WO2016050164A1 - 一种变径向厚度活塞环 - Google Patents

一种变径向厚度活塞环 Download PDF

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Publication number
WO2016050164A1
WO2016050164A1 PCT/CN2015/090543 CN2015090543W WO2016050164A1 WO 2016050164 A1 WO2016050164 A1 WO 2016050164A1 CN 2015090543 W CN2015090543 W CN 2015090543W WO 2016050164 A1 WO2016050164 A1 WO 2016050164A1
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Prior art keywords
opening
piston ring
ring body
ring
circular surface
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PCT/CN2015/090543
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English (en)
French (fr)
Inventor
吴映雪
胡敏
刘千喜
周月亭
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仪征亚新科双环活塞环有限公司
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Application filed by 仪征亚新科双环活塞环有限公司 filed Critical 仪征亚新科双环活塞环有限公司
Priority to DE212015000233.0U priority Critical patent/DE212015000233U1/de
Publication of WO2016050164A1 publication Critical patent/WO2016050164A1/zh

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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
    • F16J9/00—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction
    • F16J9/12—Details
    • F16J9/14—Joint-closures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F5/00—Piston rings, e.g. associated with piston crown
    • 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
    • F16J9/00—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction
    • F16J9/12—Details
    • F16J9/20—Rings with special cross-section; Oil-scraping rings

