CN111237466A - Double-ring lip-shaped sealing ring and fluid valve sealing structure - Google Patents
Double-ring lip-shaped sealing ring and fluid valve sealing structure Download PDFInfo
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- CN111237466A CN111237466A CN202010206103.9A CN202010206103A CN111237466A CN 111237466 A CN111237466 A CN 111237466A CN 202010206103 A CN202010206103 A CN 202010206103A CN 111237466 A CN111237466 A CN 111237466A
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- Prior art keywords
- lip
- ring
- double
- moving
- crankshaft
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
- F16J15/3204—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip
- F16J15/3232—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip having two or more lips
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
- F16J15/3204—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip
- F16J15/3224—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip capable of accommodating changes in distances or misalignment between the surfaces, e.g. able to compensate for defaults of eccentricity or angular deviations
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Sealing With Elastic Sealing Lips (AREA)
Abstract
The invention relates to a double-ring lip-shaped sealing ring, which comprises a first annular ring and a second annular ring, wherein the end part of the first annular ring forms an annular lip-shaped opening, the lip-shaped opening is defined to be composed of a movable lip and a static lip, one side of the second annular ring protrudes to form a protruding part, the protruding part is abutted against the surface of a moving part, when fluid flows into a compression capacity energy charging cavity in the lip-shaped opening and the moving part moves towards the opening direction of the lip-shaped opening in a reverse direction, the compression capacity energy charging cavity reversibly expands and deforms towards the radial direction of the compression capacity energy charging cavity, so that the movable lip is in close contact with the surface of the moving part to form sealing, when the moving part moves towards the opening direction of the lip-shaped opening, the protruding part of the second annular ring is in close contact with the surface of the moving part to form sealing, and when the moving part moves towards different directions relative to the static part, the protruding part is, therefore, different positions of the sealing ring bear friction generated in the movement process, and the working durability of the dynamic sealing structure is improved.
Description
Technical Field
The invention belongs to the technical field of fluid valve sealing structures, and particularly relates to a double-ring lip-shaped sealing ring and a fluid valve sealing structure.
Background
In one common reciprocating dynamic seal configuration, the moving and stationary members reciprocate in contact, creating a seal in the process. The fluid valve mainly used for vehicles has higher requirements on the durability and stability of the dynamic sealing structure on the fluid valve.
For example, a clutch actuator on a transmission needs to be frequently switched to meet the requirement of twelve-gear or even twenty-gear speed change, and naturally, the requirement on the durability of the working condition on the clutch actuator is relatively high. In the endurance test carried out by the QCT1010-2015 industrial standard, an actuator push rod carried by a load device completes one pushing action as one cycle, and the experiment requires that the device can carry out 675000 times of normal-temperature experiments, 225000 times of high-temperature experiments and 9000 times of low-temperature experiments according to the action, and the device can keep normal working characteristics in the whole experiment process, namely the device needs to keep working endurance times of more than 91 ten thousand times under various conditions.
Which affects the life of the clutch actuator of the fluid device described above, i.e., the durability of the dynamic seal arrangement described above. This friction (thermal fatigue) generated by the dynamic sealing movement of the crankshaft and the cup is severe for the wear of rubber parts such as the cup. An easily conceivable improvement method is to adopt a rubber material with strong high-temperature resistance to reduce the loss of the rubber part caused by thermal fatigue, obviously, the replacement of the material is not a fundamental method for solving the problem, and the service life of a clutch actuator directly influences the durability of the clutch configuration of the whole vehicle, so in recent years, along with technical innovation and industrial development, the requirement of the clutch actuator on the working durability times in the prior art is improved to more than 200 ten thousand, and the working durability times can only be realized by about 100 ten thousand according to the configuration formed by the existing power cylinder structure and the mature rubber part made of the high-temperature resistant material, so that the requirement of the prior art is difficult to meet simply by replacing the high-temperature resistant rubber material as the rubber part.
In view of the above, the prior art should be improved to solve the technical problem that the dynamic sealing structure of the fluid valve of the clutch actuator has insufficient working durability.
Disclosure of Invention
The invention aims to overcome the defects of the prior art and provide a sealing ring with a double-ring-lip structure, so that when a moving part moves towards different directions relative to a static part in actual working conditions, the moving part and different parts on the sealing ring are sealed after being tightly contacted, friction generated in the moving process of the moving part relative to the static part is borne at different positions of the sealing ring, and the working durability times of the sealing ring in a dynamic sealing structure are obviously improved.
