountering a certain amount of wind.

This utility model provides a window damper with buffering assistance during compression, which includes a hollow piston rod, a cylinder, a movable locking rod, a return spring, a locking block, a locking block rubber sleeve, and a positioning clamp sleeve.

The cylinder’s middle part is designed with a cylinder diameter expansion opening, which divides the inner cavity of the cylinder into a front narrow cavity part and a rear wide cavity part. The movable locking rod is installed inside the cylinder’s inner cavity, with the front end of the movable locking rod coaxially connected to the hollow piston rod assembly. At the connection point of the movable locking rod and the hollow piston rod assembly, there is a spring positioning boss, whose diameter is smaller than the inner diameter of the cylinder’s narrow cavity part.

The return spring is installed on the movable locking rod, behind the spring positioning boss, and the back part of the movable locking rod is designed with an elliptical ball protrusion. The locking block is fitted outside the elliptical ball protrusion, with an internal stepped transition opening inside the locking block, which divides the internal cavity of the locking block into a front wide cavity part and a rear narrow cavity part.

The locking block rubber sleeve fits outside the locking block, with its diameter smaller than the cylinder’s wide cavity part and larger than the cylinder’s narrow cavity part. The positioning clamp sleeve is fixed at a corresponding position on the back end of the movable locking rod, with its diameter larger than the inner diameter of the cylinder’s narrow cavity part.

When the damper stretches, the locking block rubber sleeve moves from the cylinder’s wide cavity part into the narrow cavity part, creating friction with the inner wall of the narrow cavity part. This friction is greater than or equal to the maximum compression force value of the return spring.

When using this utility model, during window opening, the damper is in the stretching motion, with the locking block rubber sleeve creating friction with the inner wall of the cylinder’s narrow cavity part. This friction force is greater than or equal to the maximum compression force value of the return spring. When the window stops at any angle, if wind moves the window, the damper enters a compressed state. The return spring first compresses, moving the elliptical ball protrusion on the movable locking rod from the wide cavity part of the locking block into the narrow cavity part, expanding the locking block outward. This increases the friction between the locking block rubber sleeve and the narrow cavity part of the cylinder, preventing the window from being easily closed by the wind, providing buffering and resistance.

Further Details

Furthermore, the movable locking rod on the front side of the positioning clamp sleeve is also equipped with an anti-slip buffer rubber ring.

Further, a guide sleeve is installed at the front end opening of the cylinder. The inner diameter of the guide sleeve and the outer diameter of the hollow piston rod are slide-fitted.

Additionally, a slot is provided on the outer wall of the guide sleeve, and it is connected to the front end opening of the cylinder through the slot.

Furthermore, a rear block connecting piece is installed at the rear end opening of the cylinder.

The portion of the rear block connecting piece located inside the cylinder has a circular groove that is coaxial with the movable locking rod.

Further, the cylinder diameter expansion opening and the stepped transition opening are both arc-shaped transitions.

Additional aspects and advantages of this utility model will be partially illustrated in the following description, partially become apparent from the description, or be learned through the practice of this utility model.

Description of Drawings

Figure 1 is a schematic structural diagram of a window damper with buffering assistance during compression according to an embodiment of this utility model.

Figure 2 is a schematic structural diagram of the stretched state of the window damper with buffering assistance during compression according to an embodiment of this utility model.

Figure 3 is a schematic structural diagram of the compressed state of the window damper with buffering assistance during compression according to an embodiment of this utility model.

Reference Marked in the Drawings:

1 – Hollow piston rod assembly 2 – Guide sleeve 2 – Slot 3 – Cylinder 31 – Cylinder diameter expansion opening 4 – Movable locking rod 41 – Spring positioning boss 42 – Elliptical ball protrusion 5 – Return spring 6 – Locking block 61 – Stepped transition opening 7 – Locking block rubber sleeve 8 – Anti-slip buffer rubber ring 9 – Positioning clamp sleeve 10 – Rear block connecting piece 101 – Groove

Specific Embodiments

The embodiments of this utility model are described in detail below. The examples of the embodiments are shown in the drawings, where the same or similar reference numbers indicate the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the drawings are exemplary and are intended to explain this utility model rather than to limit it.

The embodiments of this utility model provide a window damper with buffering assistance during compression, as shown in Figure 1, including a hollow piston rod assembly (1), a cylinder (3), a movable locking rod (4), a return spring (5), a locking block (6), a locking block rubber sleeve (7), and a positioning clamp sleeve (9).

When describing this utility model, the position of the hollow piston rod assembly (1) is considered the front, and the position of the positioning clamp sleeve (9) is considered the rear. The middle part of the cylinder (3) is provided with a cylinder diameter expansion opening (31), which divides the inner cavity of the cylinder (3) into a front narrow cavity part and a rear wide cavity part. The movable locking rod (4) can move telescopically inside the inner cavity of the cylinder (3). The front end of the movable locking rod (4) is coaxially connected to the hollow piston rod assembly (1). At the connection point of the movable locking rod (4) and the hollow piston rod assembly (1), a spring positioning boss (41) is designed, with a diameter smaller than the inner diameter of the cylinder’s narrow cavity part. The return spring (5) is installed on the movable locking rod (4) behind the spring positioning boss (41). The back part of the movable locking rod (4) is also designed with an elliptical ball protrusion (42).

The locking block (6) is fitted outside the elliptical ball protrusion (42), with an internal stepped transition opening (61) inside the locking block (6), dividing its internal cavity into a front wide cavity part and a rear narrow cavity part. The locking block rubber sleeve (7) is fitted outside the locking block (6), with a diameter smaller than the cylinder’s wide cavity part but slightly larger than the cylinder’s narrow cavity part. Preferably, the locking block is made of high-tenacity elastic material. The positioning clamp sleeve (9) is fixedly connected to the rear end of the movable locking rod (4), with a diameter smaller than the internal diameter of the cylinder’s narrow cavity part. The positioning clamp sleeve prevents the movable locking rod from slipping out and stays in the cylinder’s wide cavity part when the car window is closed.

When the damper stretches, the locking block rubber sleeve (7) moves from the cylinder’s wide cavity part into the narrow cavity part, creating a certain amount of friction with the inner wall of the narrow cavity part. This friction amount is determined based on different car window weights, ensuring it’s light enough for the window to stay open at any angle but also greater or equal to the maximum compression force value of the return spring (5).

Preferably, the cylinder diameter expansion opening (31) and the stepped transition opening (61) are both arc-shaped transitions to ensure smooth movement of the locking block rubber sleeve and the elliptical ball protrusion without causing jamming.

When using this utility model, as shown in Figure 2, the damper is in the stretched state when the window is opened. The locking block rubber sleeve (7) moves from the cylinder’s wide cavity part into the narrow cavity part, creating the necessary friction with the inner wall of the cylinder’s narrow cavity part. This friction amount is determined based on the car window’s size and weight but also must be greater or equal to the maximum compression force value of the return spring (5) for the window to stay in place at any position. When the window is fully opened, if wind moves the window, as shown in Figure 3, the damper enters a compressed state. At this point, the return spring (5) is compressed, and the elliptical ball protrusion (42) moves from the wide cavity part of the locking block (6) into the narrow cavity part, causing the locking block (6) to expand outward. This increases the friction between the locking block rubber sleeve (7) and the narrow cavity part of the cylinder, preventing the opened window from being closed by the wind and providing buffering assistance.

Further Implementation of the Utility Model

In one aspect of the embodiments of this utility model, an anti-slip buffer rubber ring (8) is also installed on the movable locking rod (4) at the front side of the positioning clamp sleeve (9). The anti-slip buffer rubber ring compensates for the excessive movement caused by the assembly gap of components like the locking block and mitigates the impact on the positioning clamp sleeve.

In one aspect of the embodiments of this utility model, a guide sleeve (2) is connected to the front end opening of the cylinder (3). The inner diameter of the guide sleeve (2) is slide-fitted with the diameter of the hollow piston rod assembly (1). A slot (21) is designed on the outer wall of the guide sleeve (2), and the guide sleeve (2) is pressed and positioned connected to the front end opening of the cylinder (3) through the slot (21). The setup of the guide sleeve and the slot ensures the precise coaxial connection of the hollow piston rod assembly and the front end of the cylinder, enhancing tensile strength and movement stability.

In one aspect of the embodiments of this utility model, a rear block connecting piece (10) is connected to the rear end opening of the cylinder (3). Portions of the rear block connecting piece (10) within the cylinder (3) have a circular groove (101) coaxial with the movable locking rod. The design of the rear block connecting piece serves a dual purpose: it connects the damper to the window and limits the position of the movable locking rod within the cylinder. When the window is closed under human force, the locking block and locking block rubber sleeve are fully retracted into the wide cavity part of the cylinder. The return spring naturally opens in the wide cavity part of the cylinder, and the elliptical ball protrusion retracts into the wide cavity part of the locking block.

Although the embodiments of this utility model have been shown and described above, it is understood that the above embodiments are exemplary and not to be construed as limiting this utility model. Those skilled in the field can make variations, modifications, replacements, and alterations to the above embodiments within the scope of this utility model.

