Tag: compression gas spring
Connectors and Marking of gas spring
4. Types
4.1 Shape and Force – Displacement Curve
The shape and force – displacement curve of the gas spring are shown in Figure 1.
4.2 Types and Codes of Gas Spring Connectors
The types and codes of gas spring connectors are shown in Figure 2. Other connection types shall be agreed upon by the supplier and the demander.
| Code | Connection Type |
| 0 | Single Piece |
| U | Double – Ear |
| L | Single – Ear |
| B | Universal Ball Head |
5. Marking
5.1 Marking Method
The marking of the gas spring consists of the code, piston rod diameter (which may not be marked), cylinder outer diameter (which may not be marked), stroke, extended length, and specified force value, as specified below: [Marking diagram description]
5.2 Marking Examples
- Example 1: For a compression gas spring with a piston rod diameter of 10 mm, a cylinder outer diameter of 22 mm, a stroke of 200 mm, an extended length of 500 mm, and a minimum extension force F₁ (lifting force) of 650 N.
Marking: YQ 10/22 – 200 – 500 F₁650 or YQ 200 – 500 F₁650 - Example 2: For a compression gas spring with a piston rod diameter of 8 mm, a cylinder outer diameter of 18 mm, a stroke of 150 mm, an extended length of 400 mm, and a nominal force F. of 350 N.
Marking: YQ 8/18 – 150 – 400 F.350 or YQ 150 – 400 F.350
Technical Specification for Compression Gas Springs (English version of national strandard, initiated by LeiYan Gas Springs), proposed and prepared by SAC/TC 235 (National Technical Committee 235 on Spring of Standardization Administration of China).
Definition & Symbols of Compression Gas Springs
3. Terms, Definitions, Symbols and Explanations
The terms, definitions, symbols and explanations established in GB/T 1805 and Table 1 apply to this standard.
| Term | Definition or Explanation | Symbol | Unit |
| Gas Spring | An elastic element composed of a sealed cylinder, a piston that can slide in the cylinder, and a piston rod assembly, using nitrogen or other inert gases as the energy – storage medium | ||
| Compression Gas Spring | A gas spring in which the piston rod is in a freely extended state without external force and can withstand pressure | ||
| Piston Rod Diameter | The diameter of the piston rod of the gas spring | d | mm |
| Cylinder Inner Diameter | The inner diameter of the gas spring cylinder | D₁ | mm |
| Cylinder Outer Diameter | The outer diameter of the gas spring cylinder | D₂ | mm |
| Stroke | The axial displacement of the piston rod from the fully extended state to the minimum compressed size | S | mm |
| Extended Length | The effective length of the gas spring in the fully extended state | L | mm |
| Start – up Force | The initial force required to press the piston rod after the gas spring has been in the extended state for a certain period | F₀ | N |
| One Cycle | The piston rod is compressed and extended once each according to the specified stroke | ||
| Specified Force | The force marked on the drawings and products confirmed by both the supplier and the demander (F, Fa, F₃, …) | Fx | N |
| Minimum Extension Force | The force measured at the specified force – measuring point C at the starting point of the working stroke during the extension process | F₁ | N |
| Maximum Extension Force | The force measured at the specified force – measuring point C at the end point of the working stroke during the extension process | F₂ | N |
| Minimum Compression Force | The force measured at the specified force – measuring point C at the starting point of the working stroke during the compression process | F₃ | N |
| Maximum Compression Force | The force measured at the specified force – measuring point C at the end point of the working stroke during the compression process | F₄ | N |
| Nominal Force a | F.=(F₁ + F₃)/2. Nominal force a is one of the indicators of the comprehensive characteristics of the gas spring | F. | N |
| Nominal Force b | F₆=(F₂ + F₄)/2. Nominal force b is generally used for calculating the force ratio | F₆ | N |
| Dynamic Friction Force | F,=(F₃ – F₁)/2 | F, | N |
| Extension Speed | The average speed at which the piston rod freely extends from the end of the specified stroke to the initial position | v | mm/s |
| Gas Damper Part | The area where the piston movement is affected by gas damping during the extension process of the piston rod | mm | |
| Liquid Damper Part | The area where the piston movement is affected by liquid damping during the extension process of the piston rod | mm | |
| Measuring Point | The point for collecting force values during dynamic or static testing. When S≤80 mm, C = 5 mm; when S>80 mm, C = 10 mm | C | mm |
| Force Ratio | α = F₆/F. | α |
Technical Specification for Compression Gas Springs (English version of national strandard, initiated by LeiYan Gas Springs), proposed and prepared by SAC/TC 235 (National Technical Committee 235 on Spring of Standardization Administration of China).
Technical Specification for Compression Gas Springs – national standard
Compression gas spring technical specification
Issued on December 23, 2010 – Implemented on October 1, 2011
Issued by the General Administration of Quality Supervision, Inspection and Quarantine of the People’s Republic of China and the Standardization Administration of China
Foreword
This standard is proposed by China Machinery Industry Federation.
This standard is under the jurisdiction of the National Spring Standardization Technical Committee.
Technical Specification for Compression Gas Springs
1. Scope
This standard specifies the terms and definitions, markings, technical requirements, test methods, inspection rules, as well as requirements for identification, packaging, transportation, and storage of compression gas springs (hereinafter referred to as “gas springs”).
This standard is applicable to gas springs using nitrogen or other inert gases as energy – storage working media.
2. Normative References
The provisions of the following documents are incorporated into this standard by reference. For dated references, subsequent amendments (excluding errata) or revised editions do not apply to this standard. However, parties reaching agreements based on this standard are encouraged to explore the possibility of using the latest editions of these documents. For undated references, their latest editions apply to this standard.