In order to solve the above technical problems, the present invention provides a double-ring lip seal ring, which is disposed in a clutch, and is fixed to a moving member or a stationary member of a dynamic seal structure, wherein the seal ring includes a first annular ring and a second annular ring, the first annular ring has an end forming an annular lip opening, the lip opening is defined by a dynamic lip and a stationary lip, a contact surface of the second annular ring protrudes toward one side of the moving member to form a protrusion, the protrusion abuts against a surface of the moving member, a cavity formed in the lip opening is defined as a compression capacity charging cavity, and when a fluid flows into the compression capacity charging cavity and the moving member moves in a reverse direction with respect to the stationary member toward an opening direction of the lip opening, the compression capacity charging cavity is reversibly expanded and deformed in a radial direction thereof, so that the moving lip of the first annular ring is brought into close contact with the moving member surface and forms a seal, and when the moving member moves relative to the stationary member in the opening direction of the lip-shaped opening, the protrusion of the second annular ring is brought into close contact with the moving member surface and forms a seal.
Preferably, the first annular ring and the second annular ring each include a fitting surface facing the stationary surface and in surface contact therewith, and a contact surface facing the surface of the moving member, the fitting surface being formed on the outer wall of the stationary lip on the first annular ring, the contact surface being formed on the outer wall of the moving lip, and the protruding portion being located on the outer wall on the same side as the moving lip of the first annular ring on the second annular ring.
Further preferably, when the double-ring lip seal ring is disposed on the hole sealing wall, the lip portion inside the lip opening is a moving lip, the lip portion outside the lip opening is a static lip, and the protrusion portion extends inward of the seal ring on the second annular ring; when the double-ring lip-shaped sealing ring is arranged on the shaft sealing wall, the lip part on the outer side of the lip opening is a moving lip, the lip part on the inner side of the lip opening is a static lip, and the protruding part extends to the outer side of the sealing ring on the second annular ring.
Still further preferably, when the moving lip is in close contact with the moving member surface and forms a seal, a frictional force between the moving lip and the moving member is larger than a frictional force between the protruding portion and the moving member; when the protrusion is in close contact with the moving member surface and forms a seal, the frictional force between the moving lip and the moving member is smaller than the frictional force between the protrusion and the moving member.
Correspondingly, the invention also provides a fluid valve sealing structure based on the double-ring lip-shaped sealing ring, which comprises a cylinder body and a crankshaft reciprocating in the cylinder body, wherein a gap is formed between the crankshaft and the inner wall of the cylinder body, a table-shaped flange is formed in the cylinder body, a blocking sleeve is fixedly arranged on the inner wall of the cylinder body below the flange, a first accommodating cavity is formed between the end part of the blocking sleeve and the flange, a first double-ring lip-shaped sealing ring is arranged in the first accommodating cavity, the assembly surfaces of the first annular ring and the second annular ring are attached to the inner wall of the cylinder body on the first double-ring lip-shaped sealing ring, the movable lip of the first annular ring and the protruding part of the second annular ring are in contact with the outer side surface of the crankshaft, the opening direction of the first double-ring lip-shaped sealing ring is defined to be vertical upwards, and then when fluid is introduced into the cylinder body, the fluid flows into a compression energy charging cavity on the first annular ring through a gap between the machine shaft and the inner wall of the cylinder body, the compression energy charging cavity radially deforms towards one side of the machine shaft, so that a moving lip of the first annular ring is in close contact with the surface of the machine shaft to form a seal, and meanwhile, the fluid drives the machine shaft to move downwards, and friction is generated between the outer wall of the moving lip and the outer surface of the machine shaft; the protrusion rubs between the outer surface of the crankshaft when the crankshaft moves in an upward direction.
Preferably, the inner wall of the blocking sleeve is recessed to form a second receiving cavity, and a second double-ring lip seal ring is arranged in the second receiving cavity, wherein the opening direction of the lip-shaped opening on the second double-ring lip seal ring is opposite to the opening direction of the lip-shaped opening on the first double-ring lip seal ring, and wherein the opening direction of the lip-shaped opening on the second double-ring lip seal ring is opposite to the opening direction of the lip-shaped opening on the first double-ring lip seal ring, then when fluid is introduced into the cylinder, the fluid flows into the first ring of the first double-ring lip seal ring through the gap between the machine shaft and the inner wall of the cylinder, the compression amount can be charged into the cavity, and the moving lip of the first double-ring lip seal ring is in close contact with the surface of the machine shaft to form a seal, and simultaneously, the fluid flows between the protrusion of the second double-ring lip seal ring and the surface of the machine shaft to make the protrusion in close contact, the fluid drives the machine shaft to move downwards, and friction is generated between a moving lip of the first double-ring lip-shaped sealing ring and the outer surface of the machine shaft at the moment, and friction is generated between a protruding part of the second double-ring lip-shaped sealing ring and the outer surface of the machine shaft; when the shaft moves upwards, friction is generated by close contact between the moving lip of the second double-ring lip-shaped sealing ring and the outer surface of the shaft, and friction is generated by close contact between the protruding part of the first double-ring lip-shaped sealing ring and the outer surface of the shaft.
