Piston ring
By setting a double-barrel structure and applying a lubricating coating on the outer ring of the piston ring, the problem of poor lubrication effect of the piston ring under high temperature and high pressure is solved, the formation of oil wedges is achieved, the risk of wear and cylinder pulling is reduced, and the reliability and service life of the piston ring is improved.
Patent Information
- Application Number
- CN202422680963.2
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2024-11-05
- Publication Date
- 2025-08-26
- Estimated Expiration
- 2034-11-05
AI Technical Summary
The existing piston rings are prone to deform under high temperature and high pressure, making it difficult to form oil wedges on the rig, resulting in poor lubrication effect, abnormal wear and cylinder failure, affecting engine reliability and safety.
A double-barrel structure is provided on the outer ring of the piston ring. By setting the first arc surface and the second arc surface at the hook to form an inward concave intersection line, it ensures that an oil wedge can be formed during the upward and downward processes, and a lubricating or wear-resistant coating is applied to reduce wear.
Effectively form oil film protection, improve lubrication effect, reduce abnormal wear and cylinder pulling risks, and improve the reliability and service life of the piston ring.
Smart Images
Figure CN223270068U_ABST
Abstract
Description
Technical Field
[0001] The utility model relates to the field of internal combustion engine parts, in particular to a piston ring. Background Art
[0002] Piston rings are primarily used in internal combustion engines such as gasoline and diesel engines, and construction machinery. These metal rings, with an opening, fit into the piston groove. When operating, they appear circular, but in their free state, they assume an elliptical shape. They are primarily classified into two types based on their intended use: compression rings, which seal the combustible mixture within the combustion chamber, and oil rings, which remove excess oil from the cylinder.
[0003] As engines demand increasingly stringent sealing performance, overlapping piston rings are increasingly common. However, because the cross-sectional profile of the working surface (i.e., the outer ring) of existing piston rings is typically a symmetrical barrel surface or a single barrel surface with an offset barrel surface, deformation caused by high temperature and high pressure can easily prevent the upper or lower overlap of the piston ring from forming an oil wedge during the downward or upward movement. This results in poor lubrication and even dry friction, leading to abnormal wear and cylinder scuffing, seriously affecting engine reliability, causing significant economic losses, and even posing significant safety risks to operating equipment. Utility Model Content
[0004] The purpose of the utility model is to propose a piston ring in response to the shortcomings of the existing technology, optimize the outer ring structure of the existing piston ring, and provide arc-shaped barrel surfaces above and below the overlap to form a double-barrel surface structure, so that an oil wedge can be effectively formed at the overlap during the upward and downward processes of the piston ring, generating oil film protection, thereby greatly improving the lubrication effect at this position, reducing the risk of abnormal wear and cylinder scuffing, and improving the reliability and service life of the piston ring.
[0005] The technical solution to achieve the purpose of this utility model is:
[0006] A piston ring comprises a piston ring body having an overlap, wherein the outer circular cross-section of the piston ring body is provided with a first arc surface and a second arc surface arranged in a continuous manner along the axial direction, and the intersection line of the first arc surface and the second arc surface is recessed inward to form a double barrel surface structure, the axial distance between the intersection line and the top surface of the piston ring body is k, the axial fitting clearance of the overlap is δ, and the axial distance between the upper fitting surface of the outer ring of the overlap and the top surface of the piston ring body is h3, and h3≤k≤h3+δ is satisfied.
[0007] Furthermore, an intersection line between the first arc surface and the second arc surface is located at an upper portion of the piston ring body.
[0008] Furthermore, the first arc surface and the second arc surface are both smooth arc surfaces.
[0009] Furthermore, the upper end of the first arc surface, the lower end of the first arc surface, and the intersection line between the first arc surface and the second arc surface are located on the same outer circular surface.
[0010] Furthermore, the center of the first arc surface is aligned with the center of the second arc surface along the axial direction.
[0011] Furthermore, the distance between the center of the first arc surface and the top surface of the piston ring is h1, and satisfies h1=(1 / 4-3 / 4)h3.