- GB/T 1771 Paints and Varnishes – Determination of Resistance to Neutral Salt Spray (GB/T 1771—2007, ISO 7253:1996, IDT)
- GB/T 1800.1 Geometrical Product Specifications (GPS) – Limits and Fits – Part 1: Basics of Tolerances, Deviations and Fits (GB/T 1800.1—2009, ISO 286 – 1:1988, MOD)
- GB/T 1805 Spring Terminology
- GB/T 2348 Hydraulic and Pneumatic Systems and Components – Cylinder Bore Diameters and Piston Rod Outer Diameters (GB/T 2348—1993, neq ISO 3320:1987)
- GB/T 2349 Hydraulic and Pneumatic Systems and Components – Piston Stroke Series of Cylinders
- GB/T 2828.1 Sampling Procedures for Inspection by Attributes – Part 1: Sampling Plans for Lot – by – Lot Inspection Retrieved by Acceptable Quality Limit (AQL) (GB/T 2828.1—2003, ISO 2859 – 1:1999, IDT)
- GB/T 2829 Sampling Procedures and Tables for Periodic Inspection by Attributes (Applicable to the Inspection of Process Stability)
- GB/T 10125 Corrosion Tests in Artificial Atmospheres – Salt Spray Tests (GB/T 10125—1997, eqv ISO 9227:1990)
- QC/T 484 Automobile Paint Coatings
- QC/T 625 Coatings and Chemical Treatment Layers for Automobiles
Technical Specification for Compression Gas Springs (English version of national strandard, initiated by LeiYan Gas Springs), proposed and prepared by SAC/TC 235 (National Technical Committee 235 on Spring of Standardization Administration of China).
Threaded Groove Damping Gas Spring
Patent No.:CN113007255A Date:2021-04-27
Google Patent: https://patents.google.com/patent/CN113007255A/en?oq=CN113007255A
China Patent: http://epub.cnipa.gov.cn/
A Threaded Groove Damping Device
Abstract
The present invention provides a threaded groove damping gas spring. The gas spirng comprises a piston assembly and a closed cavity. There is a gap between the piston assembly and the closed cavity, and a sealing member is arranged in the closed cavity to seal the gap between the piston assembly and the closed cavity. The piston assembly includes a piston body and a piston sleeve. A damping structure and a first flow-through hole are provided on the piston body. The damping structure is a threaded damping groove, which is arranged circumferentially around the piston body. A second flow-through hole is provided on the piston sleeve, and the second flow-through hole is in communication with both the damping structure and the first flow-through hole. Since this super-long damping structure is arranged circumferentially around the piston body, the damping stroke is effectively extended, enabling the movement of the piston assembly to be smooth, ensuring the smooth spring-back speed of the damping device. The design concept is ingenious. At the same time, the safety and service life are greatly improved, thus solving the problems of traditional gas springs, such as fast movement speed, and inability to effectively ensure their safety and service life.
Description
Technical Field
The present invention relates to the field of gas springs, and specifically to a threaded groove damping device.
Background Art
Gas springs are components that can achieve functions such as support, buffering, braking, height and angle adjustment. In construction machinery, they are mainly applied to parts such as covers and doors. A gas spring mainly consists of a piston rod, a piston, a sealing guide sleeve, a filler, a pressure cylinder, a joint, etc. The pressure cylinder is a closed cavity, filled with inert gas or an oil – gas mixture inside, and the pressure in the cavity is several or dozens of times that of the atmospheric pressure.
Traditional gas springs are filled with gas at a certain pressure in the cylinder. Due to the difference in cross – sectional areas at both ends, a pressure difference is generated, causing the side with higher pressure to move towards the side with lower pressure. However, the movement speed is relatively fast. The extension time within 100 mm is as short as 2 – 3 seconds. Even if the diameter of the piston damping hole is adjusted, the movement speed does not decrease significantly. This poses a greater safety hazard to operators and greatly reduces the consistency, stability, and service life of the product.
Summary of the Invention
In view of this, the present invention provides a threaded groove damping device, which can at least solve one of the above – mentioned problems. Through the threaded damping groove arranged circumferentially around the piston body, the movement of the piston assembly is made smooth, ensuring the smooth spring – back speed of the damping device. The design concept is ingenious, and at the same time, the safety and service life are improved.
To achieve the above – mentioned objectives, the present invention provides the following technical solutions: A threaded groove damping device includes a piston assembly and a closed cavity. There is a gap between the piston assembly and the closed cavity, and the piston assembly reciprocates in the closed cavity. A sealing member is arranged in the closed cavity, and the sealing member is used to seal the gap between the piston assembly and the closed cavity. The piston assembly includes a piston body and a piston sleeve closely sleeved on the piston body. A damping structure and a first flow – through hole are provided on the piston body. The damping structure is a threaded damping groove, which is arranged circumferentially around the piston body. A second flow – through hole is provided on the piston sleeve, and the second flow – through hole is in communication with both the threaded damping groove on the piston body and the first flow – through hole.
In some preferred embodiments, the threaded damping groove is a threaded slot, and the threaded damping groove is provided at both ends of the piston body or at one end of the piston body.
In some preferred embodiments, the second flow – through hole includes a side – surface flow – through hole and an end – surface communication hole, and the end – surface communication hole is adapted to the first flow – through hole.
In some preferred embodiments, one end of the threaded damping groove is connected to the side – surface flow – through hole, and the other end is connected to the end – surface communication hole, and the end – surface communication hole is connected to the first communication hole.
In some preferred embodiments, the threaded damping groove is provided on the side surface of the piston body.
In some preferred embodiments, the top of the groove of the threaded damping groove is in close contact with the inner surface of the piston sleeve.
In some preferred embodiments, a first protrusion and a second protrusion are provided on the piston body, and a groove is formed between the first protrusion and the second protrusion.
In some preferred embodiments, the sealing member moves within the groove. The axial width of the groove is greater than the maximum diameter of the cross – section of the sealing member. The sealing member is located above the first flow – through hole to ensure that the groove is in communication with the first flow – through hole.
In some preferred embodiments, the first flow – through hole includes a first left flow – through hole and a first right flow – through hole.
In some preferred embodiments, the first left flow – through hole is provided on the first protrusion, and the first right flow – through hole is provided on the second protrusion.