Compared with the prior art, the invention has the following beneficial technical effects due to the adoption of the technical scheme:
1. the double-ring lip-shaped sealing ring comprises a first annular ring and a second annular ring, wherein a lip-shaped opening on the first annular ring is composed of a movable lip and a static lip, the side surface of the static lip is used as an assembly surface to be attached and contacted with a static part, the side surface of the movable lip is used as a contact surface to be contacted with a moving part under a non-pressure-bearing state, a protruding part extending towards one side of the moving part is formed on the second annular ring, under non-pressure-bearing loading, the protruding part is contacted with the surface of the moving part, when fluid flows into a compression quantity energy charging cavity formed by the lip-shaped opening, the compression quantity energy charging cavity generates expansion deformation towards the radial direction, meanwhile, the fluid pushes the moving part to move towards the lip-shaped opening, and the realization is that when the moving part and the lip-shaped opening move in the same direction, the movable lip is tightly contacted with the moving part to realize sealing, and when the protruding part, when the moving part moves relative to the static part towards different directions, different parts of the sealing ring are in close contact with the moving part to realize sealing, so that different positions of the sealing ring bear friction generated in the moving process of the moving part relative to the static part, and the working durability times of the sealing ring in the dynamic sealing structure are obviously improved;
2. because the movable lip and the protruding part respectively bear the friction generated in the process that the movable part moves relative to the static part, namely, any one of the two structures bears half of the friction borne by the lower sealing ring of the existing structure, the existing configuration formed by a rated-motion sealing structure such as a clutch actuator and the like and a mature rubber material can also meet the requirement that the working durability times of the power cylinder reach 200 ten thousand times;
3. during actual assembly, for example, in a cylinder body of a clutch actuator, a blocking sleeve is arranged, a first accommodating cavity is formed between one end of the blocking sleeve and the inner wall of the cylinder body, the surface of the blocking sleeve is recessed to form a second accommodating cavity, a first double-ring lip-shaped sealing ring and a second double-ring lip-shaped sealing ring are respectively arranged in the first accommodating cavity and the second accommodating cavity, and the lip opening directions of the first double-ring lip-shaped sealing ring and the second double-ring lip-shaped sealing ring are opposite, so that when a crankshaft in the cylinder body moves in a direction opposite to the lip opening direction of the first double-ring lip-shaped sealing ring, friction is generated between a moving lip of the first double-ring lip-shaped sealing ring and the outer surface of the crankshaft, and friction is generated between a protruding part of the second double-; when the crankshaft in the cylinder body moves in the same direction as the lip-shaped opening of the first double-ring lip-shaped sealing ring, the moving lip of the second double-ring lip-shaped sealing ring is in close contact with the outer surface of the crankshaft to generate friction, and the protruding part of the first double-ring lip-shaped sealing ring is in close contact with the outer surface of the crankshaft to generate friction; thereby forming the hierarchical friction of multichannel sealing washer, further reducing the frictional force that bears under the pressure-bearing state of every sealing washer, extension sealing washer's life-span then.
4. On each double-ring lip-shaped sealing ring, because the first annular ring and the second annular ring are arranged, and the movable lip on the first annular ring and the protruding part on the second annular ring can respectively realize the sealing with the moving part, therefore, after the movable lip or the protruding part on each double-ring lip-shaped sealing ring is damaged by thermal fatigue, the sealing effect of the sealing lip ring at the rest part can still be realized.