Claims – A Window Damper with Buffering Assistance during Compression,  invented by LeiYan Gas Spring, a pioneer Chinese Gas Spring Manufacture

  1. A window damper with buffering assistance during compression, characterized by:
    • A hollow piston rod assembly, a cylinder, a movable locking rod, a return spring, a locking block, a locking block rubber sleeve, and a positioning clamp sleeve;
    • The middle part of the cylinder is provided with a cylinder diameter expansion opening, which divides the inner cavity of the cylinder into a front narrow cavity part and a rear wide cavity part;
    • The movable locking rod is telescopically installed inside the inner cavity of the cylinder, with the front end of the movable locking rod coaxially connected to the hollow piston rod assembly. The rear side of the connection point between the movable locking rod and the hollow piston rod assembly is provided with a spring positioning boss. The diameter of the spring positioning boss is smaller than the inner diameter of the cylinder’s narrow cavity part. The return spring is installed on the movable locking rod behind the spring positioning boss. The movable locking rod on the rear side of the return spring is also provided with an elliptical ball protrusion;
    • The locking block is sleeved on the outer side of the elliptical ball protrusion, and the internal cavity of the locking block is provided with a stepped transition opening, dividing its internal cavity into a front wide cavity part and a rear narrow cavity part. The locking block rubber sleeve is sleeved on the outer side of the locking block. The outer diameter of the locking block rubber sleeve is smaller than the inner diameter of the cylinder’s wide cavity part but larger than the inner diameter of the cylinder’s narrow cavity part;
    • The positioning clamp sleeve is fixedly connected to the rear end of the movable locking rod, and its outer diameter is larger than the inner diameter of the cylinder’s narrow cavity part;
    • When the damper stretches, the locking block rubber sleeve moves from the cylinder’s wide cavity part into the narrow cavity part, creating friction with the inner wall of the narrow cavity part. This friction force is greater than or equal to the maximum compression force of the return spring.
  2. The window damper with buffering assistance during compression according to claim 1, characterized by:
    • The positioning clamp sleeve’s front side of the movable locking rod is also fitted with an anti-slip buffer rubber ring.
  3. The window damper with buffering assistance during compression according to claim 1, characterized by:
    • A guide sleeve is fixed at the front end opening of the cylinder. The inner diameter of the guide sleeve is greater than that of the hollow piston rod assembly, which slides within the guide sleeve.
  4. The window damper with buffering assistance during compression according to claim 3, characterized by:
    • A slot is provided on the outer wall of the guide sleeve, and the guide sleeve is fastened to the front end opening of the cylinder through the slot.
  5. The window damper with buffering assistance during compression according to claim 1, characterized by:
    • A rear block connecting piece is connected to the rear end opening of the cylinder.
  6. The window damper with buffering assistance during compression according to claim 5, characterized by:
    • Portions of the rear block connecting piece within the cylinder have a circular groove that is coaxial with the movable locking rod.
  7. The window damper with buffering assistance during compression according to any of claims 1-6, characterized by:
    • Both the cylinder diameter expansion opening and the stepped transition opening are arc-shaped transitions.

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Posted by: | on January 9, 2025

Dual-Sided Anti-Rotation Linear Telescopic Electric Compressed Gas Spring

Patent No.:CN207934684U Date:2017-07-11

Google Patent: https://patents.google.com/patent/CN207934684U/en?oq=CN207934684U

China Patent: http://epub.cnipa.gov.cn/

Abstract: 

This utility model proposes a dual-sided anti-rotation linear telescopic electric compressed gas spring, which includes a cylinder with a drive device installation section. The outer end of the drive device installation section is equipped with an anti-rotation sealing rear plug. The part of the cylinder close to this installation section is equipped with drive device fasteners and a first sealing guide assembly. A screw and a piston nut are installed inside the cylinder. One end of the screw matches the first sealing guide assembly. The outer edge of the piston nut slides along the inner wall of the cylinder. An anti-rotation structure is set within the cylinder to limit the rotation of the piston nut. A piston rod fixedly connected to the piston nut is installed on the other side of the cylinder. The other side of the cylinder is equipped with a second sealing guide assembly.

This utility model uses an electric drive device as a compensating force, eliminating the need for the user to apply external force. An anti-rotation sealing rear plug is installed at one end of the cylinder, and an anti-rotation structure to limit the rotation of the piston nut is set within the cylinder. The anti-rotation structure and the anti-rotation sealing rear plug form a dual-sided anti-rotation structure, improving the structural stability of the gas spring and extending its service life.

Description – Dual-Sided Anti-Rotation Linear Telescopic Electric Compressed Gas Spring

Technical Field: This utility model relates to a dual-sided anti-rotation linear telescopic electric compressed gas spring.

Background Technology: Currently, existing electric push rods have a mechanical spring structure. When in use, the elastic force of the mechanical spring tends to decay over time due to being in a compressed state for long periods, resulting in a shorter service life. Electric push rods with a mechanical spring structure are not only large in size but also have low output force, requiring wide and deep tailgate rain grooves, affecting the tailgate design, and leading to higher direct and indirect costs. Gas springs are industrial accessories that can support, cushion, brake, adjust height, and adjust angle. When used, gas springs have significant advantages over mechanical springs: they have a relatively slow speed, minimal dynamic force changes, and are easy to control, making them quite popular. Therefore, how to provide an electric push rod with a gas spring structure that is stable, cost-effective, and has a long service life is a technical problem that needs to be addressed by professionals in this field.

In light of this, the utility model is proposed.

Content of the Utility Model: The utility model aims to address at least one of the technical problems in the related technology to some extent. To achieve this, the utility model proposes a dual-sided anti-rotation linear telescopic electric compressed gas spring. The specific technical scheme is as follows:

A dual-sided anti-rotation linear telescopic electric compressed gas spring, including a cylinder storing power gas, with one side of the cylinder provided with a drive device installation section. A drive device is installed within the drive device installation section, and the outer end of the drive device installation section is equipped with an anti-rotation sealing rear plug to secure the drive device. The part of the cylinder near the drive device installation section is sequentially provided with drive device fasteners and a first sealing guide assembly from the outside in. A screw connected to the drive device and a piston nut threaded to the screw are installed inside the cylinder. One end of the screw is placed inside the first sealing guide assembly and matches the first sealing guide assembly. The outer edge of the piston nut slides along the inner wall of the cylinder, and an anti-rotation structure to limit the rotation of the piston nut is set along the length of the inner wall of the cylinder. The other side of the cylinder is equipped with a piston rod fixedly connected to the piston nut, and the end of the other side of the cylinder is equipped with a second sealing guide assembly matching the piston rod.

According to the dual-sided anti-rotation linear telescopic electric compressed gas spring provided by the utility model, the electric drive device serves as a compensating force, eliminating the need for users to apply external force. An anti-rotation sealing rear plug is installed at the first end of the cylinder to secure the drive device and prevent shaking or shifting during operation. Additionally, an anti-rotation structure to limit the rotation of the piston nut is set within the cylinder, and this anti-rotation structure, along with the anti-rotation sealing rear plug, forms a dual-sided anti-rotation structure, further improving the structural stability of the gas spring and extending its service life.

Additionally, the dual-sided anti-rotation linear telescopic electric compressed gas spring according to the above embodiments of the utility model may have the following additional technical features:

  1. According to one example of the utility model, the anti-rotation structure comprises multiple anti-rotation grooves or protrusions axially extending along the inner wall of the cylinder, and the outer edge of the piston nut is provided with multiple anti-rotation protrusions or grooves that match the inner wall of the cylinder.
  2. According to one example of the utility model, the anti-rotation structure comprises an anti-rotation sleeve installed on the inner wall of the cylinder, and the inner wall of the anti-rotation sleeve is provided with multiple anti-rotation grooves or protrusions axially extending along the sleeve, and the outer edge of the piston nut is provided with multiple anti-rotation protrusions or grooves that match the anti-rotation sleeve.
  3. According to one example of the utility model, the middle part of the anti-rotation sealing rear plug is provided with an anti-rotation connection hole that matches an external anti-rotation connection member, a drive device outlet hole below the anti-rotation connection hole, and the outer edge of the anti-rotation sealing rear plug is provided with an anti-rotation shoulder that matches the positioning anti-rotation notch at the end of the cylinder, and the outer edge of the anti-rotation sealing rear plug is further provided with a limit groove and a waterproof sealing groove that match the inner wall of the cylinder.
  4. According to one example of the utility model, the first sealing guide assembly comprises bearings and multiple guide sleeves arranged at intervals from the inside to the outside of the cylinder, and the outer edges of the guide sleeves and bearings are connected to the inner wall of the cylinder, and seals are installed between the bearings and guide sleeves and between the two guide sleeves.
  5. According to one example of the utility model, the second sealing guide assembly comprises at least two guide sleeves arranged at intervals and seals installed between the guide sleeves.
  6. According to one example of the utility model, the drive device comprises a motor connected to the anti-rotation sealing rear plug and a reducer connected to the motor and the screw.
  7. According to one example of the utility model, the drive device fastener is a reducer anti-rotation combined fixing member installed between the reducer and the first sealing guide assembly, and the reducer anti-rotation combined fixing member is connected to the inner wall of the reducer and the cylinder.
  8. According to one example of the utility model, the screw is a multi-head screw, and the piston nut is a multi-head nut that matches the multi-head screw.
  9. According to one example of the utility model, the power gas is an inert gas.