Definitions

  • the invention relates to the technical field of piston ring manufacturing, and in particular to a variable radial thickness piston ring.
  • FIG. 1 it is a schematic structural view of a piston ring 10 in the prior art, as shown in FIG. 2 , which is a schematic diagram of a state in which a piston ring and a cylinder liner are matched in the prior art, wherein the piston ring 10 includes a ring body 11 .
  • the ring body 11 is a uniform ring structure having an opening 12 on one side, which has the following disadvantages in operation:
  • the inner and outer circular surfaces of the ring body 11 have different operating temperatures, that is, the inner circular surface has a high operating temperature, and the outer circular surface has a lower operating temperature than the inner circular surface.
  • the amount of thermal expansion of the inner circular surface is greater than the thermal expansion amount of the outer circular surface, and since the outer circular surface of the annular body 11 is restricted by the inner circular surface of the cylinder liner 20, thermal expansion cannot be released, thereby causing the ring body 11 to be at the opening 12 In the range of 90° on each side, the ring body 11 will be deformed and a gap will appear between the outer circular surface of the ring body 11 and the inner circular surface of the cylinder liner 20, and the outer circular surface of the ring body 11 and the inner circular surface of the cylinder liner 20 The phenomenon of non-contact occurs, and at this time, due to the existence of the width of the opening 12 of the ring body 11, the ring body 11 has a certain deformation space at the two ends of the opening 12, so that the ring body 11 is at both ends of the opening 12.
  • the outer circular surface at the position remains in contact with the inner circular surface of the cylinder liner 20, which causes the outer circular surface which should be within 90 degrees of both sides of the opening 12 of the ring body 11 to be inside the cylinder liner 20.
  • Round contact pressure Transfer to the position of both ends of the opening 12, thereby causing a sharp rise in the contact pressure between the outer circular surface at the both ends of the opening 12 of the ring body 11 and the inner circular surface of the cylinder liner 20, exacerbating the wear there Especially for an engine with a high heat load, the wear on both sides of the opening 12 of the ring body 11 of the piston ring 10 of the prior art is more serious, which greatly affects the durability of the engine.
  • An object of the present invention is to provide a variable radial thickness piston ring which solves the problem of wear of the outer circular surface of the piston ring opening portion in the prior art high heat load engine, improves the durability of the piston ring, and further improves the durability of the engine.
  • a variable radial thickness piston ring includes a ring body having an opening, the piston ring being symmetrically disposed on both sides of the opening in a mounted state, and being clipped from the centerline of the opening by 1° to 90°
  • the inner diameter R2 of the ring body in the circumferential sector of the corner is greater than the inner diameter R1 of the ring body in the circumferential sector of the angle of 90 to 180 with the centerline of the opening.
  • the diameter of the ring body in a circumferential sector region at an angle of 1° to 90° to the center line of the opening is smaller than the radial thickness a1 of the ring body of the remaining portion.
  • the radial thickness a2 of the ring body in the circumferential sector region at an angle of 1 to 90 with respect to the center line of the opening is the radial thickness a1 of the ring body of the remaining portion 0.5 to 0.995 times.
  • the variable radial thickness piston ring of the present invention comprises a ring body having an opening, the piston ring being symmetrically disposed on both sides of the opening in a mounted state, from a circumference of an angle of 1 to 90 with respect to the center line of the opening
  • the inner diameter R2 of the ring body in the sector-shaped region is larger than the inner diameter R1 of the ring body in the circumferential sector region at an angle of 90° to 180° with the center line of the opening; when the piston ring is in the mounted state, due to the ring body
  • the outer diameter is constant, so that the two ends of the opening of the ring body are close to each other by the inner circular surface of the cylinder sleeve, and at this time, the circumference will be made to be at an angle of 1° to 90° with the center line of the opening.
  • the inner diameter R2 of the ring body in the sector body in the sector-shaped region is larger than the inner diameter R1 of the ring body in an angle of 90° to 180° with the center line of the opening, that is, a range of 89° on both sides of the opening.
  • the inner diameter of the inner circular surface becomes larger, and the thickness of the corresponding position becomes smaller. Therefore, under high heat load conditions, the outer circumference of the piston ring in the range of 1° to 90° on both sides of the opening and the inner circumference of the cylinder liner can be made.
  • the state of contact between the faces changes to the state of most contacts, so that not only The outward tension of the small non-contact portion is transferred toward the opening of the piston ring, and the contact pressure between the outer circular surface of the opening and the inner circular surface of the cylinder liner is reduced by 5% to 50%, thereby greatly reducing the piston ring.
  • the wear amount of the outer circular surface at the two ends of the opening solves the problem of the wear of the outer circular surface of the opening portion of the piston ring in the high heat load engine in the prior art, improves the durability of the piston ring, and further improves the durability of the engine.
  • FIG. 1 is a schematic front view showing the structure of a piston ring in the prior art.
  • FIG. 2 is a schematic view showing the state in which the piston ring and the cylinder liner of FIG. 1 are engaged.
  • Figure 3 is a front elevational view showing the variable radial thickness piston ring of the present invention.
  • FIG. 4 is a schematic view showing the state in which the variable radial thickness piston ring of FIG. 3 is engaged with the cylinder liner.
  • a variable radial thickness piston ring 10 includes a ring body 11 having an opening 12.
  • the piston ring is symmetrically disposed on both sides of the opening 12 when in the mounted state, and from the opening 12
  • the inner diameter R2 of the ring body 11 in the circumferential sector region in which the center line is at an angle of 1 to 90 is larger than the ring body 11 in the circumferential sector region at an angle of 90 to 180 with the center line of the opening 12.
  • the ring body 11 is in the range of 1° to 90° (-270° to -359°) and 270° to 359° (-1° to -90°) on both sides of the opening 12, respectively.
  • the structure is symmetrically arranged, and the inner diameter R2 thereof is greater than the inner diameter R1 in the range of 90° to 270° (or ⁇ 90° to -270°), and the outer diameter is a uniform value, that is, the outer diameter in each angular range constant.
  • the two ends of the opening of the ring body 11 are brought into close contact by the inner circular surface of the cylinder casing 20, and then the The inner diameter R2 of the ring body 11 in the circumferential sector region at an angle of 1 to 90 with respect to the center line of the opening 12 is larger than the circumferential sector area at an angle of 90 to 180 with respect to the center line of the opening 12.
  • the inner diameter R1 of the ring body 11 that is, the inner diameter of the inner circular surface in the range of 89° on both sides of the opening 12 becomes larger, and the thickness of the corresponding position becomes smaller, so that the piston ring 10 can be made under high heat load conditions.
  • the radial thickness a2 of the ring body 11 in the circumferential sector portion at an angle of 1 to 90 with respect to the center line of the opening 12 is 0.5 to the radial thickness a1 of the ring body 11 of the remaining portion. 0.995 times.
  • the piston ring of the invention utilizes the characteristics that the piston ring material has different thermal expansion under different temperature conditions, and designs a reasonable piston ring structure. By designing such dimensional parameters, the outer ends of the opening 12 can be realized.
  • the contact pressure between the circular surface and the inner circular surface of the cylinder liner 20 is reduced by about 5% to 50%, thereby greatly reducing the amount of wear of the outer circular surface at the position of both ends of the opening 12 of the piston ring 10, that is, changing the piston.
  • the piston ring of this structure reduces the gap between the outer circumferential surface of the piston ring and the inner circular surface of the cylinder liner 20 by changing the inner diameter and the thickness, thereby improving the sealing of the piston ring, which is advantageous for reducing Engine air leakage and oil consumption.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)