Drawings
Fig. 1 is a schematic view illustrating a structure of the double-ring lip seal according to a first embodiment of the present invention;
fig. 2 is a schematic sectional view showing a sectional structure of the double-ring lip seal shown in fig. 1;
FIG. 3 is a cross-sectional view of a fluid valve seal configuration utilizing the dual ring lip seal of FIG. 1 in accordance with a preferred embodiment of the present invention;
fig. 4 is a partially enlarged view illustrating a state in which a moving member moves in a reverse direction in accordance with a lip opening direction of a double-ring lip seal in the fluid valve sealing structure shown in fig. 3;
fig. 5 is a partially enlarged view illustrating a state in which the moving member moves in the same direction as the lip opening direction of the double-ring lip seal in the fluid valve sealing structure shown in fig. 3;
FIG. 6 is an enlarged fragmentary view of a fluid valve seal structure incorporating two double-ring lip seals in accordance with another preferred embodiment of the present invention;
fig. 7 is a schematic view showing the structure of a double-ring lip seal ring according to a second embodiment of the present invention;
fig. 8 is a schematic sectional view showing a sectional structure of the double-ring lip seal shown in fig. 6;
fig. 9 is a partially enlarged view illustrating a state in which a moving member moves in the opposite direction to the lip opening direction of the double-ring lip seal in the fluid valve sealing structure using the further preferred embodiment of the double-ring lip seal shown in fig. 7;
fig. 10 is a partially enlarged view illustrating a state in which the moving members move in the same direction as the lip opening direction of the double-ring lip seal in the fluid valve sealing structure using the further preferred embodiment of the double-ring lip seal shown in fig. 7;
wherein: 1. an assembly surface; 2. a contact surface; 3. a lip-shaped opening; 10. a first annular ring; 20. a second annular ring; 21. a protrusion; 31. moving the lips; 32. a static lip; 40. a cylinder body; 41. a flange; 42. a blocking sleeve; 43. a second receiving cavity; 44. a first double-ring lip-shaped sealing ring; 45. a second double-ring lip-shaped sealing ring; 50. the crankshaft.
Detailed Description
Embodiments of a double-ring lip seal and a fluid valve seal structure according to the present invention will be described below with reference to the accompanying drawings. Those of ordinary skill in the art will recognize that the described embodiments can be modified in various different ways, without departing from the spirit and scope of the present invention. Accordingly, the drawings and description are illustrative in nature and not intended to limit the scope of the claims. Furthermore, in the present description, the drawings are not to scale and like reference numerals refer to like parts.
It should be noted that, in the embodiments of the present invention, the expressions "first" and "second" are used to distinguish two entities with the same name but different names or different parameters, and it is understood that "first" and "second" are merely for convenience of description and should not be construed as limitations of the embodiments of the present invention, and the descriptions thereof in the following embodiments are omitted.
In the preferred embodiment of the invention, the double-ring lip-shaped sealing ring is a sealing element under the dynamic sealing working condition of relative movement between a moving element and a static element, such as a clutch actuator, and fluid flows into a compression energy-charging cavity formed at a lip-shaped opening on the double-ring lip-shaped sealing ring and generates reversible expansion deformation to realize the dynamic sealing structure between the moving element and the static element, and the double-ring lip-shaped sealing ring generates friction with the surface of the moving element in the process of the moving element.
Example one
Fig. 1 is a schematic view illustrating a structure of the double-ring lip seal according to the first embodiment of the present invention. Fig. 2 is a schematic sectional view showing a sectional structure of the double-ring lip seal shown in fig. 1. Referring to fig. 1, in the first embodiment of the present invention, the double-ring lip-shaped seal ring is made of rubber material by a conventional process, and includes two annular rings integrally formed, including a mounting surface 1 facing the stationary surface and contacting with the surface thereof, and a contact surface 2 facing the surface of the moving member, and the top portion includes an annular lip-shaped opening 3. Referring to fig. 1 and 2, the two annular rings are respectively defined as a first annular ring 10 and a second annular ring 20 in a top-down direction, the lip opening 3 is formed on the first annular ring 10, the two lips constituting the lip opening 3 are respectively a moving lip 31 and a static lip 32, the mounting surface 1 is a side surface of the static lip 32 away from the moving lip 31, and the contact surface 2 is a side surface of the moving lip 31 away from the static lip 32. In the unpressurized state, the movable lip 31 may be disposed close to the surface of the moving member, or may be disposed in non-close contact with the surface of the moving member. The contact surface on the second annular ring 20 projects to one side and forms a projection 21, which projection 21 should likewise, in the unpressurized state, abut against the surface of the moving element.
The cavity in the lip-shaped opening 3 is defined as a compression energy charging cavity, that is, when fluid flows to the compression energy charging cavity, the compression energy charging cavity generates reversible expansion deformation in the radial direction of the moving member, so that the moving lip 31 of the first annular ring 10 is in a pressure-bearing state due to the extrusion of the fluid, and in this state, the moving lip 31 approaches in the direction of the moving member until the surface of the moving lip is in close contact with the surface of the moving member to realize sealing.
During the continuous downward movement of the moving member, the moving lip 31 is always in close contact with the surface of the moving member to generate friction. At this time, since the protrusion 21 on the second annular ring 20 is in an unpressurized state, the friction force between the moving lip 31 and the surface of the moving element is greater than the friction force between the protrusion 21 and the moving element, that is, the friction force between the moving element and the double-ring lip seal ring during the continuous downward movement of the moving element is concentrated at the contact position of the moving lip 31 and the moving element. In the same cycle, when the moving element is changed from continuous downward movement to continuous upward movement, the second annular ring 20 is changed to a pressure-bearing state to be in close contact with the surface of the moving element and realize sealing, and at the moment, the friction force between the moving lip 31 and the moving element is smaller than that between the protruding part 21 and the moving element, namely, the friction force between the moving element and the double-ring lip seal ring during the continuous upward movement of the moving element is concentrated at the contact position of the protruding part 21 and the moving element.
