CN109630499B - Floating type low-friction sealing ring cylinder - Google Patents
Floating type low-friction sealing ring cylinder Download PDFInfo
- Publication number
- CN109630499B CN109630499B CN201811638562.3A CN201811638562A CN109630499B CN 109630499 B CN109630499 B CN 109630499B CN 201811638562 A CN201811638562 A CN 201811638562A CN 109630499 B CN109630499 B CN 109630499B
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- Prior art keywords
- sealing ring
- piston
- sealing
- cylinder
- groove
- Prior art date
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- 238000007789 sealing Methods 0.000 title claims abstract description 144
- 238000005299 abrasion Methods 0.000 description 5
- 238000009423 ventilation Methods 0.000 description 5
- 239000000463 material Substances 0.000 description 4
- 238000003754 machining Methods 0.000 description 3
- 238000012986 modification Methods 0.000 description 3
- 230000004048 modification Effects 0.000 description 3
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 239000004519 grease Substances 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000008092 positive effect Effects 0.000 description 2
- 230000007547 defect Effects 0.000 description 1
- 229920006351 engineering plastic Polymers 0.000 description 1
- 238000001125 extrusion Methods 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
- F15B15/1423—Component parts; Constructional details
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
- F15B15/1423—Component parts; Constructional details
- F15B15/1447—Pistons; Piston to piston rod assemblies
- F15B15/1452—Piston sealings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2215/00—Fluid-actuated devices for displacing a member from one position to another
- F15B2215/30—Constructional details thereof
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/80—Technologies aiming to reduce greenhouse gasses emissions common to all road transportation technologies
- Y02T10/86—Optimisation of rolling resistance, e.g. weight reduction
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Sealing Devices (AREA)
- Pistons, Piston Rings, And Cylinders (AREA)
Abstract
The application provides a floating type low-friction sealing ring cylinder, which comprises: the piston is arranged in the cylinder barrel and connected with the piston rod, and the piston sealing ring groove is an annular groove body positioned on the piston, and the section of the piston sealing ring groove is Y-shaped; the cross section of the sealing ring is Y-shaped, the radial outer surface of the sealing ring is an outwards-protruding arc-shaped sealing part, and the Y-shaped linear part of the sealing ring comprises a plurality of protruding sealing parts which are axially and symmetrically protruding; the sealing ring is sleeved with a connecting piston sealing ring groove, and the inner ring of the sealing ring does not contact the bottom of the piston sealing ring groove. The pressure of the sealing ring to the cylinder barrel is only generated by the forming supporting force of the sealing ring per se, and the sealing ring does not have the sealing pressure to the bottom of the sealing ring groove of the piston, so the pressure is small and the movement is quick.
Description
Technical Field
The application relates to the technical field of air cylinders, in particular to an air cylinder with a floating type low-friction sealing ring adopted by an air cylinder piston.
Background
The low friction cylinder is a cylinder with small sliding resistance of a piston, is commonly used for supporting a load, and is used for supporting and balancing the load force when the load force value changes. Thus requiring extremely low frictional resistance and rapid response speed when the cylinder piston moves. As shown in fig. 1, the generation of the sliding resistance of the cylinder piston is generally composed of friction force of a guide sleeve 1, a support ring 2 and a cylinder sealing ring 3.
With the development of self-lubricating engineering plastics and the application and development of industrial grease in different industries. When the cylinder piston slides, the friction resistance of the guide sleeve 1 and the support ring 2 is negligible. The friction force generated by the cylinder sealing ring 3 accounts for more than 80% of the sliding resistance of the piston, and the friction force of the cylinder sealing ring 3 mainly comprises the following 3 parts, namely 1. The friction coefficient between the sealing ring and the cylinder barrel (the machining precision and the finish of the inner hole of the cylinder barrel, the finish of the surface of the sealing ring and the movement of lubricating grease between the sealing ring and the cylinder barrel); 2. the design interference of the sealing ring (namely the pressure of the sealing ring to the cylinder) 3. The contact area between the sealing ring and the cylinder.