The additional aspects and advantages of the utility model will be partially given in the following description and will become apparent from the following description or through the practice of the utility model.

Description of Drawings:

  • Figure 1 is a structural schematic diagram of the dual-sided anti-rotation linear telescopic electric compressed gas spring of this embodiment.
  • Figure 2 is an anti-rotation structure of the dual-sided anti-rotation linear telescopic electric compressed gas spring of this embodiment.
  • Figure 3 is a piston nut of the dual-sided anti-rotation linear telescopic electric compressed gas spring of this embodiment.
  • Figure 4 is another anti-rotation structure of the dual-sided anti-rotation linear telescopic electric compressed gas spring of this embodiment.
  • Figure 5 is another piston nut of the dual-sided anti-rotation linear telescopic electric compressed gas spring of this embodiment.
  • Figure 6 is a structural schematic diagram of the anti-rotation sealing rear plug (one) of the dual-sided anti-rotation linear telescopic electric compressed gas spring of this embodiment.
  • Figure 7 is a structural schematic diagram of the anti-rotation sealing rear plug (two) of the dual-sided anti-rotation linear telescopic electric compressed gas spring of this embodiment.
  • Figure 8 is a structural schematic diagram of the anti-rotation sealing rear plug (three) of the dual-sided anti-rotation linear telescopic electric compressed gas spring of this embodiment.

In the figures:

  1. Cylinder
  2. Drive Device Installation Section
  3. Screw
  4. Piston Nut
  5. Air Passage Hole
  6. Anti-Rotation Structure
  7. Hollow Piston Rod
  8. Anti-Rotation Sealing Rear Plug
  9. Anti-Rotation Connection Hole
  10. Outlet Hole
  11. Anti-Rotation Shoulder
  12. Limit Slot
  13. Waterproof Sealing Groove
  14. First Sealing Guide Assembly
  15. Bearing
  16. Guide Sleeve
  17. Seal
  18. Second Sealing Guide Assembly
  19. Drive Device
  20. Drive Device Fastener
  21. Anti-Rotation Protrusion
  22. Anti-Rotation Groove
  23. Motor
  24. Reducer

Specific Implementation Method: The following describes the embodiments of this utility model in detail. The examples of the embodiments are shown in the figures, where the same or similar reference numbers throughout indicate the same or similar elements or elements with the same or similar functions. The embodiments described below with reference to the figures are exemplary and intended to explain this utility model, and should not be understood as limiting this utility model.

The dual-sided anti-rotation linear telescopic electric compressed gas spring according to the utility model is described in detail with reference to the figures.

As shown in Figure 1, this embodiment provides a dual-sided anti-rotation linear telescopic electric compressed gas spring, including a cylinder (1) storing power gas. One side of the cylinder (1) is provided with a drive device installation section (101), and a drive device (9) is installed inside the drive device installation section (101). The outer end of the drive device installation section (101) is equipped with an anti-rotation sealing rear plug (6) to secure the drive device, preventing shaking or shifting during operation. The part of the cylinder (1) near the drive device installation section (101) is sequentially provided with a drive device fastener (10) and a first sealing guide assembly (7) from the outside in. Inside the cylinder (1), a screw (2) connected to the drive device (9) and a piston nut (3) threaded to the screw (2) are installed. One end of the screw (2) is placed inside the first sealing guide assembly (7) and matches the first sealing guide assembly (7). The outer edge of the piston nut (3) slides along the inner wall of the cylinder (1), and an anti-rotation structure (4) to limit the rotation of the piston nut (3) is set along the length of the inner wall of the cylinder (1). The other side of the cylinder (1) is equipped with a hollow piston rod (5) fixedly connected to the piston nut (3), and the end of the other side of the cylinder (1) is equipped with a second sealing guide assembly (8) matching the hollow piston rod (5).

Specifically, in this embodiment, the screw (2) is a multi-head screw, and the piston nut (3) is formed by designing a multi-head nut inside the piston. The multi-head nut and piston can be integrally injection molded, and the piston nut (3) slides along the inner wall of the cylinder (1) under the rotation of the screw (2).

As shown in Figures 6-8, the middle part of the anti-rotation sealing rear plug (6) in this embodiment is provided with an anti-rotation connection hole (601) that matches the motor. The anti-rotation connection hole (601) is riveted to the connector to secure the motor, and an outlet hole (602) for the drive device leads is provided below the anti-rotation connection hole (601). The outer edge of the anti-rotation sealing rear plug (6) is sequentially provided with an anti-rotation shoulder (603) that matches the anti-rotation notch of the cylinder (1), a limit slot (604) that matches the inner wall of the cylinder, and a waterproof sealing groove (605) from the outside in. The anti-rotation sealing rear plug (6) not only functions as a waterproof seal but also combines with the cylinder (1) to form an anti-rotation structure, longitudinally positioning the motor to prevent movement and providing an outlet hole to align the motor’s power and signal wires. Additionally, it ensures the anti-rotation performance and pull-out strength after crimping the anti-rotation rear plug and the cylinder.

The anti-rotation structure (4) in this embodiment has various forms. For example, as shown in Figures 2 and 3, the anti-rotation structure (4) comprises multiple anti-rotation protrusions (11) arranged along the length of the inner wall of the cylinder, and the outer edge of the piston nut (3) is provided with multiple anti-rotation grooves (12) that match the anti-rotation protrusions. Additionally, the piston nut (3) is provided with air passage holes (301). More specifically, in this embodiment, four anti-rotation protrusions (11) are symmetrically distributed on the anti-rotation structure (4), and the piston nut (3) is provided with four anti-rotation grooves (12) that match them.

As shown in Figures 4 and 5, another example of the anti-rotation structure (4) is an anti-rotation sleeve installed on the inner wall of the cylinder, which is tightly connected to the inner wall of the cylinder (1). The inner wall of the anti-rotation sleeve is provided with multiple anti-rotation grooves (12) extending along its length, and the outer edge of the piston nut (3) is provided with multiple anti-rotation protrusions (11) that match the anti-rotation grooves (12). This structure can effectively limit the rotation of the piston nut (3). Of course, the structure is not limited to this, and other anti-rotation structures known to those skilled in the art are also within the scope of protection of this embodiment, which will not be described one by one here.

As shown in Figure 1, the first end of the cylinder (1) has a drive device installation section (101), specifically, the drive device (9) consists of a motor (13) and a reducer (14) connected to it. The motor (13) is connected to the anti-rotation sealing rear plug (6), and the reducer (14) is fixed to the inner wall of the cylinder using the drive device fastener (10). The reducer (14) is connected to the screw (2), more specifically, one end of the screw is inserted into the internal spline of the reducer, and the other part of the screw (2) is also installed in the sealing guide assembly (7).

By rotating the motor (13), the screw (2) is driven to rotate, thereby sliding the piston nut (3) and providing compensating force. The drive device fastener (10) is a reducer anti-rotation combined fixing member installed between the reducer (14) and the first sealing guide assembly (7), and it is connected to the inner wall of the reducer (14) and the cylinder (1), functioning to fix the reducer (14) and prevent its rotation. The motor in this embodiment preferably uses a 9V-12V DC power supply, and the motor is equipped with interfaces for power input, speed, and direction decoding signal output (not shown). The electronic control part of the motor is implemented by an external controller, which can be selected according to functional needs, and will not be described in detail here.

Additionally, to further improve structural stability and sealing performance, this embodiment is equipped with a first sealing guide assembly (7) and a second sealing guide assembly (8) at the left and right ends of the cylinder (1). The first end of the screw (2) is guided and fixed by the first guide sealing assembly (7), and the hollow piston rod (5) is guided and fixed by the second sealing guide assembly (8). Specifically, as shown in Figure 1, the first sealing guide assembly (7) includes bearings (701) and two guide sleeves (702) arranged at intervals from the inside to the outside of the cylinder. The bearings (701) can be directly installed in the cylinder (1) or connected to the cylinder through a bearing fixing sleeve to improve installation stability. The outer edges of the guide sleeves (702) and bearings (701) are connected to the inner wall of the cylinder (1), and seals (703) are installed between the bearings (701) and guide sleeves (702) and between the two guide sleeves. The second sealing guide assembly (8) includes two guide sleeves arranged at intervals and seals installed between the guide sleeves. The guide sleeves of the first sealing guide assembly (7) and the second sealing guide assembly (8) serve to provide a certain limit during the rotation of the screw and the telescoping of the piston rod, preventing the screw or piston from deviating, and the seals can be of sealing ring structure.

It should be noted that in the above description, “first end” refers to the upward direction in Figure 1, and “second end” refers to the downward direction in Figure 1. Other positional terms used in this embodiment to describe Figure 1 follow the same logic.

Advantages: In this embodiment, the preferred power gas is an inert gas. Compared to the electric push rods currently used in the market, inert gas has the advantages of low noise, long lifespan, small size, precise force, and low production cost.