This process is described in detail with reference to the accompanying drawings, and fig. 3 is a sectional view showing a sectional structure of a fluid valve sealing structure using the double-ring lip seal shown in fig. 1 in a preferred embodiment of the present invention. The fluid valve sealing structure includes a cylinder block 40 and a crankshaft 50 reciprocating in the cylinder block 40, and as shown in fig. 3, a gap is formed between the crankshaft 50 and an inner wall of the cylinder block 40, and fluid flows even in the gap. A stepped flange 41 is formed in the cylinder 40 so that a blocking sleeve 42 can be fitted over the inner wall of the cylinder below the flange 41, and a first receiving chamber (not shown) is formed between the end of the blocking sleeve 42 and the flange 41, into which a double ring lip seal according to the present invention is fitted, and in a non-pressurized state, a fitting surface of the double ring lip seal is in contact with the inner wall of the cylinder 40, and the movable lip 31 and the protrusion 21 are in contact with the outer surface of the crankshaft 50.
Fig. 4 is a partially enlarged view illustrating a state in which a moving member moves in a reverse direction in accordance with a lip opening direction of a double-ring lip seal in the fluid valve sealing structure shown in fig. 3; fig. 5 is a partially enlarged view illustrating a state in which the moving member moves in the same direction as the lip opening direction of the double-ring lip seal in the fluid valve sealing structure shown in fig. 3; the direction of the arrows in fig. 4 and 5 show the direction of movement of the moving element (i.e. the crankshaft) in the respective operating condition. Referring to fig. 4, if the opening direction of the double-ring lip seal in fig. 4 is defined as vertical upward, when fluid is introduced into the cylinder 40, the fluid flows into the compression energy charging cavity of the double-ring lip seal through the gap between the crankshaft 50 and the inner wall of the cylinder 40, and the compression energy charging cavity, i.e. the lip opening, is reversibly expanded and deformed radially toward one side of the crankshaft 50 under the filling of the fluid, so that the moving lip of the first annular ring is in close contact with the surface of the crankshaft 50 to form a seal, and at this time, the moving lip 31 is in a pressure-bearing state; at the same time, the fluid-driven machine shaft 50 continues to move downward, and the close contact between the outer wall of the moving lip 31 and the outer surface of the machine shaft 50 continues to generate friction. Referring again to fig. 5, in the next working condition of the same cycle, when the crankshaft 50 is continuously moved upwards from the downward movement, the moving lip 31 is no longer pressurized and returns to the deformation, i.e. is rotated to the unpressurized loose state, the fluid flows between the moving lip 31 and the crankshaft 50 to the space between the protruding part 21 of the second annular ring and the crankshaft 50, and the protruding part 21 is in close contact with the crankshaft 50 and forms a seal, when the protruding part 21 is in the pressurized state, and then, the fluid drives the crankshaft 50 to continuously move upwards, and the close contact between the outer wall of the protruding part 21 and the outer surface of the crankshaft 50 continuously generates friction.
As a preferable aspect of the present invention, two double-ring lip seals may be further provided in the fluid valve seal structure as described above. Fig. 6 is a partially enlarged view showing a fluid valve sealing structure provided with two double-ring lip seals according to another preferred embodiment of the present invention. As shown in the figure, besides the first receiving cavity formed between the blocking sleeve 42 and the inner wall of the cylinder 40, a double-ring lip seal ring may be disposed in the second receiving cavity 43 formed by the inner wall of the blocking sleeve 42 being recessed, and the two seal rings are respectively defined as a first double-ring lip seal ring 44 and a second double-ring lip seal ring 45 according to the top-down direction, and referring to fig. 6, the lip opening direction of the second double-ring lip seal ring 45 is opposite to the lip opening direction of the first double-ring lip seal ring.