[0012] Furthermore, the distance between the center of the second arc surface and the bottom surface of the piston ring is h2, and satisfies h2=(1 / 4~3 / 4)(h-h3), where h is the axial thickness of the piston ring.
[0013] Furthermore, the distance between the convex point of the first arc surface and the inner circle of the piston ring body is smaller than the distance between the convex point of the second arc surface and the inner circle of the piston ring body.
[0014] Furthermore, a radial distance between the convex points of the first arc surface and the convex points of the second arc surface is e, and satisfies e≤0.1 mm.
[0015] Furthermore, the outer circle of the piston ring body is coated with a lubricating coating or a wear-resistant coating.
[0016] Furthermore, the overlap is formed by matching upper and lower mating surfaces, the upper or lower mating surface is a first plane or a special-shaped surface, the first plane extends horizontally to the inner ring of the piston ring body or extends obliquely downward to the inner ring or bottom surface of the piston ring body, the special-shaped surface is composed of a second plane and a third plane that are perpendicular to each other and have arc transitions, and the third plane extends to the bottom surface of the piston ring.
[0017] By adopting the above technical solution, the utility model has the following beneficial effects:
[0018] (1) The utility model uses the overlap as the dividing line, and sets a first arc surface and a second arc surface on the outer cylindrical working surface of the piston ring body, forming a double-barrel surface structure. Since the intersection is located at the overlap and is concave inward, an oil wedge can be effectively formed at the overlap during the upward and downward processes of the piston ring, generating oil film protection, thereby greatly improving the lubrication effect at this position, reducing the risk of abnormal wear and cylinder pulling, and improving the reliability and service life of the piston ring.
[0019] (2) The outer circle of the piston ring body of the utility model adopts a smooth arc surface to form a double barrel surface structure. The three endpoints of the double barrel surface outer circle are located on the same outer circle surface. The centers of the first arc surface and the second arc surface are aligned along the axial direction, which facilitates processing and reduces manufacturing costs.
[0020] (3) The present invention limits the values of the arc center and the two end faces. When the values fall within this range, it is more conducive to the piston ring to generate oil film during the upward or downward movement, which is more conducive to lubrication and reduces friction and wear.
[0021] (4) The present invention limits the distance e between the convex points of the arc surface, which is not only conducive to the formation of oil film on both the upper and lower barrel surfaces during the upward movement of the piston ring, but also leaves a gap at the convex point position of the first arc surface, which can perform thermal compensation during actual use, reduce the risk of hard contact between the piston ring and the cylinder liner, and thus reduce the risk of cylinder pulling.
[0022] (5) The utility model applies a lubricating coating on the surface of the double barrel surface structure to further reduce wear and make the piston ring more widely used.
[0023] (6) The utility model provides a variety of double-barrel piston ring joint structures to meet different usage requirements. BRIEF DESCRIPTION OF THE DRAWINGS
[0024] In order to make the content of the utility model easier to understand, the utility model is further described in detail below based on specific embodiments and in conjunction with the accompanying drawings, wherein:
[0025] Figure 1 Schematic diagram of the cross-sectional structure of the piston body of Example 1;
[0026] Figure 2 Schematic diagram of the cross-sectional structure of the piston body at the joint of Example 1;
[0027] Figure 3 Schematic diagram of the cross-sectional structure of the piston body at the joint of Example 2;
[0028] Figure 4 Schematic diagram of the cross-sectional structure of the piston body at the joint of Example 3;
[0029] Figure 5 Schematic diagram of the cross-sectional structure of the piston body at the joint of Example 4.
[0030] The reference numerals in the accompanying drawings are:
[0031] First arc surface 1, second arc surface 2, first plane 3, special-shaped surface 4, second plane 4-1, and third plane 4-2. DETAILED DESCRIPTION
[0032] In order to better understand the above technical solution, the above technical solution will be described in detail below with reference to the accompanying drawings and specific implementation methods.