Summary of Beneficial Effects:

  1. The electric drive device serves as a compensating force, eliminating the need for users to apply external force, making it labor-saving and convenient.
  2. An anti-rotation sealing rear plug is installed at one end of the cylinder to secure the drive device, preventing shaking or shifting during operation. Additionally, an anti-rotation structure to limit the rotation of the piston nut is set within the cylinder. The anti-rotation structure and the anti-rotation sealing rear plug form a dual-sided anti-rotation structure, further improving the structural stability of the gas spring and extending its service life.
  3. One end of the screw is guided and fixed by the first guide sealing assembly, and the hollow piston rod is guided and fixed by the second sealing guide assembly, enhancing structural stability and sealing performance.
  4. Using inert gas as the power gas offers the advantages of low noise, long lifespan, small size, precise force, and low production cost.

Terminology Clarification: In the description of this utility model, it should be understood that terms like “center,” “longitudinal,” “transverse,” “length,” “width,” “thickness,” “up,” “down,” “front,” “back,” “left,” “right,” “vertical,” “horizontal,” “top,” “bottom,” “inside,” “outside,” “clockwise,” “counterclockwise,” “axial,” “radial,” “circumferential,” and other positional or directional terms are based on the orientation or positional relationships shown in the figures. They are for the purpose of describing this utility model and simplifying the description, not to indicate or imply that the referred devices or elements must have specific orientations, constructions, or operations. Therefore, they should not be understood as limiting this utility model.

Broad Interpretation of Terms: In this utility model, unless otherwise specified and defined, terms like “installation,” “connection,” “fixing,” etc., should be understood broadly. For example, they can refer to fixed connections, detachable connections, or integral connections; they can be mechanical connections or electrical connections; they can be direct connections or indirect connections through intermediaries, or they can be connections or interactions between the interiors of two elements. Those skilled in the art can understand the specific meanings of these terms in this utility model based on specific circumstances.

In this utility model, unless otherwise specified and defined, the first feature being “above” or “below” the second feature can mean the first and second features are in direct contact, or they can be in indirect contact through intermediaries. Furthermore, the first feature being “above,” “above,” or “on top” of the second feature can mean the first feature is directly above or diagonally above the second feature, or it simply indicates the first feature is at a higher horizontal level than the second feature. The first feature being “below,” “below,” or “underneath” the second feature can mean the first feature is directly below or diagonally below the second feature, or it simply indicates the first feature is at a lower horizontal level than the second feature.

Comprehensive Description: In the description of this utility model, the terms “one embodiment,” “some embodiments,” “example,” “specific example,” or “some examples,” etc., mean specific features, structures, materials, or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of this utility model. Furthermore, the described specific features, structures, materials, or characteristics can be combined in suitable ways in any one or more embodiments or examples. Additionally, it is clear to those skilled in the art that different embodiments or examples described in this utility model and their features can be combined and combined without conflicting with each other.

Disclaimer: While the utility model has been shown and described through the embodiments, it is understood that the embodiments are exemplary and not restrictive of this utility model. Those skilled in the art can make changes, modifications, substitutions, and variations to the embodiments within the scope of the utility model.

Claims: Dual-Sided Anti-Rotation Linear Telescopic Electric Compressed Gas Spring,  invented by LeiYan Gas Spring, a pioneer Chinese Gas Spring Manufacture

  1. A dual-sided anti-rotation linear telescopic electric compressed gas spring, characterized by: Including a cylinder storing power gas, with one side of the cylinder provided with a drive device installation section. A drive device is installed within the drive device installation section, and the outer end of the drive device installation section is equipped with an anti-rotation sealing rear plug to secure the drive device. The part of the cylinder near the drive device installation section is sequentially provided with drive device fasteners and a first sealing guide assembly from the outside in. Inside the cylinder, a screw connected to the drive device and a piston nut threaded to the screw are installed. One end of the screw is placed inside the first sealing guide assembly and matches the first sealing guide assembly. The outer edge of the piston nut slides along the inner wall of the cylinder, and an anti-rotation structure to limit the rotation of the piston nut is set within the inner wall of the cylinder. The other side of the cylinder is equipped with a piston rod fixedly connected to the piston nut, and the end of the other side of the cylinder is equipped with a second sealing guide assembly matching the piston rod.
  2. The dual-sided anti-rotation linear telescopic electric compressed gas spring according to claim 1, characterized by: The anti-rotation structure comprises multiple anti-rotation grooves or protrusions axially extending along the inner wall of the cylinder, and the outer edge of the piston nut is provided with multiple anti-rotation protrusions or grooves that match the inner wall of the cylinder.
  3. The dual-sided anti-rotation linear telescopic electric compressed gas spring according to claim 1, characterized by: The anti-rotation structure comprises an anti-rotation sleeve installed on the inner wall of the cylinder. The inner wall of the anti-rotation sleeve is provided with multiple anti-rotation grooves or protrusions axially extending along the sleeve, and the outer edge of the piston nut is provided with multiple anti-rotation protrusions or grooves that match the anti-rotation sleeve.
  4. The dual-sided anti-rotation linear telescopic electric compressed gas spring according to claim 1, characterized by: The middle part of the anti-rotation sealing rear plug is provided with an anti-rotation connection hole that matches an external anti-rotation connection member. A drive device outlet hole is provided below the anti-rotation connection hole. The outer edge of the anti-rotation sealing rear plug is provided with an anti-rotation shoulder that matches the positioning anti-rotation notch at the end of the cylinder, and the outer edge of the anti-rotation sealing rear plug is further provided with a limit groove and a waterproof sealing groove that match the inner wall of the cylinder.
  5. The dual-sided anti-rotation linear telescopic electric compressed gas spring according to claim 1, characterized by: The first sealing guide assembly comprises bearings and multiple guide sleeves arranged at intervals from the inside to the outside of the cylinder, and the outer edges of the guide sleeves and bearings are connected to the inner wall of the cylinder. Seals are installed between the bearings and guide sleeves and between the two guide sleeves.
  6. The dual-sided anti-rotation linear telescopic electric compressed gas spring according to claim 1, characterized by: The second sealing guide assembly comprises at least two guide sleeves arranged at intervals and seals installed between the guide sleeves.
  7. The dual-sided anti-rotation linear telescopic electric compressed gas spring according to claim 1, characterized by: The drive device comprises a motor connected to the anti-rotation sealing rear plug and a reducer connected to the motor and the screw.
  8. The dual-sided anti-rotation linear telescopic electric compressed gas spring according to claim 7, characterized by: The drive device fastener is a reducer anti-rotation combined fixing member installed between the reducer and the first sealing guide assembly, and the reducer anti-rotation combined fixing member is connected to the inner wall of the reducer and the cylinder.
  9. The dual-sided anti-rotation linear telescopic electric compressed gas spring according to claim 1, characterized by: The screw is a multi-head screw, and the piston nut is a multi-head nut that matches the multi-head screw.
  10. The dual-sided anti-rotation linear telescopic electric compressed gas spring according to claim 1, characterized by: The power gas is an inert gas.

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Posted by: | on January 8, 2025

Compressed Gas Spring with Floating Vibration Damping

Patent No.:CN205896005U Date:2016-08-23

Google Patent: https://patents.google.com/patent/CN205896005U/en?oq=CN205896005U

China Patent: http://epub.cnipa.gov.cn/

Abstract:

The utility model relates to a compressed gas spring with floating vibration damping, which includes a cylinder body, a guide seal crimped at the right end port of the cylinder body, a piston rod installed inside the cylinder body, a piston assembly mounted at the left end of the piston rod, and a floating piston installed within the cylinder body. The utility model achieves vibration or shock absorption through a buffer chamber, improves processability via a concave surface, and employs a lapped piston, pressure plate, and valve plate. It has good processability and is easy to manufacture.

Description

Title: Compressed Gas Spring with Floating Vibration Damping

Technical Field: The utility model relates to a compressed gas spring with floating vibration damping.

Background Technology: Currently, compressed gas springs have a single structure and lack cushioning and damping effects, resulting in a short service life that affects the lifespan and precision of related equipment. Additionally, the piston structure is complex and costly to process.

Content of the Utility Model: The technical problem to be solved by this utility model is to provide a compressed gas spring with floating vibration damping that is reasonably designed, compact in structure, and easy to use. To solve the above problems, the technical solution adopted by this utility model includes: A compressed gas spring with floating vibration damping, including a cylinder body, a guide seal crimped at the right end port of the cylinder body, a piston rod installed inside the cylinder body, a piston assembly mounted at the left end of the piston rod, and a floating piston installed within the cylinder body; In the cylinder body: the floating piston is located on the left side of the piston assembly, forming a rod chamber between the piston assembly and the guide seal, a non-rod chamber between the piston assembly and the floating piston, and a buffer chamber between the floating piston and the left end of the cylinder body.