At present, a common low-friction sealing ring suitable for a piston generally adopts a design structure of reducing the sealing ring pressure to reduce friction resistance, wherein the design structure is shown in fig. 2, and the contact area between the sealing ring 3 and a cylinder barrel is reduced, or the design structure is shown in fig. 3, and the design structure is shown in fig. 3. However, as the design structure of the sealing ring and the bottom of the piston sealing ring groove is not changed all the time, the problem that the pressure of the sealing ring to the cylinder barrel can be increased when the design interference pressure of the sealing ring is too large can be solved. There are always 2 problems:
1. the design interference pressure of the sealing ring is smaller, and the relative abrasion movement life is shorter;
2. when the sealing ring is worn by a side force and a single side, the sealing ring cannot be effectively compensated due to small interference pressure of the sealing ring design, and the sealing ring is easy to fail.
Therefore, the cylinder in the prior art has a few technical problems to be solved.
Disclosure of Invention
Aiming at the defects, the application aims to provide a cylinder with a floating type low-friction sealing ring adopted by a cylinder piston, so as to solve the technical problems in the prior art.
In order to achieve the above purpose, the present application adopts the following technical scheme:
a floating low friction seal ring cylinder comprising: the piston rod penetrates through the front cover, part of the piston rod is arranged in the cylinder barrel, the piston is arranged in the cylinder barrel and connected with the piston rod, and the piston also comprises a sealing ring and a piston sealing ring groove, wherein the piston sealing ring groove is an annular groove body positioned on the piston, and the section of the piston sealing ring groove is Y-shaped; the cross section of the sealing ring is Y-shaped, the radial outer surface of the sealing ring is an arc-shaped sealing part protruding outwards, and the Y-shaped linear part of the sealing ring comprises a plurality of protruding sealing parts protruding axially symmetrically; the sealing ring is sleeved with the piston sealing ring groove, and the inner ring of the sealing ring does not contact the bottom of the piston sealing ring groove.
According to the floating type low-friction sealing ring cylinder disclosed by the embodiment of the application, the sealing ring further comprises a plurality of air vents, and the air vents are positioned at the outermost edges of two sides of the sealing ring.
The application improves the existing cylinder, changes the sealing form between the sealing ring and the piston sealing ring groove, and ensures that the pressure of the sealing ring to the cylinder barrel is only generated by the forming supporting force of the sealing ring per se, which is far smaller than the internal stress of the sealing member during material compression, and the pressure of the sealing ring to the cylinder barrel is smaller, so that the designed interference pressure can be more, more wear compensation and longer service life; the abdication of the piston seal ring groove is less, and the contact area of the seal ring and the cylinder barrel is smaller; the trend that the contact area of the sealing ring with the cylinder barrel is increased when the sealing ring is compressed and deformed by the cylinder barrel is avoided; the piston sealing ring groove is processed without concentricity requirement, and because of floating, the piston sealing ring groove automatically and concentrically trends under the action of the inner hole of the cylinder barrel, and the quick response and the stability of the cylinder are improved.
Due to the adoption of the technical characteristics, compared with the prior art, the application has the following advantages and positive effects:
the pressure of the sealing ring to the cylinder barrel is only generated by the forming supporting force of the sealing ring, and the sealing ring does not have the sealing pressure to the bottom of the piston sealing ring groove, so the pressure is small;
secondly, the pressure of the sealing ring to the cylinder barrel is smaller, the designed interference pressure can be more, more abrasion compensation is realized, and the service life is longer;
thirdly, the piston seal ring groove is processed without concentricity requirement, and because of floating, the piston seal ring groove automatically and concentrically trends under the action of the inner hole of the cylinder barrel, and the quick response and the stability of the cylinder are improved.
Of course, it is not necessary for any one embodiment to practice the teachings of the present application to have all of the above described advantages.
Drawings
FIG. 1 is a schematic cut-away view of a prior art cylinder;
FIG. 2 is a schematic illustration of a prior art seal ring;
FIG. 3 is another schematic view of a prior art seal ring;
FIG. 4 is a schematic view of a seal ring and piston seal groove of the present application;
FIG. 5 is a schematic perspective view of a seal ring of the present application;
FIG. 6 is a schematic cut-away view of a seal ring of the present application;
FIG. 7 is a front view of a seal ring of the present application;
fig. 8 is a schematic view of the movement of the seal ring and the piston seal groove of the present application.