[0033] (Example 1)
[0034] like Figure 1 and Figure 2 The piston ring shown includes a piston ring body with an overlap. The outer cross-section of the piston ring body is axially arranged with a first curved surface 1 and a second curved surface 2, which are connected to each other. The intersection of the first curved surface 1 and the second curved surface 2 is recessed inward, forming a double-barrel surface structure. As the piston ring moves upward and downward, a wedge-shaped surface is formed between the intersection and the convex points of the curved surface, thereby forming an oil film at the intersection. The axial distance between the intersection and the top surface of the piston ring body is k, the axial fit clearance of the overlap is δ, and the axial distance between the upper fitting surface of the outer ring of the overlap and the top surface of the piston ring body is h3, where h3 ≤ k ≤ h3 + δ is satisfied. This ensures that the overlap is located at the intersection, significantly improving lubrication at this location, reducing the risk of abnormal wear and cylinder scuffing, and increasing the reliability and service life of the piston ring.
[0035] Specifically, the overlap is formed by a matching upper mating surface and a lower mating surface, wherein the upper mating surface is a first plane 3, and the first plane horizontally extends from the intersection of the two arc surfaces to the inner circle of the piston ring body.
[0036] The intersection of the first and second curved surfaces 1 and 2 is located on the upper portion of the piston ring body. Both surfaces are coated with a lubricating or wear-resistant coating to further reduce wear or improve wear resistance. The first and second curved surfaces 1 and 2 are smooth circular arcs for ease of machining. The upper end of the first curved surface 1, the lower end of the first curved surface 2, and the intersection between the first and second curved surfaces 1 and 2 are located on the same outer surface. The center of the first curved surface 2 is axially aligned with the center of the second curved surface 2. The distance between the center of the first curved surface 1 and the top surface of the piston ring is h1, satisfying h1 = (1 / 4 to 3 / 4)h3. The distance between the center of the second curved surface 2 and the bottom surface of the piston ring is h2, satisfying h2 = (1 / 4 to 3 / 4)(h - h3), where h is the axial thickness of the piston ring. This facilitates the generation of an oil film during the upward or downward movement of the piston ring, promoting lubrication and reducing friction and wear.
[0037] The distance between the convex point of the first arc surface 1 and the inner circle of the piston ring body is smaller than the distance between the convex point of the second arc surface 2 and the inner circle of the piston ring body, and the radial spacing e between the two convex points satisfies e≤0.1mm. This is not only beneficial to the formation of oil film on both the upper and lower barrel surfaces during the upward movement of the piston ring, but also leaves a gap at the convex point position of the first arc surface, which can perform thermal compensation during actual use, reduce the risk of hard contact between the piston ring and the cylinder liner, and thus reduce the risk of cylinder pulling.
[0038] The working principle of this embodiment is as follows: During the upward movement, since the distance from the upper end of the first arc surface 1 to the inner circle of the piston ring body is less than the distance from the convex point of the first arc surface to the inner circle of the piston ring body, a wedge-shaped area is formed from the upper end of the first arc surface 1 to the convex point and then to the inner wall of the cylinder liner in the upward direction. According to the relevant theory of dynamic pressure lubrication, this allows the upper end of the first arc surface 1 to form an oil film protection, greatly reducing the risk of abnormal wear and cylinder scuffing. Similarly, during the downward movement, the distance from the intersection line to the inner circle of the piston ring body is less than the distance from the convex point of the first arc surface to the inner circle. At this time, along the downward direction, from the intersection line to the convex point and then to the inner wall of the cylinder liner, a wedge-shaped area is formed. According to the relevant theory of dynamic pressure lubrication, this allows the lower end of the first arc surface, that is, the overlap, to also form an oil film protection, greatly reducing the risk of abnormal wear and cylinder scuffing. Similarly, whether moving upward or downward, the corresponding position of the second arc surface can also form an oil film protection, greatly reducing the risk of abnormal wear and cylinder scuffing.
[0039] (Example 2)
[0040] The structure of this embodiment is similar to that of embodiment 1, except that Figure 2 As shown, the first plane extends obliquely downward to the inner circle of the piston ring body.