Further Improvements to the Technical Solution:

  • A second seal ring that makes sealing contact with the inner wall of the cylinder body is set on the outer side wall of the floating piston.
  • A concave surface is set on the side end face of the floating piston.
  • The piston assembly includes a lapped piston mounted on the piston rod, two pressure plates, and two valve plates;
  • The two valve plates are installed between the two pressure plates, and the lapped piston is installed between the two valve plates.
  • A first seal ring that makes sealing contact with the inner wall of the cylinder body is set on the outer side wall of the lapped piston.
  • At least one vent hole, connecting the rod chamber and the non-rod chamber, is set on the lapped piston.
  • End face notches are set on both side end faces of the lapped piston, with the bottom of the notches connecting to the corresponding vent hole.
  • A right connector is connected to the right end of the piston rod; the cylinder body is filled with inert gas or nitrogen.
  • A left connector is connected to the left end of the cylinder body.

Beneficial Effects: This utility model can meet the requirements of gas springs with damping functions on both sides, especially achieving damping suspension at the end of compression. Therefore, a floating piston is used to isolate part of the original gas chamber into an independent gas chamber filled with inert gas. The amount of gas is calculated according to the user’s required suspension effect, achieving the desired suspension damping effect by adding an airbag at the compression end of the gas spring. First, inject a fixed amount of inert gas for suspension damping from the left connector end of the gas spring, then perform conventional compression inflation from the gap between the piston rod and the guide seal and the cylinder body, and test the calculated force value of the gas spring as usual. This utility model achieves vibration or shock absorption through the buffer chamber, improves processability via the concave surface, and employs a lapped piston, pressure plate, and valve plate. It has good processability and is easy to manufacture.

Description of Drawings:

  • Figure 1 is a structural schematic diagram of the utility model.
  • Figure 2 is a structural schematic diagram of the lapped piston of the utility model.

Where:

  1. Piston Rod
  2. Cylinder Body
  3. Guide Seal
  4. Rod Chamber
  5. Piston Assembly
  6. Pressure Plate
  7. Valve Plate
  8. First Seal Ring
  9. Lapped Piston
  10. Non-Rod Chamber
  11. Buffer Chamber
  12. Left Connector
  13. Floating Piston
  14. Concave Surface
  15. Second Seal Ring
  16. End Face Notch
  17. Vent Hole

Specific Implementation Method: As shown in Figures 1-2, this embodiment of the compressed gas spring with floating vibration damping includes a cylinder body (2), a guide seal (3) crimped at the right end port of the cylinder body (2), a piston rod (1) installed inside the cylinder body (2), a piston assembly (5) mounted at the left end of the piston rod (1), and a floating piston (13) installed within the cylinder body (2); In the cylinder body (2): the floating piston (13) is located on the left side of the piston assembly (5), forming a rod chamber (4) between the piston assembly (5) and the guide seal (3), a non-rod chamber (10) between the piston assembly (5) and the floating piston (13), and a buffer chamber (11) between the floating piston (13) and the left end of the cylinder body (2).

  • A second seal ring (15) that makes sealing contact with the inner wall of the cylinder body (2) is set on the outer side wall of the floating piston (13).
  • A concave surface (14) is set on the side end face of the floating piston (13).
  • The piston assembly (5) includes a lapped piston (9) mounted on the piston rod (1), two pressure plates (6), and two valve plates (7);
  • The two valve plates (7) are installed between the two pressure plates (6), and the lapped piston (9) is installed between the two valve plates (7).
  • A first seal ring (8) that makes sealing contact with the inner wall of the cylinder body (2) is set on the outer side wall of the lapped piston (9).
  • At least one vent hole (17), connecting the rod chamber (4) and the non-rod chamber (10), is set on the lapped piston (9).
  • End face notches (16) are set on both side end faces of the lapped piston (9), with the bottom of the notches (16) connecting to the corresponding vent hole (17).
  • A right connector is connected to the right end of the piston rod (1); the cylinder body (2) is filled with inert gas or nitrogen.

This utility model can meet the requirements of gas springs with damping functions on both sides, especially achieving a damping suspension effect at the end of compression. Therefore, a floating piston (13) is used to isolate part of the original gas chamber into an independent gas chamber filled with inert gas. The amount of gas is calculated according to the user’s required suspension effect, achieving the desired suspension damping effect by adding an airbag at the compression end of the gas spring. First, a fixed amount of inert gas for suspension damping is injected from the left connector (12) end of the gas spring, then conventional compression inflation is performed from the gap between the piston rod (1) and the guide seal (3) and the cylinder body (2), and the calculated force value of the gas spring is tested as usual. This utility model achieves vibration or shock absorption through the buffer chamber (11), improves processability via the concave surface (14), and employs a lapped piston (9), pressure plate (6), and valve plate (7). It has good processability and is easy to manufacture.

Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of this utility model, not to limit them; although the utility model has been described in detail with reference to the above embodiments, those skilled in the art should understand that they can still make modifications to the technical solutions described in the above embodiments, or make some technical features equivalent replacements; it is obvious for those skilled in the art to combine multiple technical solutions of this utility model. These modifications or replacements do not make the essence of the corresponding technical solutions depart from the spirit and scope of the utility model embodiments.

Claims (9) – Compressed Gas Spring with Floating Vibration Damping, invented by LeiYan Gas Spring, a pioneer Chinese Gas Spring Manufacture

A compressed gas spring with floating vibration damping, characterized by: Including a cylinder body (2), a guide seal (3) crimped at the right end port of the cylinder body (2), a piston rod (1) installed inside the cylinder body (2), a piston assembly (5) mounted at the left end of the piston rod (1), and a floating piston (13) installed within the cylinder body (2); Within the cylinder body (2): the floating piston (13) is located on the left side of the piston assembly (5), forming a rod chamber (4) between the piston assembly (5) and the guide seal (3), a non-rod chamber (10) between the piston assembly (5) and the floating piston (13), and a buffer chamber (11) between the floating piston (13) and the left end of the cylinder body (2).

The compressed gas spring with floating vibration damping according to claim 1, characterized by: A second seal ring (15) that makes sealing contact with the inner wall of the cylinder body (2) is set on the outer side wall of the floating piston (13).

The compressed gas spring with floating vibration damping according to claim 1, characterized by: A concave surface (14) is set on the side end face of the floating piston (13).

The compressed gas spring with floating vibration damping according to any one of claims 1-3, characterized by: The piston assembly (5) includes a lapped piston (9) mounted on the piston rod (1), two pressure plates (6), and two valve plates (7); The two valve plates (7) are installed between the two pressure plates (6), and the lapped piston (9) is installed between the two valve plates (7).

The compressed gas spring with floating vibration damping according to claim 4, characterized by: A first seal ring (8) that makes sealing contact with the inner wall of the cylinder body (2) is set on the outer side wall of the lapped piston (9).

The compressed gas spring with floating vibration damping according to claim 5, characterized by: At least one vent hole (17) connecting the rod chamber (4) and the non-rod chamber (10) is set on the lapped piston (9).

The compressed gas spring with floating vibration damping according to claim 6, characterized by: End face notches (16) are set on both side end faces of the lapped piston (9), with the bottom of the notches (16) connecting to the corresponding vent hole (17).

The compressed gas spring with floating vibration damping according to claim 7, characterized by: A right connector is connected to the right end of the piston rod (1); the cylinder body (2) is filled with inert gas or nitrogen.

The compressed gas spring with floating vibration damping according to claim 8, characterized by:

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Posted by: | on January 7, 2025

Automated Assembly and Inflation equipment for Simultaneous Closing and Double-Sealed Gas Springs

Patent No.:CN205978236U Date:2016-08-11

Google Patent: https://patents.google.com/patent/CN205978236U/en?oq=CN205978236U

China Patent: http://epub.cnipa.gov.cn/

Abstract

This utility model relates to equipment for automated assembly, inflation, simultaneous closing, and double-sealed structure of gas springs. It includes a base, a clamping equipment set in the middle of the base, and an inflation closing equipment set on the left side of the base. The clamping equipment includes a vertically mounted lower pressure cylinder or hydraulic cylinder on the middle of the base, a lower connecting seat mounted on the lower pressure cylinder or hydraulic cylinder piston rod, an upper half-round replaceable frame set on the lower connecting seat, and a lower half-round replaceable frame installed on the base. This utility model has advanced structure, high automation degree, high work efficiency, sturdy and durable structure, convenient use, good quality of assembled products, low cost, and reasonable process.

Description

Automated Assembly and Inflation equipment for Simultaneous Closing and Double-Sealed Gas Springs

Technical Field

This utility model relates to equipment for automated assembly, inflation, simultaneous closing, and double-sealed structure of gas springs.

Background Technology

Currently, the “CN201120169308.0-Repairable Gas Spring” cannot achieve direct inflation of the cylinder, leading to inaccurate inflation volumes; subsequent gas or oil leakage phenomena in products; the existing gas springs generally adopt pre-inflation and post-welded plug seals for the sealing guide parts, resulting in a short lifespan of the seals.

Utility Model Content

The technical problem to be solved by this utility model is to provide an automated assembly, inflation, simultaneous closing, and double-sealed structure gas spring equipment with a reasonable design, compact structure, and convenient use.