Detailed Description
Several preferred embodiments of the present application will be described in detail below with reference to the attached drawings, but the present application is not limited to these embodiments only. The application is intended to cover any alternatives, modifications, equivalents, and variations that fall within the spirit and scope of the application. In the following description of preferred embodiments of the application, specific details are set forth in order to provide a thorough understanding of the application, and the application will be fully understood to those skilled in the art without such details. In other instances, well-known methods, procedures, flows, components, and so forth have not been described in detail so as not to unnecessarily obscure aspects of the present application.
The floating type low-friction sealing ring cylinder comprises: the front cover, the rear cover, the cylinder barrel, the piston rod and the piston are sequentially connected, the piston rod penetrates through the front cover, part of the piston rod is arranged in the cylinder barrel, the piston is arranged in the cylinder barrel and connected with the piston rod, and the piston also comprises a sealing ring 10 and a piston sealing ring groove 20 as shown in fig. 4. The piston sealing ring groove 20 is an annular groove body positioned on the piston, and the cross section of the piston sealing ring groove 20 is Y-shaped.
In addition, referring to fig. 5, fig. 6 and fig. 7, the cross section of the seal ring 10 is Y-shaped, the radial outer surface of the seal ring 10 is an arc-shaped sealing portion 11 protruding outwards, the Y-shaped portion of the seal ring 10 includes a plurality of protruding sealing portions 12 protruding axially symmetrically, the protruding sealing portions 12 are attached to the piston seal ring groove 20 to achieve a sealing effect, as shown in fig. 6, the number of protruding sealing portions 12 protruding symmetrically is two each, but the application cannot be limited, and more or less, as long as the sealing requirement can be met, is the protection scope of the application; the sealing ring 10 is sleeved and connected with the piston sealing ring groove 20, as shown in fig. 4, the inner ring of the sealing ring 10 does not contact the bottom of the piston sealing ring groove 20, and enough space is designed at the bottom of the groove for yielding when the sealing ring 10 and the cylinder barrel form interference, so that the compression of the sealing ring 10 to the bottom of the piston sealing ring groove can not be generated, and the pressure is reduced.
In addition, as shown in fig. 5 and 7, the sealing ring 10 further includes a plurality of air vents 13, the air vents 13 are located at the outermost edges of two sides of the sealing ring 10, and the purpose of the air vents 13 is to allow air to enter and exit in time; the number of ventilation openings 13 is 8 symmetrically arranged on one side as shown in the figure, but the number of ventilation openings is not limited to the application, and the protection scope of the application can be realized only if the purpose of timely ventilation can be achieved.
Next, the working principle of the present application is described, as shown in fig. 8, after the assembly, the inner wall of the cylinder barrel presses the arc-shaped sealing portion 11 of the sealing ring 10, and the arc-shaped sealing portion 11 is deformed inwards to achieve the sealing effect, that is, the interference Q between the sealing ring 10 and the cylinder barrel is reduced to the inner side by the whole extrusion of the inner wall of the cylinder barrel, and the sealing ring 10 and the bottom of the piston sealing ring groove do not contact. It is emphasized here that the pressure F of the sealing ring 10 against the cylinder is only generated by the material forming supporting force of the sealing ring 10 itself, so the pressure is small; in the case of right side ventilation, as shown in fig. 8, the piston moves leftward, and the seal ring 10 is left-leaning by the influence of the cylinder and the right side ventilation hole of the seal ring 10, and at this time, the gas presses the seal ring 10 leftward, and the two convex seal portions 12 located on the left side are bonded to the groove walls of the piston seal ring groove 20 to generate sealing, so that the gas does not flow, as shown at points a and B in the figure. Conversely, when the piston moves rightward, the two projecting seal portions 12 located on the right side are fitted to the groove walls of the piston seal groove 20 to produce a seal.