Features and advantages of the present invention: When the piston assembly moves under the extrusion of gas or oil pressure in the closed cavity, the sealing member provided in the closed cavity forms a frictional displacement with the inner wall of the closed cavity. The gas or oil pressure makes the sealing member tightly seal the gap between the piston assembly and the closed cavity, causing the gas to pass through the first flow – through hole, the circumferential damping structure and the second flow – through hole. Since the damping structure is arranged circumferentially around the piston body, the damping stroke for the gas or oil pressure is effectively extended, making the movement of the piston assembly smooth, ensuring the smooth spring – back speed of the damping device. The design concept is ingenious. At the same time, the safety and service life are greatly improved, thus solving the problems that the traditional gas spring has a fast movement speed and cannot effectively ensure its safety and service life.
Description of the Drawings
The following drawings are provided to further understand this application and form a part of this application. They are only intended to provide a schematic explanation and description of the present invention, and are not intended to limit the scope of the present invention. In the drawings:
- Fig. 1 is a schematic diagram of the assembly structure of a threaded groove damping device in Embodiment 1 of this application.
- Fig. 2 is a gas – flow diagram of the double – damping – structure piston assembly in the stretching movement in Embodiment 1 of this application.
- Fig. 3 is a gas – flow diagram of the double – damping – structure piston assembly in the compressing movement in Embodiment 1 of this application.
- Fig. 4 is a schematic diagram of the structure of the double – damping – structure piston body in Embodiment 1 of this application.
- Fig. 5 is a right – view of Fig. 4.
- Fig. 6 is a schematic sectional – view of the structure of the piston sleeve in Embodiment 1 of this application.
- Fig. 7 is a right – view of Fig. 6.
- Fig. 8 is a schematic diagram of the structure of the single – damping – structure piston body in Embodiment 2 of this application.
- Fig. 9 is a gas – flow diagram of the single – damping – structure piston assembly in the stretching movement in Embodiment 2 of this application.
- Fig. 10 is a gas – flow diagram of the single – damping – structure piston assembly in the compressing movement in Embodiment 2 of this application.
Reference numerals in the drawings:
- 2: Closed cavity
- 3: Sealing member
- 4: Rear connecting part
- 5: Front connecting part
- 11: Piston body
- 12: Piston sleeve
- 13: Piston rod
- 111: Threaded damping groove
- 112: First communication hole
- 114: Groove
- 115: First protrusion
- 116: Second protrusion
- 131: First baffle
- 132: Second baffle
- 121: Second communication hole
- 1121: First left communication hole
- 1122: First right communication hole
- 1211: End – surface flow – through hole
- 1212: Side – surface flow – through hole
Detailed Implementation Modes
The following will disclose multiple embodiments of this application through drawings. The technical solutions of the present invention will be described clearly and completely. The attached drawings, which form part of this application, are provided to further understand the present invention. The illustrative embodiments and descriptions of the present invention are used to explain the present invention and do not constitute improper limitations to the present invention. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative efforts fall within the protection scope of the present invention.
It should be noted that, unless the direction is defined separately, the directions such as up, down, left, right, inner, and outer involved in this text are based on the up, down, left, right, inner, and outer directions shown in Fig. 1 of the embodiment of this application. If the specific posture changes, the directional indication will change accordingly. The meanings of “multiple” and “several” are two or more, which are explained here together. The use of words such as “first”, “second”, “third” and the like does not indicate any order, quantity, or importance, but are only used to distinguish different components. In addition, in each embodiment of the present disclosure, the same or similar reference numerals represent the same or similar components.
In the present invention, unless otherwise clearly defined and limited, terms such as “connection” and “fixation” should be understood in a broad sense. For example, “fixation” can be a fixed connection, a detachable connection, or an integral one, unless otherwise clearly limited. For those of ordinary skill in the art, the specific meanings of the above – mentioned terms in the present invention can be understood according to specific situations.
In addition, the technical solutions among the various embodiments of the present invention can be combined with each other, but it must be based on what can be achieved by those of ordinary skill in the art. When the combination of technical solutions leads to contradictions or cannot be realized, it should be considered that such a combination of technical solutions does not exist and is not within the protection scope claimed by the present invention.
Embodiment 1
Please refer to Figs. 1 to 7. In this embodiment, for a threaded groove damping device, as shown in Fig. 1, the fixed end of the damping device is connected to the front connecting part 5, and the other movable end is connected to the rear connecting part 4. The damping device in this embodiment includes a piston assembly and a closed cavity 2. There is a gap between the piston assembly and the closed cavity 2, that is, they are in clearance fit, enabling the piston assembly to reciprocate in the closed cavity 2, dividing the closed cavity 2 into a left – hand closed cavity and a right – hand closed cavity 2. A sealing member 3 is arranged in the closed cavity 2. The sealing member 3 is used to seal the gap between the piston assembly and the closed cavity 2, so that the extruded gas cannot pass through the closed gap but flows to the threaded damping groove. The piston assembly includes a piston body 11, a piston sleeve 12 closely sleeved on the piston body 11, and a piston rod 13 for transmission. The piston body 11 and the piston sleeve 12 are fixed at one end of the piston rod by a first baffle 131, a second baffle 132, and a set nut. Specifically, a damping structure and a first flow – through hole 112 are provided on the piston body 11, and a second flow – through hole 121 is provided on the piston sleeve 12. The second flow – through hole 121 is in communication with both the damping structure on the piston body 11 and the first flow – through hole. It should be noted that the damping structure is arranged circumferentially around the piston body 11, which lengthens the damping stroke of the piston body 11 and makes the movement of the piston assembly more stable.
Using the technical solution of this embodiment, when the piston assembly moves under the extrusion of gas or oil pressure in the closed cavity 2, the sealing member 3 arranged in the closed cavity 2 forms a frictional displacement with the inner wall of the closed cavity 2. The gas or oil pressure makes the sealing member 3 tightly seal the gap between the piston assembly and the closed cavity 2, causing the gas to pass through the first flow – through hole, the circumferential threaded damping groove, and the second flow – through hole. Since the threaded damping groove is arranged circumferentially around the piston body, the damping stroke for the gas or oil pressure is effectively extended, making the movement of the piston assembly stable, ensuring the smooth spring – back speed of the damping device. The design concept is ingenious. At the same time, the safety and service life are greatly improved, thus solving the problems that the traditional gas spring has a fast movement speed and cannot effectively ensure its safety and service life.