To solve the above problems, the technical scheme adopted by this utility model is: An automated assembly, inflation, simultaneous closing, and double-sealed structure gas spring equipment includes a base, a clamping equipment set in the middle of the base, and an inflation closing equipment set on the left side of the base. The clamping equipment includes a vertically mounted lower pressure cylinder or hydraulic cylinder on the middle of the base, a lower connecting seat mounted on the lower pressure cylinder or hydraulic cylinder piston rod, and an upper half-round replaceable frame set on the lower connecting seat and a lower half-round replaceable frame installed on the base. The inflation closing equipment includes a left push-in port hydraulic cylinder installed at the left end of the base, a replaceable left push-in port inflation seat mounted on the piston rod of the left push-in port hydraulic cylinder, an inflation pipeline interface set at the replaceable left push-in port inflation seat’s outlet, an inflation sealing shoulder set at the right end of the replaceable left push-in port inflation seat, a left closing mold installed in the inflation sealing shoulder, and an inflation through hole set in the replaceable left push-in port inflation seat.

The replaceable left push-in port inflation seat has a positioning shoulder for placing the rear plug, which is connected to the central hole of the inflation sealing shoulder and the cylinder rodless cavity’s left end during inflation. The rear plug of the assembled gas spring is set in the inflation through hole, and its assembly stroke is less than the distance between the stepped hole’s inner side surface and the mold seal ring. It also includes a control system. The control system includes clamping oil or air circuits, left push-in closing oil circuits, and inflation air circuits.

The clamping oil or air circuits include a clamping pump connected to an oil tank or atmosphere at the inlet, a lower pressure cylinder or hydraulic cylinder, and a clamping three-position four-way solenoid valve. The clamping pump’s outlet is connected to one inlet of the clamping three-position four-way solenoid valve, while the other inlet is connected to the oil tank. One outlet of the clamping three-position four-way solenoid valve is connected to the rodless cavity of the lower pressure cylinder or hydraulic cylinder, and the other outlet is connected to the rod cavity of the lower pressure cylinder or hydraulic cylinder.

The left push-in closing oil circuits include a left push-in port hydraulic cylinder, a closing oil pump connected to the oil tank at the inlet, and a closing push two-position four-way solenoid valve. The closing oil pump is connected to one inlet of the closing push two-position four-way solenoid valve, while the other inlet is connected to the oil tank. One outlet of the closing push two-position four-way solenoid valve is connected to the rodless cavity of the left push-in port hydraulic cylinder, and the other outlet is connected to the rod cavity of the left push-in port hydraulic cylinder.

The inflation air circuits include a high-pressure inflation air pump, two-position three-way solenoid valve, inflation through hole, rodless cavity of the assembled gas spring, and an electronic pressure gauge. The high-pressure inflation air pump, two-position three-way solenoid valve, inflation through hole, and rodless cavity of the assembled gas spring are sequentially connected, and the electronic pressure gauge is set on the inflation through hole.

Further Improvements on the Technical Scheme

Additionally, it includes a right pushing and closing equipment set on the right side of the base. The right pushing and closing equipment includes a right pushing and closing hydraulic cylinder and a guide seat set at the left end of the piston rod of the right pushing and closing hydraulic cylinder. A right closing mold is set in the stopping mouth at the left end of the guide seat, corresponding to the right end closing of the cylinder.

The control system also includes a right pushing and closing oil circuit, which has the same structure as the left pushing and closing oil circuit. Additionally, the control system includes time relays or logic controllers to control the on and off sequence and timing of the clamping three-position four-way solenoid valve, closing push two-position four-way solenoid valve, and two-position three-way solenoid valve’s corresponding coils.

A balance circuit or a bidirectional hydraulic lock is set between the clamping three-position four-way solenoid valve and the rod chamber of the lower pressure cylinder or hydraulic cylinder; a replenishment oil circuit is set between the oil tank and the rodless chamber of the lower pressure cylinder or hydraulic cylinder, including a compensation check valve set between the oil tank or atmosphere and the rodless chamber of the lower pressure cylinder or hydraulic cylinder.

The intermediate function of the clamping three-position four-way solenoid valve is M-type.

Benefits of the Technical Scheme

The beneficial effects produced by adopting the above technical scheme include:

  • The clamping mechine can use either a three-jaw chuck or a four-jaw chuck, which can be manually, mechanically, or pneumatically driven. The preferred structure is shown in the diagram.
  • The clamping structure with the replaceable lower and upper half-round frames is reasonable, sturdy, durable, accurately positioned, highly efficient, firmly clamped, and highly extendable.
  • The inflation closing mechine can adopt hot riveting or cold riveting, with press riveting being preferred.
  • According to different customer requirements for the closing size and shape, the connection root is set with an internal chamfer or internal rounded corners.
  • The assembly stroke of the rear plug is less than the distance between the inner side of the stepped hole and the mold seal ring, ensuring the continuity and rationality of the assembly work.
  • The coaxial setting improves assembly precision.
  • To improve equipment assembly efficiency and optimize processes, a right pushing and closing mechine was added.
  • The through-hole can extend the versatility and extendability of the equipment.
  • To improve automation, electric, hydraulic, or pneumatic controls can also be adopted.
  • The electronic pressure gauge achieves pressure monitoring, ensuring the stability of equipment pressure.
  • The balance circuit or bidirectional hydraulic lock ensures the stability of the lower pressure cylinder or hydraulic cylinder. The replenishment oil circuit ensures rapid oil replenishment during quick descent.
  • The intermediate function is M-type, facilitating unloading work and improving pressure retention effects.
  • The replaceable lower and upper half-round frames are set in two groups, with the left and right ends of the lower connecting seat respectively, improving coaxiality and workmanship.

This utility model has an advanced structure, high automation degree, high work efficiency, sturdy and durable structure, convenient use, good quality of assembled products, low cost, and reasonable process.

Illustration Description

Figure 1: Schematic diagram of the gas spring structure with the rear plug to be assembled. Figure 2: Schematic diagram of the local structure on the left side of the gas spring after assembling the rear plug. Figure 3: Schematic diagram of the piston plate structure. Figure 4: Right side view of the piston plate structure. Figure 5: Schematic diagram of the gas spring assembly equipment. Figure 6: Schematic diagram of the inflation air circuit. Figure 7: Schematic diagram of the closing air circuit. Figure 8: Schematic diagram of oil circuit in clamping scheme 1. Figure 9: Schematic diagram of air circuit in clamping scheme 2.

Description of Components

  1. Cylinder
  2. Piston rod
  3. Right connector
  4. Left connector
  5. Rear plug
  6. Seal ring
  7. Piston
  8. Damping hole
  9. Sealing groove
  10. Piston plate
  11. First lip seal
  12. Fit clearance
  13. Ventilation groove
  14. Intermediate seal spacer
  15. Second lip seal guide sleeve
  16. Left closing end
  17. Closing groove
  18. Gas spring to be assembled
  19. Base
  20. Lower pressure cylinder or hydraulic cylinder
  21. Movable lower pressure seat
  22. Upper semi-circular replaceable frame
  23. Lower semi-circular replaceable frame
  24. Left push-in hydraulic cylinder
  25. Replaceable left push-in inflation seat
  26. Inflation through hole
  27. Left closing mold
  28. Inflation sealing shoulder
  29. Right pushing hydraulic cylinder
  30. Right closing mold
  31. High-pressure inflation air pump
  32. Two-position three-way solenoid valve
  33. Electronic pressure gauge
  34. Closing oil pump
  35. Two-position four-way solenoid valve for closing push
  36. Clamping pump
  37. Three-position four-way solenoid valve for clamping
  38. Balance circuit
  39. Compensation check valve

Specific Implementation Mode

As shown in Figures 1-4, Figure 1 shows the gas spring with simultaneous closing and double-sealed structure of this embodiment, including cylinder 1, rear plug 5 installed in the inner hole at the left end of cylinder 1, and at least one set of seal rings 6 installed between the outer wall of rear plug 5 and the inner wall of cylinder 1.

At least one annular groove for placing seal rings 6 is set on the outer wall of rear plug 5. Closing groove 17 is set on rear plug 5, while left closing end 16 is set at the left end of cylinder 1, hooking into closing groove 17.

Piston rod 2 is installed inside cylinder 1. A guiding and sealing assembly is set on piston rod 2 at the right end of cylinder 1, including a first lip seal 11, an intermediate seal spacer 14, and a second lip seal guide sleeve 15. A buffer pressure-free sealing area is formed between the first lip seal 11 and the intermediate seal spacer 14, as well as between the intermediate seal spacer 14 and the second lip seal guide sleeve 15.

Right closing is set at the right end of cylinder 1. Right closing annular groove is set on the second lip seal guide sleeve 15, hooking into the right closing annular groove. Intermediate seal spacer 14 is firmly riveted between the outer wall of intermediate seal spacer 14 and the inner wall of cylinder 1.

Piston rod 2 is installed inside cylinder 1, with piston 7 and piston plate 10 set on piston rod 2. Piston 7 divides the inner cavity of cylinder 1 into a rod cavity and a rodless cavity, with the rod cavity on the right side of the rodless cavity. Piston 7 and piston plate 10 are tightly riveted on piston rod 2. A fit clearance 12 is set between the inner wall of cylinder 1 and the outer wall of piston 7. A sealing groove 9 is set between the right side of piston 7 and the left side of piston plate 10. Damping hole 8 and O-ring seal are set on piston 7, with ventilation groove 13 set on piston plate 10.