When fluid is introduced into the cylinder block 40, the fluid flows into the energy charging chamber through the gap between the crankshaft 50 and the inner wall of the cylinder block 40 by the compression amount on the first annular ring of the first double-annular lip-shaped sealing ring 44 and causes the moving lip 31 of the first double-annular lip-shaped sealing ring 44 to be in close contact with the surface of the crankshaft 50 to form a seal, and simultaneously flows between the protrusion 21 of the second double-annular lip-shaped sealing ring 45 and the surface of the crankshaft 50 to cause the protrusion 21 to be in close contact with the surface of the crankshaft 50 to form a seal, and then the fluid drives the crankshaft 50 to move downwards, at this time, friction is generated between the moving lip 31 of the first double-annular lip-shaped sealing ring 44 and the outer surface of the crankshaft 50, and friction is generated between the protrusion 21 of the second double-; in the next working condition, when the machine shaft 50 moves upwards, the moving lip 31 of the second double-ring lip-shaped sealing ring 45 is in close contact with the outer surface of the machine shaft 50 to generate friction, and the protruding part 21 of the first double-ring lip-shaped sealing ring 44 is in close contact with the outer surface of the machine shaft 50 to generate friction. Two or even multi-stage sealing rings are arranged, so that the graded friction of a plurality of sealing rings is formed, the friction force borne by each sealing ring in a pressure bearing state is further reduced, and the service life of the sealing rings is prolonged.
Example two
The double-ring lip seal of the first embodiment is applied to the bore seal wall, while the second embodiment is an embodiment applied to the shaft seal wall as a parallel aspect of the present invention.
Fig. 6 is a partially enlarged view showing a fluid valve sealing structure provided with two double-ring lip seals according to another preferred embodiment of the present invention. Fig. 7 is a schematic view showing the structure of the double-ring lip seal according to the second embodiment of the present invention. The difference from the first embodiment is that the mounting surface 1 and the contact surface 2 on the first annular ring 10 and the second annular ring 20 are changed correspondingly because the relative positions of the moving member and the stationary member are changed in the case of shaft sealing. As shown in fig. 6, in the second embodiment, the lip portion of the first annular ring 10 located outside the lip-shaped opening 3 is the moving lip 31, and the lip portion located inside the lip-shaped opening 3 is the static lip 32, and accordingly, the protrusion 21 of the second annular ring 20 extends outward of the seal ring. Fig. 9 is a partially enlarged view illustrating a state in which a moving member moves in the opposite direction to the lip opening direction of the double-ring lip seal in the fluid valve sealing structure using the further preferred embodiment of the double-ring lip seal shown in fig. 7; fig. 10 is a partially enlarged view illustrating a state in which the moving members move in the same direction as the lip opening direction of the double-ring lip seal in the fluid valve sealing structure using the further preferred embodiment of the double-ring lip seal shown in fig. 7; the direction of the arrows in fig. 9 and 10 show the direction of movement of the moving element (i.e. the crankshaft) in the respective operating conditions. Referring to fig. 9, if the opening direction of the double-ring lip seal in fig. 9 is defined as vertical upward, when fluid is introduced into the cylinder 40, the fluid flows into the compression energy charging cavity of the double-ring lip seal through the gap between the crankshaft 50 and the inner wall of the cylinder 40, and the compression energy charging cavity, i.e., the lip opening, is reversibly expanded and deformed radially toward one side of the crankshaft 50 under the filling of the fluid, so that the moving lip 31 of the first annular ring is in close contact with the surface of the crankshaft 50 and forms a seal, and at this time, the moving lip 31 is in a pressure-bearing state; at the same time, the fluid-driven machine shaft 50 continues to move downward, and the close contact between the outer wall of the moving lip 31 and the outer surface of the machine shaft 50 continues to generate friction. Referring again to fig. 10, in the next operating condition of the same cycle, the crankshaft 50 is turned from downward movement to upward continuous movement, and then the moving lip 31 is no longer pressurized and turned into an unpressurized loose state, and the fluid flows from between the moving lip 31 and the crankshaft 50 to between the protruding part 21 of the second annular ring and the crankshaft 50, and makes the protruding part 21 and the crankshaft 50 tightly contact and form a seal, and at this time, the protruding part 21 is in a pressurized state, and then, the fluid drives the crankshaft 50 to upward continuous movement, and then, the tight contact between the outer wall of the protruding part 21 and the outer surface of the crankshaft 50 continuously generates friction.
Of course, in this embodiment, two or more stages of sealing rings may be adopted as shown in fig. 6, and the working principle and the process are similar, so that the detailed description is omitted here.