Abstract

一种变径向厚度活塞环（10），包括具有一开口（12）的环本体（11），活塞环（10）在安装状态时，在开口（12）的两侧对称地，从与开口（12）的中心线呈1°至90°的夹角的周向扇形区域内的环本体（11）的内径R2大于与开口（12）的中心线呈90°至180°的夹角的周向扇形区域内的环本体（11）的内径R1。该活塞环解决了现有技术中高热负荷发动机中的活塞环开口部位外圆面磨损严重的问题，提高了活塞环的耐久性，进而提高了发动机的耐久性。

Description

一种变径向厚度活塞环 技术领域
本发明涉及活塞环制造技术领域，尤其涉及一种变径向厚度活塞环。
背景技术
现代汽车要求发动机具有更高的功率、更低的燃油耗和更长的使用寿命，并进一步减少尾气排放对环境的负担，因而发动机制造商都在为追求此目标而进行不断的研发。在研发过程中，为了适应上述发动机技术的发展趋势，现有技术的汽油机和柴油机中的活塞环对耐磨性和耐久性能有了更高的要求。
如图1所示，为现有技术中的活塞环10的结构示意图，如图2所示，为现有技术中的活塞环与缸套配合状态示意图，其中，该活塞环10包括环本体11，环本体11为一侧有开口12的均匀圆环结构，其在工作时，存在以下缺点：
1)由于环本体11的内部有高温燃气通过，因而环本体11的内、外圆面工作温度不同，即内圆面的工作温度高，外圆面的工作温度比内圆面的工作温度低，造成内圆面的热膨胀量大于外圆面的热膨胀量，又由于环本体11的外圆面受到缸套20的内圆面的限制，热膨胀无法得到释放，从而导致环本体11在开口12的两侧各90°范围内，环本体11将出现变形而环本体11的外圆面同缸套20的内圆面之间出现间隙，进而环本体11的外圆面与缸套20的内圆面出现不接触的现象，而此时，由于环本体11的开口12的宽度的存在，使得环本体11在开口12的两端位置处拥有一定的变形空间，从而环本体11在开口12的两端位置处的外圆面仍然与缸套20的内圆面之间保持接触，这就使得原本应该在环本体11的开口12的两侧各90°范围内的外圆面与缸套20的内圆面的接触压力 转移到开口12的两端位置处，因而引起环本体11的开口12的两端位置处的外圆面与缸套20的内圆面之间的接触压力的急剧升高，加剧此处的磨损；尤其对于热负荷高的发动机来说，现有技术中的活塞环10的环本体11的开口12两侧的磨损更为严重，极度影响发动机的耐久性能。
2)活塞环10开口两侧各30°附近的外圆面与缸套内圆面的接触压力小，在换气过程中，该部位外圆面同缸套内圆面之间存在较大的间隙，从而影响活塞环的密封，不利于减小发动机的漏气量和机油消耗量。
为此，通过设计一款新的活塞环的结构，以提高高热负荷发动机用活塞环的开口两侧外圆面的耐磨性，进而提高耐久性，是活塞环设计和制造的重点工程之一。
发明内容
本发明的目的在于提出一种变径向厚度活塞环，解决现有技术中高热负荷发动机中的活塞环开口部位外圆面的磨损问题，提高活塞环的耐久性，进而提高发动机的耐久性。
为达此目的，本发明采用以下技术方案：
一种变径向厚度活塞环，包括具有一开口的环本体，活塞环在安装状态时，在所述开口的两侧对称地，从与所述开口的中心线呈1°至90°的夹角的周向扇形区域内的所述环本体的内径R2大于与所述开口的中心线呈90°至180°的夹角的周向扇形区域内的所述环本体的内径R1。
优选的，活塞环在安装状态时，在所述开口的两侧对称地，从与所述开口的中心线呈1°至90°的夹角的周向扇形区域内的所述环本体的径向厚度a2小于其余部位的所述环本体的径向厚度a1。
进一步优选的，从与所述开口的中心线呈1°至90°的夹角的周向扇形区域内的所述环本体的径向厚度a2是其余部位的所述环本体的径向厚度a1的0.5～0.995倍。
本发明的有益效果为：
本发明的变径向厚度活塞环，包括具有一开口的环本体，活塞环在安装状态时，在开口的两侧对称地，从与开口的中心线呈1°至90°的夹角的周向扇形区域内的环本体的内径R2大于与开口的中心线呈90°至180°的夹角的周向扇形区域内的环本体的内径R1；该活塞环在安装状态时，由于环本体的外径不变，因而通过缸套的内圆面的挤压，使得环本体的开口两端接近贴合，这时，将通过将与开口的中心线呈1°至90°的夹角的周向扇形区域内的环本体的内径R2大于与开口的中心线呈90°至180°的夹角的周向扇形区域内的环本体的内径R1，也就是在开口的两侧各89°的范围内的内圆面的内径变大，对应位置的厚度变小，因而在高热负荷条件下，可以使得活塞环在开口两侧各1°至90°范围内的外圆面与缸套的内圆面之间不接触的状态改变为大部分接触的状态，这样，不仅减小原先不接触的部分向外的张力向着活塞环的开口转移，而且减小开口的外圆面与缸套的内圆面的接触压力达5％～50％，进而极大地减小活塞环的开口的两端位置处的外圆面的磨损量，解决了现有技术中高热负荷发动机中的活塞环开口部位外圆面的磨损问题，提高活塞环的耐久性，进而提高发动机的耐久性。