Ventilation groove 13 is set in a radial groove shape, dividing piston plate 10 into three or more odd or even blade structures. Ventilation groove 13 is set in a radial arc or curved long groove.

Left connector 4 is installed at the left end of rear plug 5, while right connector 3 is installed at the right end of piston rod 2.

The annular groove for placing seal rings 6 preferably includes two grooves, with one seal ring 6 installed in each groove. The structure is reasonable and provides a good sealing effect. The right closing hooks into the right closing annular groove. The closing groove 17 hooks with the left closing end 16, facilitating assembly without welding deformation, providing high precision, reasonable structure, and long service life.

The guiding and sealing assembly includes the first sealing cover 11, intermediate sealing cover 14, and second sealing cover 15 set sequentially from left to right inside cylinder 1. The structure is reasonable and provides a long service life. Intermediate sealing cover 14 is firmly fixed by riveting between the outer wall of intermediate sealing cover 14 and the inner wall of cylinder 1.

Detailed Implementation Mode

The piston structure of this utility model is reasonable and operates stably. The central hole (13) divides the piston plate (10) into spiral blade structures, improving its rigidity and ensuring smoother ventilation.

This utility model adopts post-inflation closing and pressing riveting. The rear plug (5) is enhanced with two O-rings. When the rear plug (5) and the cylinder (1) are separated, high-pressure sealing inflation is performed on the empty cylinder (1) cavity, ensuring consistent inflation volume and meeting the precise force requirements of the gas spring. At the moment of inflation completion, the closing molds of the high-pressure inflation equipment, namely the left closing mold (112) and the right closing mold (115), push the rear plug (5) into the cylinder (1) while closing, ensuring the precision consistency of the gas spring’s inflation force value, improving the sealing performance and service life of the guiding sealing assembly.

The piston plate (10) is a new type of five-point daisy piston plate. The five points of the daisy piston improve the concentricity of the piston rod (2), guiding sealing assembly, cylinder (1), piston body (7), and piston plate (10), making the gas spring run more stably. The guiding sealing assembly adopts secondary pressureless sealing, which means there is no initial air pressure between the two sealing components. The first sealing component blocks air pressure, while the second sealing component, due to the absence of pressure, exerts negligible friction on the piston rod. As the gas spring extends and retracts, a reasonable accumulation of oil on the piston rod surface gradually applies pressure to the second sealing component’s lip, thereby improving the sealing performance and service life of the guiding sealing assembly.

This utility model can be widely applied to any category of gas springs.

Figures 5-9: Explanation

The equipment for the assembly, inflation, simultaneous closing, and double-sealed gas spring structure includes a base (102), a clamping equipment set in the middle of the base (102), and an inflation closing equipment set on the left side of the base (102). The clamping equipment includes a vertically mounted lower pressure cylinder or hydraulic cylinder (103), a movable lower pressure seat (104) installed at the lower end of the piston rod of the lower pressure cylinder or hydraulic cylinder (103), an upper half-round replaceable frame (105) set at the lower end of the movable lower pressure seat (104), and a lower half-round replaceable frame (106) installed on the base (102). The lower half-round replaceable frame (106) and the upper half-round replaceable frame (105) clamp the horizontally set gas spring (101) to be assembled.

The inflation closing equipment includes a left push-in hydraulic cylinder (107) installed at the left end of the base (102), a replaceable left push-in inflation seat (108) installed on the piston rod of the left push-in hydraulic cylinder (107), an inflation pipeline interface set on the replaceable left push-in inflation seat (108), an inflation sealing shoulder (113) set at the right end of the replaceable left push-in inflation seat (108), a left closing mold (112) installed in the inflation sealing shoulder (113), and an inflation through hole (110) set in the replaceable left push-in inflation seat (108). The inflation through hole (110) is located at the left end of the left closing mold (112), and the left closing mold (112) has a central hole. The left closing mold (112) has a stepped hole with a connection root for closing the left end of the cylinder (1) to be assembled.

The replaceable left push-in inflation seat (108) has a positioning shoulder for placing the rear plug (5). During inflation, the inflation pipeline interface, inflation through hole (110), central hole of the left closing mold (112), and the rodless cavity at the left end of the cylinder (1) are connected for inflation. The rear plug (5) of the gas spring (101) to be assembled is set in the inflation through hole (110). The assembly stroke of the rear plug (5) is less than the distance between the inner side surface of the stepped hole and the mold seal ring. The rear plug (5), cylinder (1), left closing mold (112), lower half-round replaceable frame (106), and upper half-round replaceable frame (105) are coaxially set.

Additionally, the equipment includes a right pushing and closing equipment set on the right side of the base (102). The right pushing and closing equipment includes a right pushing and closing hydraulic cylinder (114) and a guide seat set at the left end of the piston rod of the right pushing and closing hydraulic cylinder (114). A right closing mold (115) is set in the stopping mouth at the left end of the guide seat, corresponding to the right end closing of the cylinder (1). The right pushing and closing hydraulic cylinder (114) and piston rod have through holes for the piston rod (2) of the gas spring (101) to pass through. The right closing mold (115) has a through hole for the piston rod (2) to pass through, and a stepped hole at its left side, with a connection root for closing the right end of the cylinder (1). The connection root is set with internal chamfer or internal rounded corners. The right closing mold (115), rear plug (5), cylinder (1), left closing mold (112), lower half-round replaceable frame (106), and upper half-round replaceable frame (105) are coaxially set. The upper half-round replaceable frame (105) is set in two groups on the left and right ends of the movable lower pressure seat (104). The lower half-round replaceable frame (106) is set in two groups, identical in structure to the upper half-round replaceable frame (105), and correspondingly set.

Control System

The control system includes clamping oil or air circuits, right pushing and closing oil circuit, left pushing and closing oil circuit, and inflation air circuit. The clamping oil or air circuit includes a clamping pump (121) connected to the oil tank or atmosphere at the inlet, a lower pressure cylinder or hydraulic cylinder (103), and a three-position four-way solenoid valve (122) for clamping. The outlet of the clamping pump (121) is connected to one inlet of the three-position four-way solenoid valve (122), while the other inlet is connected to the oil tank or atmosphere. One outlet of the three-position four-way solenoid valve (122) is connected to the rodless cavity of the lower pressure cylinder or hydraulic cylinder (103), and the other outlet is connected to the rod cavity of the lower pressure cylinder or hydraulic cylinder (103).

The left pushing and closing oil circuit includes a left push-in hydraulic cylinder (107), a closing oil pump (119) connected to the oil tank at the inlet, and a two-position four-way solenoid valve (120) for closing push. The closing oil pump (119) is connected to one inlet of the two-position four-way solenoid valve (120), while the other inlet is connected to the oil tank. One outlet of the two-position four-way solenoid valve (120) is connected to the rod cavity of the left push-in hydraulic cylinder (107). The right pushing and closing oil circuit is identical in structure to the left pushing and closing oil circuit.

The inflation air circuit includes a high-pressure inflation air pump (116), two-position three-way solenoid valve (117), inflation through hole (110), rodless cavity of the gas spring (101) to be assembled, and an electronic pressure gauge (118). The high-pressure inflation air pump (116), two-position three-way solenoid valve (117), inflation through hole (110), and rodless cavity of the gas spring (101) to be assembled are sequentially connected. The electronic pressure gauge (118) is set on the inflation through hole (110).

The control system also includes time relays or logic controllers to control the on/off timing and sequence of the coils of the three-position four-way solenoid valve (122) for clamping, the two-position four-way solenoid valve (120) for closing push, and the two-position three-way solenoid valve (117). A balance circuit (123) or bidirectional hydraulic lock is set between the three-position four-way solenoid valve (122) for clamping and the rod cavity of the lower pressure cylinder or hydraulic cylinder (103). A replenishment oil circuit is set between the oil tank and the rodless cavity of the lower pressure cylinder or hydraulic cylinder (103), including a compensation check valve (124) set between the oil tank and the rodless cavity of the lower pressure cylinder or hydraulic cylinder (103).

The intermediate function of the three-position four-way solenoid valve (122) for clamping is M-type. The upper half-round replaceable frame (105) is set in two groups on the left and right ends of the movable lower pressure seat (104), and the lower half-round replaceable frame (106) is set in two groups, identical in structure to the upper half-round replaceable frame (105), and correspondingly set.

The clamping equipment can adopt three-jaw chuck or four-jaw chuck clamping, which can be manually, mechanically, or pneumatically driven. The preferred structure is shown in Figure 5. The clamping structure with the lower half-round replaceable frame (106) and the upper half-round replaceable frame (105) is reasonable, sturdy, durable, accurately positioned, highly efficient, firmly clamped, and highly extendable.

Specific Implementation Method

The inflation closing equipment can adopt hot riveting or cold riveting, with press riveting being preferred. According to different customer requirements for the closing size and shape, the connection root can be set with an internal chamfer or internal rounded corners. The assembly stroke of the rear plug (5) is less than the distance between the inner side surface of the stepped hole and the mold seal ring, ensuring the continuity and rationality of the assembly work. Coaxial setting improves assembly precision.