Compared with the prior art, the invention has the following beneficial technical effects due to the adoption of the technical scheme:
1. the double-ring lip-shaped sealing ring comprises a first annular ring and a second annular ring, wherein a lip-shaped opening on the first annular ring is composed of a movable lip and a static lip, the side surface of the static lip is used as an assembly surface to be attached and contacted with a static part, the side surface of the movable lip is used as a contact surface to be contacted with a moving part under a non-pressure-bearing state, a protruding part extending towards one side of the moving part is formed on the second annular ring, under non-pressure-bearing loading, the protruding part is contacted with the surface of the moving part, when fluid flows into a compression quantity energy charging cavity formed by the lip-shaped opening, the compression quantity energy charging cavity generates expansion deformation towards the radial direction, meanwhile, the fluid pushes the moving part to move towards the lip-shaped opening, and the realization is that when the moving part and the lip-shaped opening move in the same direction, the movable lip is tightly contacted with the moving part to realize sealing, and when the protruding part, when the moving part moves relative to the static part towards different directions, different parts of the sealing ring are in close contact with the moving part to realize sealing, so that different positions of the sealing ring bear friction generated in the moving process of the moving part relative to the static part, and the working durability times of the sealing ring in the dynamic sealing structure are obviously improved;
2. because the movable lip and the protruding part respectively bear the friction generated in the process that the movable part moves relative to the static part, namely, any one of the two structures bears half of the friction borne by the lower sealing ring of the existing structure, the existing configuration formed by a rated-motion sealing structure such as a clutch actuator and the like and a mature rubber material can also meet the requirement that the working durability times of the power cylinder reach 200 ten thousand times;
3. during actual assembly, for example, in a cylinder body of a clutch actuator, a blocking sleeve is arranged, a first accommodating cavity is formed between one end of the blocking sleeve and the inner wall of the cylinder body, the surface of the blocking sleeve is recessed to form a second accommodating cavity, a first double-ring lip-shaped sealing ring and a second double-ring lip-shaped sealing ring are respectively arranged in the first accommodating cavity and the second accommodating cavity, and the lip opening directions of the first double-ring lip-shaped sealing ring and the second double-ring lip-shaped sealing ring are opposite, so that when a crankshaft in the cylinder body moves in a direction opposite to the lip opening direction of the first double-ring lip-shaped sealing ring, friction is generated between a moving lip of the first double-ring lip-shaped sealing ring and the outer surface of the crankshaft, and friction is generated between a protruding part of the second double-; when the crankshaft in the cylinder body moves in the same direction as the lip-shaped opening of the first double-ring lip-shaped sealing ring, the moving lip of the second double-ring lip-shaped sealing ring is in close contact with the outer surface of the crankshaft to generate friction, and the protruding part of the first double-ring lip-shaped sealing ring is in close contact with the outer surface of the crankshaft to generate friction; thereby forming the hierarchical friction of multichannel sealing washer, further reducing the frictional force that bears under the pressure-bearing state of every sealing washer, extension sealing washer's life-span then.
4. On each double-ring lip-shaped sealing ring, because the first annular ring and the second annular ring are arranged, and the movable lip on the first annular ring and the protruding part on the second annular ring can respectively realize the sealing with the moving part, therefore, after the movable lip or the protruding part on each double-ring lip-shaped sealing ring is damaged by thermal fatigue, the sealing effect of the sealing lip ring at the rest part can still be realized.
The present invention has been described in detail, and the embodiments are only used for understanding the method and the core idea of the present invention, and the purpose of the present invention is to enable those skilled in the art to understand the content of the present invention and to implement the present invention, and not to limit the protection scope of the present invention. All equivalent changes and modifications made according to the spirit of the present invention should be covered within the protection scope of the present invention.
Claims (6)
1. A double-ring lip-shaped sealing ring is characterized in that the sealing ring is fixed with a moving part or a static part of a dynamic sealing structure, the sealing ring comprises a first annular ring and a second annular ring which are integrally formed, the end part of the first annular ring forms an annular lip-shaped opening, the lip-shaped opening is defined to be composed of a dynamic lip and a static lip, the contact surface of the second annular ring protrudes towards one side of the moving part and forms a protruding part, and the protruding part is abutted against the surface of the moving part, wherein,
the cavity that the definition lip opening formed is the compression volume and can fill the chamber, then when fluid flows to in the compression volume can the intracavity, and the moving member is relative the stationary member is towards when the opening direction reverse motion of lip opening, the compression volume can fill the chamber and produce reversible expansion deformation to its radial direction, so that the moving lip of first annular ring with moving member surface in close contact with and form the seal, when the moving member is relative the stationary member is towards when the opening direction of lip opening moves, the protruding portion of second annular ring with moving member surface in close contact with and form the seal.
2. The double-ring lip seal according to claim 1, wherein the first and second annular rings each include a fitting surface facing the stationary surface and in surface contact therewith, and a contact surface facing the moving member surface, the fitting surface being formed on an outer wall of the stationary lip and the contact surface being formed on an outer wall of the moving lip, respectively, wherein,
on the second annular ring, the protruding part is located on the outer wall of the first annular ring on the same side as the moving lip.