附图说明
图1是现有技术中的活塞环的主视结构示意图。
图2是图1中的活塞环与缸套配合状态示意图。
图3是本发明的变径向厚度活塞环的主视结构示意图。
图4是图3中的变径向厚度活塞环与缸套配合状态示意图。
图中：10-活塞环；20-缸套；11-环本体；12-开口。
具体实施方式
下面结合附图并通过具体实施方式来进一步说明本发明的技术方案。
如图3、图4所示，一种变径向厚度活塞环10，包括具有一开口12的环本体11，活塞环在安装状态时，在开口12的两侧对称地，从与开口12的中心线呈1°至90°的夹角的周向扇形区域内的环本体11的内径R2大于与开口12的中心线呈90°至180°的夹角的周向扇形区域内的环本体11的内径R1。
优选的，活塞环在安装状态时，在开口12的两侧对称地，从与开口12的中心线呈1°至90°的夹角的周向扇形区域内的环本体11的径向厚度a2小于其余部位的环本体11的径向厚度a1。
具体地，也就是说，环本体11在开口12的两侧分别以1°至90°(-270°至-359°)、270°至359°(-1°至-90°)的范围内，结构对称设置，并且其内径R2均大于90°至270°(或-90°至-270°)范围内的内径R1，外径为统一数值，也即在每个角度范围内的外径均不变。
该活塞环10在安装状态时，由于环本体11的外径不变，因而通过缸套20的内圆面的挤压，使得环本体11的开口两端接近贴合，这时，将通过将与开口12的中心线呈1°至90°的夹角的周向扇形区域内的环本体11的内径R2大于与开口12的中心线呈90°至180°的夹角的周向扇形区域内的环本体11的内径R1，也就是在开口12的两侧各89°的范围内的内圆面的内径变大，对应位置的厚度变小，因而在高热负荷条件下，可以使得活塞环10在开口12两侧各1° 至90°范围内的外圆面与缸套20的内圆面之间不接触的状态改变为大部分接触的状态，从而减小了开口12的两侧各90°范围内的外圆面与缸套20的内圆面之间的热膨胀间隙，使得活塞环10的环本体11在开口12的两侧各90°范围内其外圆面与缸套20的内圆面的接触压力又重新部分建立，大大减小了转移至开口的两端位置处的热膨胀力，从而减小了活塞环10的开口12的两端位置处的外圆面与缸套20的内圆面之间的接触压力，这就减小了原先不接触的部分向外的张力向着活塞环的开口转移，而且减小开口的外圆面与缸套的内圆面的接触压力，进而极大地减小活塞环的开口的两端位置处的外圆面的磨损量，改善活塞环的磨损，提高活塞环的耐久性能，解决了现有技术中高热负荷发动机中的活塞环开口部位外圆面的磨损问题。
进一步优选的，从与开口12的中心线呈1°至90°的夹角的周向扇形区域内的环本体11的径向厚度a2是其余部位的环本体11的径向厚度a1的0.5～0.995倍。
本发明的活塞环利用活塞环材料在不同的温度条件下，热膨胀量有差异的特性，设计出合理的活塞环结构，通过这样的尺寸参数的设计，可实现开口12的两端位置处的外圆面与缸套20的内圆面之间的接触压力降低约5％～50％，进而极大地降低活塞环10的开口12的两端位置处的外圆面的磨损量，也即改变活塞环在受热状态下，活塞环外圆面同缸套内圆面的接触状态，降低活塞环的开口12的两端位置处的外圆面与缸套20的内圆面的接触压力，进而改善活塞环的开口的两端位置处的磨损速度。同时，这种结构的活塞环，其通过改变内径及厚度，减小活塞环在该部位的外圆面与缸套20的内圆面之间的间隙，改善活塞环的密封，有利于减小发动机的漏气量和机油消耗量。
其特别适合现代汽车、工程机械、船舶动力等发动机使用，达到降低能耗 和低排放的工作要求。
以上结合具体实施例描述了本发明的技术原理。这些描述只是为了解释本发明的原理，而不能以任何方式解释为对本发明保护范围的限制。基于此处的解释，本领域的技术人员不需要付出创造性的劳动即可联想到本发明的其它具体实施方式，这些方式都将落入本发明的保护范围之内。