As shown in fig. 8, the seal ring is clamped between the C surface and the D surface and the inner hole surface of the cylinder barrel to form a floating seal during movement, so that the machining requirement on the piston of the piston seal ring groove 20 or the groove bottom E surface is low, and the requirement on concentricity is not too high. Because the interference magnitude Q of the sealing ring 10 is only influenced by the forming supporting force of the material of the sealing ring 10, the interference magnitude Q can be larger than that of the low-friction sealing ring in the prior art in design, and the cylinder barrel is more compensated after long-time action abrasion.
The design idea of the application is that the sealing ring is sealed with the side edge of the piston, and the groove bottom is provided with a relief space, and under the design:
1. the interference pressure of the sealing ring on the cylinder barrel is only influenced by the forming supporting force of the sealing ring (and the cylinder barrel can inwards form yielding when assembled), and if the interference pressure is F, the F value is far smaller than the internal stress generated when the sealing ring material in the prior art is compressed;
2. because the F value is smaller, more interference magnitude of the Q value can be provided in design, and when the sealing ring moves and wears for a long time, the sealing is compensated and ensured under the action of the forming supporting force of the sealing ring, so that the sealing ring has longer service life;
3. because the sealing ring is clamped between the C surface and the D surface and the inner hole surface of the cylinder barrel to form floating sealing, the concentricity deviation (such as 0.1-0.2 mm) exists in the machining of the bottom E surface of the piston, or the concentricity deviation between the piston and the cylinder barrel formed by the matching reason can cause the single-side interference magnitude of the sealing ring (bottom sealing) in the prior art, the single-side abrasion of the sealing ring (the concentricity of the bottom dimension of the sealing ring causes the concentricity of the external dimension of the sealing ring after the sealing ring is installed) can occur during the movement, but the sealing ring is not affected because of floating.
In summary, due to the adoption of the technical characteristics, compared with the prior art, the application has the following advantages and positive effects:
the pressure of the sealing ring to the cylinder barrel is only generated by the forming supporting force of the sealing ring, and the sealing ring does not have the sealing pressure to the bottom of the piston sealing ring groove, so the pressure is small;
secondly, the pressure of the sealing ring to the cylinder barrel is smaller, the designed interference pressure can be more, more abrasion compensation is realized, and the service life is longer;
thirdly, the piston seal ring groove is processed without concentricity requirement, and because of floating, the piston seal ring groove automatically and concentrically trends under the action of the inner hole of the cylinder barrel, and the quick response and the stability of the cylinder are improved.
The preferred embodiments of the application are provided only to help illustrate the application. The preferred embodiments are not exhaustive or to limit the application to the precise form disclosed. Obviously, many modifications and variations are possible in light of the above teaching. The embodiments were chosen and described in order to best explain the principles of the application and the practical application, to thereby enable others skilled in the art to best utilize the application. The application is limited only by the claims and the full scope and equivalents thereof. The foregoing description of the preferred embodiments of the present application is provided for illustration only, and is not intended to be limiting, since various changes and modifications may be made by those skilled in the art without departing from the spirit and scope of the application.
Claims (2)
1. A floating low friction seal ring cylinder comprising: the front cover, the back cover, the cylinder barrel, the piston rod and the piston are sequentially connected, the piston rod penetrates through the front cover, part of the piston rod is arranged in the cylinder barrel, the piston is arranged in the cylinder barrel and is connected with the piston rod, the novel piston engine is characterized by further comprising a sealing ring and a piston sealing ring groove, wherein,
the piston sealing ring groove is an annular groove body positioned on the piston, and the cross section of the piston sealing ring groove is Y-shaped;
the sealing ring comprises an arc-shaped sealing part and a vertical straight part, wherein the radial outer surface of the arc-shaped sealing part protrudes outwards to form a fan shape, the two sides of the fan shape of the arc-shaped sealing part are connected with one end part of the vertical straight part in an oblique line extending manner, and the vertical straight part comprises a plurality of protruding sealing parts protruding symmetrically in the axial direction;
the sealing ring is sleeved with the piston sealing ring groove, and the inner ring of the sealing ring does not contact the bottom of the piston sealing ring groove.