[0041] (Example 3)
[0042] The structure of this embodiment is similar to that of embodiment 1, except that Figure 3 As shown, the first plane extends obliquely downward to the bottom surface of the piston ring body.
[0043] (Example 4)
[0044] The structure of this embodiment is similar to that of embodiment 1, except that Figure 4 As shown, the upper mating surface is a profiled surface 4, which is composed of a second plane 4-1 and a third plane 4-2 that are perpendicular to each other and have arc transitions, wherein the third plane extends to the bottom surface of the piston ring.
[0045] The utility model forms a double-barrel surface structure by arranging two intersecting arc surfaces on the outer circular working surface of the piston ring, and at the same time ensures that the distance k from the intersection line to the top surface, the distance h3 from the upper matching surface of the overlap to the top surface, and the overlap matching clearance δ satisfy the relationship k=h3+δ, so that the upper overlap and lower overlap of the piston ring with the overlap structure can effectively form an oil wedge between the inner wall of the cylinder liner during the downward and upward processes, thereby generating oil film protection between the upper overlap and lower overlap of the piston ring and the inner wall of the cylinder liner respectively, thereby greatly improving the lubrication effect of the overlap position, greatly reducing the risk of abnormal wear and cylinder pulling, and improving the reliability and service life of the piston ring.
[0046] The specific embodiments described above further illustrate the purpose, technical solutions and beneficial effects of the present invention in detail. It should be understood that the above description is only a specific embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, improvements, etc. made within the spirit and principles of the present invention should be included in the scope of protection of the present invention.
Claims
1. A piston ring, characterized in that: It includes a piston ring body with an overlap, wherein the outer circular cross-section of the piston ring body is axially provided with a first arc surface and a second arc surface arranged in connection with each other, and the intersection line of the first arc surface and the second arc surface is recessed inward to form a double-barrel surface structure, the axial distance between the intersection line and the top surface of the piston ring body is k, the axial fitting clearance of the overlap is δ, and the axial distance between the upper fitting surface of the outer ring of the overlap and the top surface of the piston ring body is h3, and h3≤k≤h3+δ is satisfied.
2. A piston ring according to claim 1, characterized in that: The first arc surface and the second arc surface are both smooth arc surfaces.
3. The piston ring according to claim 2, characterized in that: The upper end of the first arc surface, the lower end of the first arc surface and the intersection line between the first arc surface and the second arc surface are located on the same outer circular surface.
4. A piston ring according to claim 3, characterized in that: The center of the first arc surface is aligned with the center of the second arc surface along the axial direction.
5. The piston ring according to claim 4, characterized in that: The distance between the center of the first arc surface and the top surface of the piston ring is h1, and satisfies h1=(1 / 4-3 / 4)h3.
6. The piston ring according to claim 4, characterized in that: The distance between the center of the second arc surface and the bottom surface of the piston ring is h2, and satisfies h2=(1 / 4~3 / 4)(h-h3), where h is the axial thickness of the piston ring.
7. The piston ring according to claim 1, characterized in that: The distance between the convex point of the first arc surface and the inner circle of the piston ring body is smaller than the distance between the convex point of the second arc surface and the inner circle of the piston ring body.
8. The piston ring according to claim 7, characterized in that: The radial distance between the convex points of the first arc surface and the convex points of the second arc surface is e, and satisfies e≤0.1 mm.
9. The piston ring according to claim 1, characterized in that: The outer circle of the piston ring body is coated with a lubricating coating or a wear-resistant coating.
10. The piston ring according to claim 1, characterized in that: The overlap is formed by a matching upper mating surface and a lower mating surface, and the upper mating surface or the lower mating surface is a first plane or a special-shaped surface, and the first plane extends horizontally to the inner ring of the piston ring body or extends obliquely downward to the inner ring or bottom surface of the piston ring body, and the special-shaped surface is composed of a second plane and a third plane that are perpendicular to each other and have a circular arc transition, and the third plane extends to the bottom surface of the piston ring.