Claims (3)

  1. 一种变径向厚度活塞环，包括具有一开口(12)的环本体(11)，其特征在于，活塞环(10)在安装状态时，在所述开口(12)的两侧对称地，从与所述开口(12)的中心线呈1°至90°的夹角的周向扇形区域内的所述环本体(11)的内径R2大于与所述开口(12)的中心线呈90°至180°的夹角的周向扇形区域内的所述环本体(11)的内径R1。
  2. 根据权利要求1所述的变径向厚度活塞环，其特征在于，活塞环(10)在安装状态时，在所述开口(12)的两侧对称地，从与所述开口(12)的中心线呈1°至90°的夹角的周向扇形区域内的所述环本体(11)的径向厚度a2小于其余部位的所述环本体(11)的径向厚度a1。
  3. 根据权利要求2所述的变径向厚度活塞环，其特征在于，从与所述开口(12)的中心线呈1°至90°的夹角的周向扇形区域内的所述环本体(11)的径向厚度a2是其余部位的所述环本体(11)的径向厚度a1的0.5～0.995倍。
PCT/CN2015/090543 2014-09-30 2015-09-24 一种变径向厚度活塞环 WO2016050164A1 (zh)

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DE102016116807B3 (de) * 2016-09-08 2018-02-08 Federal-Mogul Burscheid Gmbh Zweiteiliger Ölabstreifring mit axialer Stabilisierung und Twistausgleich

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