As shown in Figs. 4 and 5, as a specific implementation mode, the threaded damping groove 111 in this embodiment is a threaded slot. The threaded damping groove 111 is arranged at both ends of the piston body 11, that is, the piston body 11 has a double – damping structure. This enables the piston assembly to be damped during both stretching and compressing movements, making the movement stable and improving safety and service life. Of course, according to actual situations, it can also be set as a one – way damping.
It should be noted that the thread profile of this threaded slot is preferably triangular. Of course, according to actual situations, it can also be trapezoidal, rectangular, or other irregular shapes. Furthermore, its groove depth (i.e., the setting parameters of the thread crest and root) and groove width (i.e., the setting parameter of the pitch) and the length of the threaded groove are set according to the actual requirements of damping.
As shown in Figs. 2 and 3, further, in this embodiment, the threaded damping groove 11 is arranged circumferentially on the side surface of the piston body 11. The groove top 1111 of the threaded damping groove 111 is in close contact with the inner surface 123 of the piston sleeve 12. The machining depth of the threaded damping groove 111 (i.e., the position of the groove bottom 1112) and its length are designed according to the actual damping strength and the required spring – back speed. It should be noted that the material of the piston body is preferably hard plastic, the piston sleeve is preferably made of copper or aluminum, and the groove top 1111 of the threaded damping groove 111 is preferably processed into a pointed shape. This is more conducive to ensuring a tighter contact between the threaded damping groove 111 and the inner wall 123 of the piston sleeve 12, thus better guaranteeing the sealing performance and enabling the flowing gas or liquid oil to flow along the path of the threaded damping groove 111.
As shown in Figs. 6 and 7, as a specific implementation mode, the second flow – through hole 121 on the piston sleeve 12 in this embodiment includes a side – surface flow – through hole 1211 and an end – surface communication hole 1212. As shown in Figs. 3 and 4, the end – surface communication hole 1212 is adapted to the first flow – through hole 112.
It should be noted that the end – surface communication hole 1212 in this embodiment is a circular blind hole, and the first flow – through hole 112 is a circular through – hole. However, their adaptation is not limited to circular holes, and they can be set as square holes, polygonal holes, or other special – shaped holes.
As shown in Figs. 4 and 5, as a specific implementation mode, a first protrusion 115 and a second protrusion 116 are provided on the piston body 11 in this embodiment. Both the first protrusion 115 and the second protrusion 116 are circumferential annular protrusions around the piston body, and a groove 114 is formed between them. Further, the first flow – through hole 112 in this embodiment includes a first left flow – through hole 1121 and a first right flow – through hole 1122. Furthermore, the first left flow – through hole 1121 and the first right flow – through hole 1122 are respectively provided on the first protrusion 115 and the second protrusion 116.
As shown in Figs. 2 and 3, as a specific implementation mode, one end of the threaded damping groove 111 in this embodiment is connected to the side – surface flow – through hole 1211, and the other end is connected to the end – surface communication hole 1212, which is connected to the first communication hole. Preferably, the sealing member 3 in this embodiment is arranged in the groove 114.
It should be noted that in this embodiment, the sealing member 3 is preferably a floating O – ring. The outer circle of the O – ring abuts against the inner wall of the closed cavity 2, and there is a certain distance between its inner circle and the bottom of the groove 114, allowing the gas flow to smoothly enter the first flow – through hole from the groove. This design can better utilize the principle of pressure to make the floating O – ring tightly abut against the inner wall of the closed cavity 2 and the side of the groove, thus achieving a better sealing effect. Moreover, it should be noted that the width of the groove 114 is greater than the maximum diameter of the cross – section of the sealing member 3, enabling the sealing member 3 to move within the groove and achieve the effect of sealing the gap on one side.
As shown in the gas – flow diagrams of the stretching and compressing movements in Figs. 2 and 3, the working principle of the two – way damping of this embodiment’s damping device with a double – damping structure when applied to a gas spring is described as follows:
- Stretching Damping Movement: When performing a stretching movement to the right, first, the sealing member 3 in the closed cavity 2 is frictionally displaced to the left side of the groove 114. The gas pressure further prompts the sealing member 3 to tightly abut against the inner wall of the closed cavity 2 and the left side of the groove 114, sealing the left – hand gap between the closed cavity 2 and the piston assembly. Furthermore, the piston assembly squeezes the gas in the right – hand closed cavity, causing the gas to flow and be released into the left – hand closed cavity. At this time, only a small part of the gas flows into the right – hand threaded damping groove through the side – surface flow – through hole on the right – hand piston sleeve 12 and then enters the groove through the first right – hand flow – through hole 1122. Instead, the vast majority of the gas directly flows into the groove through the right – hand gap between the closed cavity 2 and the piston assembly. Then, it flows into the super – long left – hand threaded damping groove through the first left – hand flow – through hole 1121 and the end – surface flow – through hole on the left – hand piston sleeve 12. Finally, it flows into the left – hand closed cavity through the side – surface flow – through hole on the left – hand piston sleeve 12, thus completing a stable stretching damping movement.
- Compressing Damping Movement: When performing a compressing movement to the left, first, the sealing member 3 in the closed cavity 2 is frictionally displaced to the right side of the groove 114. The gas pressure further prompts the sealing member 3 to tightly abut against the inner wall of the closed cavity 2 and the right side of the groove 114, sealing the right – hand gap between the closed cavity 2 and the piston assembly. Furthermore, the piston assembly squeezes the gas in the left – hand closed cavity, causing the gas to flow and be released into the right – hand closed cavity. At this time, only a small part of the gas flows into the left – hand threaded damping groove through the side – surface flow – through hole on the left – hand piston sleeve 12 and then enters the groove through the first left – hand flow – through hole. Instead, the vast majority of the gas directly flows into the groove through the left – hand gap between the closed cavity 2 and the piston assembly. Then, it flows into the super – long right – hand threaded damping groove through the first right – hand flow – through hole and the end – surface flow – through hole on the right – hand piston sleeve 12. Finally, it flows into the right – hand closed cavity through the side – surface flow – through hole on the right – hand piston sleeve 12, thus completing a stable compressing damping movement.