To improve assembly efficiency and optimize processes, a right pushing and closing equipment has been added. The through-hole can extend the versatility and expandability of the equipment. To enhance the degree of automation, electric, hydraulic, or pneumatic controls can also be adopted. The electronic pressure gauge (118) realizes pressure monitoring, ensuring the stability and monitoring capability of the equipment pressure.

Common balance circuits (123) or bidirectional hydraulic locks ensure the stability of the lower pressure cylinder or hydraulic cylinder (103). The replenishment oil circuit ensures rapid oil replenishment during quick descent. The intermediate function is M-type, facilitating unloading work and improving pressure retention effects. The lower half-round replaceable frame (106) and the upper half-round replaceable frame (105) are set in two groups on the left and right ends of the movable lower pressure seat (104), improving their coaxiality and workmanship.

When assembling the above products using this equipment, the rear plug (5) is pre-placed in the inflation through hole (110). The left closing mold (112) and right closing mold (115) are respectively placed in the inflation sealing shoulder (113) and the guide seat. This utility model can achieve interchangeable connections through various means, such as threaded connections, socket pin assembly, tapered fit, or slot ring assembly.

The intermediate relay, time controller, or PCL logic controller sets the on/off timing and sequence of each valve group. The gas spring (101) to be assembled is placed on the lower half-round replaceable frame (106). The clamping pump (121) is activated, and the three-position four-way solenoid valve (122) for clamping is powered on. The lower pressure cylinder or hydraulic cylinder (103) drives the upper half-round replaceable frame (105) downward through the movable lower pressure seat (104) to clamp the gas spring (101) to be assembled. Once clamped, at the specified time A, the three-position four-way solenoid valve (122) for clamping is powered off to retain pressure, and the compensation check valve (124) quickly replenishes oil.

The two-position four-way solenoid valve (120) for closing push is powered on for the first time, starting the left push-in hydraulic cylinder (107) with the closing oil pump (119). The left push-in hydraulic cylinder (107) drives the replaceable left push-in inflation seat (108) to move rightward. The cylinder (1) enters the stepped hole of the left closing mold (112) and achieves axial sealing through the seal ring. At the specified time B, the two-position four-way solenoid valve (120) for closing push is powered off, stopping the movement. The two-position three-way solenoid valve (117) and high-pressure inflation air pump (116) are activated. The high-pressure inflation air pump (116) inflates the rodless cavity of the cylinder (1) through the two-position three-way solenoid valve (117) and the inflation through hole (110), achieving precise inflation.

At the specified time C, the two-position three-way solenoid valve (117) and high-pressure inflation air pump (116) are powered off. The two-position four-way solenoid valve (120) for closing push of the left push-in hydraulic cylinder (107) is powered on for the second time, starting the closing oil pump (119) of the left push-in hydraulic cylinder (107). The left push-in hydraulic cylinder (107) continues to drive the rear plug (5) rightward and pushes it to the left end of the cylinder (1). Then, the replaceable left push-in inflation seat (108) continues to move rightward while the right pushing and closing hydraulic cylinder (114) moves leftward. Under the action of the left push-in hydraulic cylinder (107) and the right pushing and closing hydraulic cylinder (114), the left closing mold (112) and the right closing mold (115) close the cylinder (1).

At the specified time D, the two-position three-way solenoid valve (117) is powered on and changes direction, releasing air from the inflation through hole (110). The two-position four-way solenoid valve (120) for closing push is powered on and changes direction, releasing the cylinder (1). The three-position four-way solenoid valve (122) for clamping is powered on and changes direction, allowing the cylinder (1) to be removed. The left closing mold (112) and right closing mold (115) are sleeved on the closed end of the cylinder (1), achieving simultaneous removal. As a structural variation, one oil pump can be used to simultaneously control the linkage of the valve groups through combination. Compared to this integrated linkage control scheme, the control system of this embodiment, where each oil pump controls its valve group, avoids mutual interference, facilitates maintenance and troubleshooting, and reduces pump oil load.

This utility model has an advanced structure, high automation degree, high work efficiency, sturdy and durable structure, convenient use, good quality of assembled products, low cost, and reasonable process.

Lastly, it should be noted that the above embodiments are only for illustrating the technical scheme of this utility model, not for limiting it. Although this utility model has been described in detail with reference to the above embodiments, those skilled in the art should understand that they can still modify the technical scheme described in the above embodiments, or replace some of the technical features equivalently. It is obvious for those skilled in the art to combine multiple technical schemes of this utility model. Such modifications or replacements do not depart from the spirit and scope of the technical scheme of this utility model.

Claims

Automated Assembly and Inflation equipment for Simultaneous Closing and Double-Sealed Gas Springs, invented by LeiYan Gas Spring, a pioneer Chinese Gas Spring Manufacture

  1. Automated Assembly and Inflation equipment for Simultaneous Closing and Double-Sealed Gas Springs:
    • Components: Includes a base (102), a clamping equipment set in the middle of the base (102), and an inflation closing equipment set on the left side of the base (102).
    • Clamping equipment : Vertically mounted lower pressure cylinder or hydraulic cylinder (103) on the middle of the base (102), upper half-round replaceable frame (105) on the piston rod of the lower pressure cylinder or hydraulic cylinder (103), and lower half-round replaceable frame (106) on the base (102).
    • Inflation Closing equipment : Left push-in hydraulic cylinder (107) on the left end of the base (102), replaceable left push-in inflation seat (108) on the piston rod of the left push-in hydraulic cylinder (107), inflation pipeline interface on the replaceable left push-in inflation seat (108), inflation sealing shoulder (113) on the right end of the replaceable left push-in inflation seat (108), left closing mold (112) in the inflation sealing shoulder (113), and inflation through hole (110) in the replaceable left push-in inflation seat (108).
    • Positioning Stop Mouth: In the replaceable left push-in inflation seat (108) for placing the rear plug (5). During inflation, the inflation pipeline interface, inflation through hole (110), central hole of the left closing mold (112), and the rodless cavity at the left end of the cylinder (1) are connected for inflation. The rear plug (5) is set in the inflation through hole (110), with the assembly stroke of the rear plug (5) being less than the distance between the inner side surface of the stepped hole and the mold seal ring.
    • Control System: Includes clamping oil or air circuits, left pushing and closing oil circuit, and inflation air circuit. The clamping oil or air circuit includes a clamping pump (121) connected to the oil tank or atmosphere at the inlet, a lower pressure cylinder or hydraulic cylinder (103), and a three-position four-way solenoid valve (122) for clamping. The clamping pump (121) is connected to one inlet of the three-position four-way solenoid valve (122), with the other inlet connected to the oil tank. The clamping pump’s outlet is connected to the rodless cavity of the lower pressure cylinder or hydraulic cylinder (103), and the other outlet is connected to the rod cavity of the lower pressure cylinder or hydraulic cylinder (103). The left pushing and closing oil circuit includes a left push-in hydraulic cylinder (107), a closing oil pump (119) connected to the oil tank at the inlet, and a two-position four-way solenoid valve (120) for closing push. The closing oil pump (119) is connected to one inlet of the two-position four-way solenoid valve (120), with the other inlet connected to the oil tank. The closing push solenoid valve (120) is connected to the rodless cavity and the rod cavity of the left push-in hydraulic cylinder (107). The inflation air circuit includes a high-pressure inflation air pump (116), a two-position three-way solenoid valve (117), inflation through hole (110), rodless cavity of the gas spring (101) to be assembled, and an electronic pressure gauge (118). The high-pressure inflation air pump (116), two-position three-way solenoid valve (117), inflation through hole (110), and rodless cavity of the gas spring (101) to be assembled are sequentially connected. The electronic pressure gauge (118) is set on the inflation through hole (110).
  2. Right Pushing and Closing equipment :
    • Components: Right pushing and closing equipment set on the right side of the base (102), including a right pushing and closing hydraulic cylinder (114) and a guide seat set at the left end of the piston rod of the right pushing and closing hydraulic cylinder (114). A right closing mold (115) is set in the stopping mouth at the left end of the guide seat, corresponding to the right end closing of the cylinder (1).
  3. Control System:
    • Right Pushing and Closing Oil Circuit: The control system includes a right pushing and closing oil circuit, identical in structure to the left pushing and closing oil circuit.
  4. Control System Components:
    • Time Relays or Logic Controllers: Includes time relays or logic controllers for controlling the on/off timing and sequence of the three-position four-way solenoid valve (122) for clamping, two-position four-way solenoid valve (120) for closing push, and two-position three-way solenoid valve (117).
  5. Additional Stability Features:
    • Balance Circuit and Bidirectional Hydraulic Lock: A balance circuit (123) or a bidirectional hydraulic lock is set between the three-position four-way solenoid valve (122) for clamping and the rod cavity of the lower pressure cylinder or hydraulic cylinder (103). A replenishment oil circuit is set between the oil tank and the rodless cavity of the lower pressure cylinder or hydraulic cylinder (103), including a compensation check valve (124).
  6. Intermediate Function of Solenoid Valve:
    • M-type Intermediate Function: The intermediate function of the three-position four-way solenoid valve (122) for clamping is M-type.

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