3. The double-ring lip seal of claim 2, wherein when the double-ring lip seal is disposed on the bore seal wall, the lip opening inside lip portion is a moving lip, the lip opening outside lip portion is a static lip, and the second annular ring has the protrusion extending inwardly of the seal ring;
when the double-ring lip-shaped sealing ring is arranged on the shaft sealing wall, the lip part on the outer side of the lip opening is a moving lip, the lip part on the inner side of the lip opening is a static lip, and the protruding part extends to the outer side of the sealing ring on the second annular ring.
4. The double ring lip seal according to any one of claims 1 to 3,
when the moving lip is in close contact with the surface of the moving part and forms a seal, the friction force between the moving lip and the moving part is larger than the friction force between the protruding part and the moving part;
when the protrusion is in close contact with the moving member surface and forms a seal, the frictional force between the moving lip and the moving member is smaller than the frictional force between the protrusion and the moving member.
5. A fluid valve sealing structure based on the double-ring lip-shaped sealing ring of claims 1-4, which comprises a cylinder body and a crankshaft reciprocating in the cylinder body, wherein a gap is formed between the crankshaft and the inner wall of the cylinder body, a table-shaped flange is formed in the cylinder body, a blocking sleeve is fixedly arranged on the inner wall of the cylinder body below the flange, a first containing cavity is formed between the end part of the blocking sleeve and the flange, a first double-ring lip-shaped sealing ring is arranged in the first containing cavity, wherein,
the assembling surfaces of the first annular ring and the second annular ring are attached to the inner wall of the cylinder body, the movable lip of the first annular ring and the protruding part of the second annular ring are in contact with the outer side surface of the crankshaft, the opening of the first double-ring lip-shaped sealing ring faces vertically upwards, and then,
when fluid is introduced into a cylinder, the fluid flows into a compression energy charging cavity on the first annular ring through a gap between the crankshaft and the inner wall of the cylinder, the compression energy charging cavity radially deforms towards one side of the crankshaft, so that a moving lip of the first annular ring is in close contact with the surface of the crankshaft to form a seal, and meanwhile, the fluid drives the crankshaft to move downwards, and at the moment, the outer wall of the moving lip is in close contact with the outer surface of the crankshaft to generate friction; the protrusions are in close contact with an outer surface of the crankshaft to generate friction when the crankshaft moves in an upward direction.
6. A fluid valve seal arrangement according to claim 5, wherein the inner wall of said dam sleeve is recessed to form a second receiving cavity within which a second double annular lip seal is disposed, wherein,
the opening direction of the lip-shaped opening on the second double-ring lip-shaped sealing ring is opposite to the opening direction of the lip-shaped opening on the first double-ring lip-shaped sealing ring,
when fluid is introduced into a cylinder, the fluid flows into a compression energy charging cavity on a first annular ring of a first double-ring lip-shaped sealing ring through a gap between a crankshaft and the inner wall of the cylinder and flows between a protruding part of a second double-ring lip-shaped sealing ring and the surface of the crankshaft to enable the protruding part to be in close contact with the surface of the crankshaft to form a seal while a moving lip of the first double-ring lip-shaped sealing ring is in close contact with the surface of the crankshaft, the fluid drives the crankshaft to move downwards, and friction is generated between the moving lip of the first double-ring lip-shaped sealing ring and the outer surface of the crankshaft and between the protruding part of the second double-ring lip-shaped sealing ring and the outer surface of the crankshaft;
when the shaft moves upwards, friction is generated by close contact between the moving lip of the second double-ring lip-shaped sealing ring and the outer surface of the shaft, and friction is generated by close contact between the protruding part of the first double-ring lip-shaped sealing ring and the outer surface of the shaft.
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| Application Number | Priority Date | Filing Date | Title |
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| CN202010206103.9A CN111237466A (en) | 2020-03-23 | 2020-03-23 | Double-ring lip-shaped sealing ring and fluid valve sealing structure |
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| CN202010206103.9A CN111237466A (en) | 2020-03-23 | 2020-03-23 | Double-ring lip-shaped sealing ring and fluid valve sealing structure |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2022095071A1 (en) * | 2020-11-09 | 2022-05-12 | 深圳市大疆创新科技有限公司 | Plunger pump, plant-protection unmanned aerial vehicle, and spray device |
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2020
- 2020-03-23 CN CN202010206103.9A patent/CN111237466A/en active Pending
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2022095071A1 (en) * | 2020-11-09 | 2022-05-12 | 深圳市大疆创新科技有限公司 | Plunger pump, plant-protection unmanned aerial vehicle, and spray device |
| CN114746649A (en) * | 2020-11-09 | 2022-07-12 | 深圳市大疆创新科技有限公司 | Plunger pump, plant protection unmanned aerial vehicle and spraying apparatus |
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