Embodiment 2
The difference between this embodiment and Embodiment 1 is that, as shown in Fig. 8, the threaded damping groove 111 in this embodiment is arranged at one end of the piston body 11, that is, the piston body has a single – damping structure.
As shown in the gas – flow diagrams of the stretching and compressing movements in Figs. 9 and 10, the working principle of this embodiment’s damping device with a single – damping structure when applied to a gas spring is described as follows:
- Stretching Damping Movement: When performing a stretching movement to the right, first, the sealing member 3 in the closed cavity 2 is frictionally displaced to the left side of the groove 114. The gas pressure further prompts the sealing member 3 to tightly abut against the inner wall of the closed cavity 2 and the left side of the groove 114, sealing the left – hand gap between the closed cavity 2 and the piston assembly. Furthermore, the piston assembly squeezes the gas in the right – hand closed cavity, causing the gas to flow and be released into the left – hand closed cavity. At this time, the gas enters the groove through the first right – hand flow – through hole 1122 and/or the right – hand gap. Then, it flows into the super – long threaded damping groove through the first left – hand flow – through hole 1121 and the end – surface flow – through hole on the left – hand piston sleeve 12. Finally, it flows into the left – hand closed cavity through the side – surface flow – through hole on the piston sleeve 12, thus completing a stable stretching damping movement.
- Compressing Damping Movement: When performing a compressing movement to the left, first, the sealing member 3 in the closed cavity 2 is frictionally displaced to the right side of the groove 114. The gas pressure further prompts the sealing member 3 to tightly abut against the inner wall of the closed cavity 2 and the right side of the groove 114, sealing the right – hand gap between the closed cavity 2 and the piston assembly. Furthermore, the piston assembly squeezes the gas in the left – hand closed cavity, and the entire gas is in a compressed state, causing the gas to flow and be released into the right – hand closed cavity. At this time, only a small part of the gas flows into the left – hand threaded damping groove through the side – surface flow – through hole on the left – hand piston sleeve 12 and then enters the groove through the first left – hand flow – through hole. Instead, the vast majority of the gas directly flows into the groove through the left – hand gap between the closed cavity 2 and the piston assembly. Then, it directly flows into the right – hand closed cavity only through the first right – hand flow – through hole, thus completing the compressing damping movement. This kind of compressing damping is the characteristic of an ordinary compressed gas spring that only uses the damping hole for damping.
In conclusion, when the piston assembly in this application moves under the extrusion of gas or oil pressure in the closed cavity, the sealing member arranged in the closed cavity forms a frictional displacement with the inner wall of the closed cavity. The gas or oil pressure makes the sealing member tightly seal the gap between the piston assembly and the closed cavity, causing the gas to pass through the first flow – through hole, the circumferential damping structure, and the second flow – through hole. Since this super – long damping structure is arranged circumferentially around the piston body, the damping stroke for the gas or oil pressure is effectively extended, making the movement of the piston assembly stable, ensuring the smooth spring – back speed of the damping device. The design concept is ingenious. At the same time, the safety and service life are greatly improved, thus solving the problems that the traditional gas spring has a fast movement speed and cannot effectively ensure its safety and service life.
The above description shows and describes the preferred embodiments of this application. However, as mentioned before, it should be understood that this application is not limited to the forms disclosed herein. It should not be regarded as excluding other embodiments, but can be used in various other combinations, modifications, and environments, and can be changed within the scope of the concept of this application through the above teachings or the technologies or knowledge in related fields. Any changes and variations made by those skilled in the art without departing from the spirit and scope of this application shall fall within the protection scope of the appended claims of this application.
Claims (10) – A Threaded Groove Damping Gas Spring, invented by LeiYan Gas Spring, a pioneer Chinese Gas Spring Manufacturer.
- A threaded groove damping device, comprising a piston assembly and a closed cavity (2), characterized in that: a gap is provided between the piston assembly and the inner wall of the closed cavity (2), and the piston assembly reciprocates in the closed cavity;
a sealing member (3) is provided in the closed cavity (2), and the sealing member (3) is used to seal the gap;
the piston assembly comprises a piston body (11) and a piston sleeve (12) closely sleeved on the piston body (11). A damping structure and a first flow – through hole (112) are provided on the piston body (11). The damping structure is a threaded damping groove, which is arranged circumferentially around the piston body (11). A second flow – through hole (121) is provided on the piston sleeve (12), and the second flow – through hole (121) is in communication with both the threaded damping groove on the piston body (11) and the first flow – through hole (112). - The threaded groove damping device according to claim 1, characterized in that the threaded damping groove (111) is provided at both ends of the piston body (11) or at one end of the piston body (11).
- The threaded groove damping device according to claim 1 or 2, characterized in that the second flow – through hole (121) comprises a side – surface flow – through hole (1212) and an end – surface communication hole (1211), and the end – surface communication hole (1211) is adapted to the first flow – through hole (112).
- The threaded groove damping device according to claim 3, characterized in that one end of the threaded damping groove (111) is connected to the side – surface flow – through hole (1212), and the other end is connected to the end – surface communication hole (1211), and the end – surface communication hole (1211) is connected to the first communication hole (112).
- The threaded groove damping device according to claim 2, characterized in that the threaded damping groove (111) is provided on the side surface of the piston body (11).
- The threaded groove damping device according to claim 2, characterized in that the groove top (1111) of the threaded damping groove (111) is in close contact with the inner surface of the piston sleeve (12).
- The threaded groove damping device according to claim 1, characterized in that a first protrusion (115) and a second protrusion (116) are provided on the piston body (11), and a groove (114) is formed between the first protrusion (115) and the second protrusion (116).
- The threaded groove damping device according to claim 7, characterized in that the sealing member (3) moves in the groove (114).
- The threaded groove damping device according to claim 1 or 7, characterized in that the first flow – through hole (112) comprises a first left flow – through hole (1121) and a first right flow – through hole (1122).