2. The floating low friction seal ring cylinder as in claim 1 wherein said seal ring further comprises a plurality of air ports, said air ports being located at the outermost edges of both sides of said seal ring.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811638562.3A CN109630499B (en) | 2018-12-29 | 2018-12-29 | Floating type low-friction sealing ring cylinder |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811638562.3A CN109630499B (en) | 2018-12-29 | 2018-12-29 | Floating type low-friction sealing ring cylinder |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN109630499A CN109630499A (en) | 2019-04-16 |
| CN109630499B true CN109630499B (en) | 2023-10-24 |
Family
ID=66054664
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201811638562.3A Active CN109630499B (en) | 2018-12-29 | 2018-12-29 | Floating type low-friction sealing ring cylinder |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN109630499B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110985586A (en) * | 2019-11-15 | 2020-04-10 | 宣城协盈汽车零部件科技有限公司 | Low-noise automobile shock-absorbing floating piston and manufacturing method thereof |
Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CH436885A (en) * | 1962-10-10 | 1967-05-31 | Courtenay Edenborough Yule | Air cylinder and method of making one |
| JPS5722461A (en) * | 1980-07-12 | 1982-02-05 | Tokyu Car Corp | Synthetic resin made piston ring for operating cylinder and using method thereof |
| CN1187870A (en) * | 1995-06-14 | 1998-07-15 | 苏舍-布尔克哈特机械制造有限公司 | Sealing ring |
| CN201810781U (en) * | 2010-09-02 | 2011-04-27 | 佛山市钜仕泰粉末冶金有限公司 | Self-adjusting gas-liquid sealing device |
| CN202229891U (en) * | 2011-07-12 | 2012-05-23 | 北京建科汇峰科技有限公司 | Pipe pressure test seal ring |
| CN202867407U (en) * | 2012-09-25 | 2013-04-10 | 浙江亿日气动科技有限公司 | Cylinder with Y-shaped sealing ring |
| CN203979261U (en) * | 2014-06-24 | 2014-12-03 | 烟台润蚨祥油封有限公司 | A kind of vibration damper sealing system |
| CN106286607A (en) * | 2015-05-29 | 2017-01-04 | Skf公司 | Bearing seal and application thereof |
| CN108916154A (en) * | 2018-07-24 | 2018-11-30 | 武汉科技大学 | A kind of self-adapting seal circle sealing fluid cylinder pressure |
-
2018
- 2018-12-29 CN CN201811638562.3A patent/CN109630499B/en active Active
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CH436885A (en) * | 1962-10-10 | 1967-05-31 | Courtenay Edenborough Yule | Air cylinder and method of making one |
| JPS5722461A (en) * | 1980-07-12 | 1982-02-05 | Tokyu Car Corp | Synthetic resin made piston ring for operating cylinder and using method thereof |
| CN1187870A (en) * | 1995-06-14 | 1998-07-15 | 苏舍-布尔克哈特机械制造有限公司 | Sealing ring |
| CN201810781U (en) * | 2010-09-02 | 2011-04-27 | 佛山市钜仕泰粉末冶金有限公司 | Self-adjusting gas-liquid sealing device |
| CN202229891U (en) * | 2011-07-12 | 2012-05-23 | 北京建科汇峰科技有限公司 | Pipe pressure test seal ring |
| CN202867407U (en) * | 2012-09-25 | 2013-04-10 | 浙江亿日气动科技有限公司 | Cylinder with Y-shaped sealing ring |
| CN203979261U (en) * | 2014-06-24 | 2014-12-03 | 烟台润蚨祥油封有限公司 | A kind of vibration damper sealing system |
| CN106286607A (en) * | 2015-05-29 | 2017-01-04 | Skf公司 | Bearing seal and application thereof |
| CN108916154A (en) * | 2018-07-24 | 2018-11-30 | 武汉科技大学 | A kind of self-adapting seal circle sealing fluid cylinder pressure |
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| Publication number | Publication date |
|---|---|
| CN109630499A (en) | 2019-04-16 |
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