- The threaded groove damping device according to claim 9, characterized in that the first left flow – through hole (1121) is provided on the first protrusion (115), and the first right flow – through hole is provided on the second protrusion (116).
damping compression gas spring that can stop doors and windows
Patent No.:CN211778709U Date:2019-07-10
Google Patent: https://patents.google.com/patent/CN211778709U/en?oq=CN211778709U
China Patent: http://epub.cnipa.gov.cn/
Abstract
This utility model discloses a damping compression gas spring that can stop doors and windows, including a cylinder, a rear end block, a guiding assembly, and a piston rod assembly. Several sections of bypass grooves are arranged on the inner sidewall of the cylinder, set at intervals along the axial direction of the cylinder.
The piston rod assembly includes a piston assembly and a piston rod, with the piston assembly dividing the cylinder into a front chamber and a rear chamber. The piston assembly includes a piston body; a flow channel is provided on the piston body to communicate the front and rear chambers. The piston body also has a first one-way sealing element that can open or close the flow channel.
When the piston assembly moves towards the front end of the cylinder, the first one-way sealing element opens the flow channel. When the piston assembly moves towards the rear end of the cylinder, the first one-way sealing element closes the flow channel.
In the axial direction of the cylinder, the length of each bypass groove is greater than the length of the contact part between the first one-way sealing element and the inner sidewall of the cylinder. This utility model has the advantages of a simple structure, convenience in use, and high compressive strength.
Technical Field
This utility model relates to the field of gas spring technology, specifically to a damping compression gas spring that can stop doors and windows.
Background Technology
A gas spring is an industrial component that can perform functions such as support, buffering, braking, height adjustment, and angle adjustment. It mainly consists of a pressure cylinder, piston rod, piston, sealing guide sleeve, filling material, and joints. The principle is to fill the enclosed pressure cylinder with an inert gas or oil-gas mixture, making the pressure inside the chamber several or even dozens of times higher than atmospheric pressure. The movement of the piston rod is realized by the pressure difference caused by the difference in the force area on both ends of the piston rod.
Currently, the gas springs on the market are mainly free type, which can only stop at the shortest or longest positions and cannot stop by themselves during the stroke, which has significant limitations, such as being unsuitable for controlling the opening and closing of doors and windows. Some self-locking and stay-type gas springs can stop at any position within the stroke, but this is generally achieved through a release mechanism or controller, increasing the difficulty of installation and debugging.
An existing example disclosed in Chinese Patent Application Number CN201120003352.4 describes a stoppable compression gas spring with a cylinder with axial damping grooves on the inner wall, a piston rod, and a rear end block fixedly sealed at the rear of the cylinder. The guide sleeve and sealing ring set are installed on the piston rod and within the cylinder, with one end of the piston rod extending out of the cylinder and another end having a piston. The piston is equipped with a damping ring at the rear of the oil passage, aligning with the axial damping grooves of the cylinder. The cylinder’s inner wall has more than one annular surface isolating the axial damping grooves, each composed of more than two independent damping grooves. Although this utility model has a simple structure and can meet the requirements of different work strokes, its compressive performance is poor, making it difficult to stabilize in different strokes and easy to compress back to a compressed state. It requires considerable effort to extend it, making it cumbersome and labor-intensive to use.
Summary of the Utility Model
This utility model aims to address the defects and shortcomings of existing technology by providing a damping compression gas spring that can stop doors and windows, offering the advantages of a simple structure, easy use, and high compressive strength.
The technical solution adopted to solve its technical problem is as follows: A damping compression gas spring that can stop doors and windows includes a cylinder, a rear end block, a guiding assembly, and a piston rod assembly. The guiding assembly is fixedly sealed at the front end of the cylinder, and the rear end block is fixedly sealed at the rear end of the cylinder. Several sections of bypass grooves are arranged on the inner sidewall of the cylinder, set at intervals along the axial direction of the cylinder.
The piston rod assembly includes a piston assembly that slidably and sealingly fits with the inner sidewall of the cylinder as well as a piston rod. The piston assembly divides the cylinder into a front chamber and a rear chamber, comprising a piston body fixed at the rear end of the piston rod. The front end of the piston rod extends out of the cylinder and slidably and sealingly fits with the guiding assembly. The piston body has a flow channel to communicate the front chamber and the rear chamber and a first one-way sealing element that can open or close the flow channel.
When the piston assembly moves towards the front end of the cylinder, the first one-way sealing element opens the flow channel. When the piston assembly moves towards the rear end of the cylinder, the first one-way sealing element closes the flow channel. The length of each bypass groove in the axial direction of the cylinder is greater than the length of the contact part between the first one-way sealing element and the inner sidewall of the cylinder.
Further Details
The side wall of the cylinder protrudes outward to form the bypass groove, making the structure simple and easy to manufacture.
The piston assembly also includes piston pads press-fitted each at one end of the piston body, both fitted with through holes corresponding to the flow channel, and a sealing friction ring that opens and closes the holes. When the piston assembly moves towards the front end of the cylinder, the sealing friction ring opens the holes. When the piston assembly moves towards the rear end, the sealing friction ring closes the holes.
Both ends of the piston body are provided with annular steps consisting of a step surface and a cylindrical surface, through which the flow channel passes. The sealing friction ring slidably fits the front cylindrical surface, and the first one-way sealing element slidably fits the rear cylindrical surface.
The first one-way sealing element uses a Y-shaped sealing ring with lips facing the rear end of the cylinder. The sealing element fits tightly with the cylindrical surface, enhancing the relative sealing of the front and rear chambers.
The guiding assembly includes a front guide sleeve fixed at the front end of the cylinder and a second one-way sealing element.
The second one-way sealing element uses a Y-shaped sealing ring with lips facing the rear end of the cylinder.
The outer end of the rear end block is fixed with a rear connector, and the front end of the piston rod is fixed with a front connector.
An O-ring is provided at the junction of the rear end block and the cylinder to improve the sealing of the inner cavity of the cylinder.
Benefits
By providing a flow channel communicating the front and rear chambers on the piston body, and a first one-way sealing element that opens and closes the flow channel: when the piston assembly moves towards the front end of the cylinder, it slides relative to the cylinder while the first one-way sealing element slides relative to the piston body, opening the flow channel. The gas in the front chamber quickly flows to the rear chamber, allowing the piston rod to extend easily and quickly.
When the piston assembly moves towards the rear end of the cylinder, the sliding of the piston body relative to the cylinder and the first one-way sealing element relative to the piston body closes the flow channel, preventing gas from flowing from the front chamber to the rear chamber, stopping the piston rod assembly from moving relative to the cylinder and enabling it to withstand higher pressure with strong compressive performance.
Additionally, the length of the bypass groove in the axial direction of the cylinder is greater than the length of the contact part between the sealing element and the inner wall of the cylinder, allowing the piston rod assembly to stop at any position along the axial direction of the cylinder, with strong compressive performance. Overall, this utility model has the advantages of simple structure, ease of use, and high compressive strength.
Description of Drawings
Fig. 1: Schematic diagram of the overall structure of the utility model. Fig. 2: Enlarged schematic diagram of the guiding assembly in this utility model. Fig. 3: Schematic diagram of the flow channel closing in this utility model. Fig. 4: Schematic diagram of the flow channel opening in this utility model. Fig. 5: Cross-sectional schematic diagram of the cylinder in this utility model.
Legend: 1 – Cylinder; 11 – Bypass Groove; 2 – Rear End Block; 3 – Guiding Assembly; 31 – Front Guide Sleeve; 32 – Second One-Way Sealing Element; 4 – Piston Rod Assembly; 41 – Piston Assembly; 411 – Piston Body; 4111 – Flow Channel; 4112 – Annular Step; 412 – First One-Way Sealing Element; 413 – Piston Pad; 4131 – Through Hole; 414 – Sealing Friction Ring; 42 – Piston Rod; 5 – Front Chamber; 6 – Rear Chamber; 7 – Rear Connector; 8 – Front Connector; 9 – O-Ring.
Specific Embodiments
For a more intuitive and complete understanding of the technical solution of this utility model, the non-restrictive feature description in conjunction with the attached figures is as follows:
As shown in Figures 1 to 5, a damping compression gas spring that can stop doors and windows includes a cylinder 1, a rear end block 2, a guiding assembly 3, and a piston rod assembly 4. The guiding assembly 3 is fixedly sealed at the front end of the cylinder 1, and the rear end block 2 is fixedly sealed at the rear end of the cylinder 1. Several sections of bypass grooves 11 are arranged on the inner sidewall of the cylinder 1, set at intervals along the axial direction of the cylinder 1. The piston rod assembly 4 includes a piston assembly 41 that slidably and sealingly fits with the inner sidewall of the cylinder 1 as well as a piston rod 42. The piston assembly 41 divides the cylinder 1 into a front chamber 5 and a rear chamber 6. The piston assembly 41 includes a piston body 411, fixed at the rear end of the piston rod 42. The front end of the piston rod 42 extends out of the cylinder 1 and slidably and sealingly fits with the guiding assembly 3. The piston body 411 has a flow channel 4111 to communicate the front chamber 5 and the rear chamber 6, and a first one-way sealing element 412 that can open or close the flow channel 4111. When the piston assembly 41 moves towards the front end of the cylinder 1, the first one-way sealing element 412 opens the flow channel 4111. When the piston assembly 41 moves towards the rear end of the cylinder 1, the first one-way sealing element 412 closes the flow channel 4111. The length of each bypass groove 11 in the axial direction of the cylinder 1 is greater than the length of the contact part between the first one-way sealing element 412 and the inner wall of the cylinder 1.
Specifically, inert gas nitrogen is filled in both the front chamber 5 and the rear chamber 6 of the cylinder 1.
The side wall of the cylinder 1 protrudes outward to form the bypass grooves 11 through a riveting or stamping process, making it easy to manufacture.
The piston assembly 41 also includes piston pads 413 press-fitted each at one end of the piston body 411, both fitted with through holes 4131 corresponding to the flow channel 4111, and a sealing friction ring 414 that opens and closes the holes 4131. When the piston assembly 41 moves towards the front end of the cylinder 1, the sealing friction ring 414 opens the holes 4131. When the piston assembly 41 moves towards the rear end of the cylinder 1, the sealing friction ring 414 closes the holes 4131.
Preferably, during installation, the components are successively sleeved onto the rear end of the piston rod 42 in the order of: piston pad 413, piston body 411, first one-way sealing element 412, and piston pad 413, then fixed by a spinning riveting process, ensuring reliable connection and easy manufacturing and installation. The sealing friction ring 414 can be installed before or after the spinning riveting process.
Both ends of the piston body 411 are provided with annular steps 4112, which consist of a step surface and a cylindrical surface. The flow channel 4111 passes through the step surface, and the sealing friction ring 414 fits slidably with the front cylindrical surface, while the first one-way sealing element 412 fits slidably with the rear cylindrical surface. The first one-way sealing element 412 uses a Y-shaped sealing ring with lips facing the rear end of the cylinder 1. The sealing element fits tightly with the cylindrical surface, forming a cone surface to enhance the sealing of the front and rear chambers.
Specifically, the sealing friction ring 414 also uses a Y-shaped sealing ring with lips facing the rear end of the cylinder 1. The front cylindrical surface has a cone surface near the front step surface. When the sealing friction ring 414 opens the holes 4131, gas flows through the holes 4131, passing through this cone surface and the gap formed by the inner circle of the sealing friction ring 414, eventually flowing through the flow channel 4111 to the rear end of the piston body 411. The outer circle of the sealing friction ring 414 is cylindrical and fits slidably and sealingly with the cylinder 1, ensuring the relative sealing of the front chamber 5 and the rear chamber 6.
The guiding assembly 3 includes a front guide sleeve 31 fixed at the front end of the cylinder 1 and a second one-way sealing element 32, which uses a Y-shaped sealing ring with lips facing the rear end of the cylinder 1.
The outer end of the rear end block 2 is fixed with a rear connector 7, and the front end of the piston rod 42 is fixed with a front connector 8. Two O-rings 9 are provided at the junction of the rear end block 2 and the cylinder 1.
Preferably, the front guide sleeve 31 and the rear end block 2 are sealed to both ends of the cylinder 1 by a riveting process. Holes for connecting and installing the gas spring are provided on both the front connector 8 and the rear connector 7.
Working Principle
The specific working principle of this utility model is as follows: When extending the piston rod 42, during the extension process, the piston assembly 41 slides relative to the cylinder 1, and both the first one-way sealing element 412 and the sealing friction ring 414 slide relative to the annular steps 4112, with their lips facing the rear end of the cylinder 1. This opens the flow channel 4111 and the holes 4131, allowing nitrogen gas from the front chamber 5 to flow through the through holes 4131 on the front piston pad 413, the flow channel 4111, and the through holes 4131 on the rear piston pad 413 to the rear chamber 6, enabling the piston rod 42 to extend quickly and easily, as shown in Figure 4.
During use, when the piston rod 42 is under pressure, the piston assembly 41 slides relative to the cylinder 1, while the first one-way sealing element 412 and the sealing friction ring 414 slide relative to the annular steps 4112, with their lips facing the front end of the cylinder 1. This closes the flow channel 4111 and the holes 4131, preventing the nitrogen gas from flowing between the front chamber 5 and the rear chamber 6, keeping the piston rod assembly 4 fixed relative to the cylinder 1, as shown in Figure 3.
To adjust the extended length of the piston rod 42, when more extension is needed, repeat the extension steps. Note that when the first one-way sealing element 412 is in contact with the inner sidewall position between adjacent bypass grooves 11, the gas in the front chamber 5 and the rear chamber 6 does not flow between chambers.
When retraction is needed, apply more pressure to the piston rod 42 to compress the rear chamber 6, causing the piston assembly 41 to slide relative to the cylinder 1. When the contact area between the first one-way sealing element 412 and the inner sidewall of the cylinder 1 slides to the bypass grooves 11, the rear chamber 6 flows through the bypass grooves 11 to the front chamber 5. At this point, the piston rod assembly 4 can slide quickly and easily relative to the cylinder 1 until the first one-way sealing element 412 and the inner sidewall of the cylinder 1 contact the inner sidewall position between the adjacent bypass grooves 11 again, causing the piston rod assembly 4 to stop moving relative to the cylinder 1 and remain fixed again. Likewise, to stop the piston rod 42 at different stroke positions, repeat the above operation to make adjustments.
The above description is merely the preferred embodiment of this utility model. Therefore, any equivalent changes or modifications made according to the structural, characteristic, and principle described in the claims of this utility model are included in the scope of this utility model.
Claims – A damping compression gas spring that can stop doors and windows, invented by LeiYan Gas Spring, a pioneer Chinese Gas Spring Manufacture
- A damping compression gas spring that can stop doors and windows, comprising a cylinder (1), a rear end block (2), a guiding assembly (3), and a piston rod assembly (4). The guiding assembly (3) is fixedly sealed at the front end of the cylinder (1), and the rear end block (2) is fixedly sealed at the rear end of the cylinder (1). Several sections of bypass grooves (11) are arranged on the inner sidewall of the cylinder (1), set at intervals along the axial direction of the cylinder (1). The piston rod assembly (4) includes a piston assembly (41) that slidably and sealingly fits with the inner sidewall of the cylinder (1) as well as a piston rod (42). The piston assembly (41) divides the cylinder (1) into a front chamber (5) and a rear chamber (6). The piston assembly (41) includes a piston body (411), fixed at the rear end of the piston rod (42). The front end of the piston rod (42) extends out of the cylinder (1) and slidably and sealingly fits with the guiding assembly (3). The feature is that the piston body (411) has a flow channel (4111) to communicate the front chamber (5) and the rear chamber (6), and a first one-way sealing element (412) that can open or close the flow channel (4111). When the piston assembly (41) moves towards the front end of the cylinder (1), the first one-way sealing element (412) opens the flow channel (4111). When the piston assembly (41) moves towards the rear end of the cylinder (1), the first one-way sealing element (412) closes the flow channel (4111). The length of each bypass groove (11) in the axial direction of the cylinder (1) is greater than the length of the contact part between the first one-way sealing element (412) and the inner wall of the cylinder (1).
- The damping compression gas spring as described in claim 1, wherein the side wall of the cylinder (1) protrudes outward to form the bypass grooves (11).
- The damping compression gas spring as described in claim 1, wherein the piston assembly (41) also includes piston pads (413) press-fitted each at one end of the piston body (411). Both piston pads (413) are fitted with through holes (4131) corresponding to the flow channel (4111), and a sealing friction ring (414) that opens and closes the holes (4131). When the piston assembly (41) moves towards the front end of the cylinder (1), the sealing friction ring (414) opens the holes (4131). When the piston assembly (41) moves towards the rear end of the cylinder (1), the sealing friction ring (414) closes the holes (4131).
- The damping compression gas spring as described in claim 3, wherein both ends of the piston body (411) are provided with annular steps (4112) consisting of a step surface and a cylindrical surface. The flow channel (4111) passes through the step surface, and the sealing friction ring (414) fits slidably with the front cylindrical surface while the first one-way sealing element (412) fits slidably with the rear cylindrical surface.
- The damping compression gas spring as described in claim 4, wherein the first one-way sealing element (412) uses a Y-shaped sealing ring with lips facing the rear end of the cylinder (1). The sealing element fits tightly with the cylindrical surface, forming a cone surface.
- The damping compression gas spring as described in claim 1, wherein the guiding assembly (3) includes a front guide sleeve (31) fixed at the front end of the cylinder (1) and a second one-way sealing element (32).
- The damping compression gas spring as described in claim 6, wherein the second one-way sealing element (32) uses a Y-shaped sealing ring with lips facing the rear end of the cylinder (1).
- The damping compression gas spring as described in claim 1, wherein the outer end of the rear end block (2) is fixed with a rear connector (7), and the front end of the piston rod (42) is fixed with a front connector (8).
- The damping compression gas spring as described in claim 8, wherein an O-ring (9) is provided at the junction of the rear end block (2) and the cylinder (1).