Engine rocker arm bias spring rod

Abstract

The utility model discloses an engine rocker arm bias spring rod, include: installation part and function department, the bolt mounting hole is set up on installation part, and the spring rod is installed on the rocker arm axle through the bolt mounting hole, and the plane of function department is provided with the boss, and the boss is used for the one end of bias spring and is pressed, and the plane of function department extends the boss and the axis between bolt mounting hole is one preset angle, so that when the rocker arm swings to make bias spring be compressed to the limit working position of shortest, the plane of function department and the spring mounting seat plane on the rocker arm keep parallel, through above -mentioned mode, the utility model discloses can preset angle and make bias spring parallel at limit position both ends surface to reduce stress, and through integral type torsion portion, optimization guide height and nimble layout, comprehensively promote spring life, system reliability and space utilization.

Description

Technical Field

[0001] This utility model relates to the field of engine technology, and in particular to an engine rocker arm bias spring rod. Background Technology

[0002] In engine valve trains or auxiliary braking systems, a bias spring assembly is typically used to ensure continuous contact between the rollers and cams in the rocker arm assembly, preventing disengagement and reducing operating noise while extending component lifespan. In this assembly, the bias spring is pre-compressed between a mounting base on the rocker arm and a mounting surface of the spring rod itself via a spring bar. However, when upgrading existing mass-produced engines, cost control often necessitates avoiding structural modifications to core components such as the already designed rocker arm shaft assembly and support. This constraint presents a significant technical challenge: the mounting surface of the spring rod on the rocker arm shaft and the mounting surface of the rocker arm supporting the spring have a large, non-parallel spatial angle due to the original design layout.

[0003] This initial structural mismatch can lead to more complex dynamic problems. During operation, the rocker arm oscillates around its axis at a necessary small angle, causing the relative spatial positions (including relative angles and axial positions) of the two support ends of the spring to constantly change throughout the entire operating cycle. This continuous relative motion forces the spring wire to repeatedly bend and twist while bearing conventional axial pressure. The direct consequence is the generation of significant additional alternating stress within the spring wire. This additional stress not only exacerbates material fatigue and significantly shortens the spring's service life but also potentially affects the reliability and safety of the entire system. Utility Model Content

[0004] The main technical problem solved by this utility model is to provide an engine rocker arm bias spring rod that can reduce stress by making the two ends of the bias spring parallel at the extreme position through a preset included angle, and comprehensively improves spring life, system reliability and space utilization through an integrated torsion part, optimized guide height and flexible layout.

[0005] To solve the above-mentioned technical problems, the present invention provides a technical solution: an engine rocker arm bias spring rod, comprising: a mounting part and a functional part; the mounting part has bolt mounting holes, and the spring rod is mounted on the rocker arm shaft through the bolt mounting holes; the functional part has a boss on its plane, which is used to press against one end of the bias spring; the plane of the functional part with the boss extends forms a preset non-90° angle with the axis of the bolt mounting holes, so that when the rocker arm swings to the limit working position where the bias spring is compressed to its shortest length, the plane of the functional part remains parallel to the plane of the spring mounting seat on the rocker arm.

[0006] Preferably, it also includes a torsion part, through which the mounting part and the functional part are connected, and the torsion part forms a preset non-90° angle between the plane of the boss and the axis of the bolt mounting hole.

[0007] Preferably, the mounting section is located at the end of the functional section.

[0008] Preferably, the functional units are arranged in multiple ways.

[0009] Preferably, the included angle is 20°-25°.

[0010] Preferably, the outer circumferential surface of the boss is a cylindrical guide surface, which is used to cooperate with the inner ring of the bias spring to limit the radial displacement of the bias spring.

[0011] Preferably, the effective guide height of the boss is 0.5-1 times the wire diameter of the bias spring.

[0012] The beneficial effects of this utility model are as follows: By setting a preset angle between the plane of the protrusion extending from its functional part and the axis of the bolt mounting hole, the spring rod is transformed from a simple connector into a "space adapter," making it suitable for more engine conditions. This ensures that when the rocker arm swings to the extreme working position where the bias spring is compressed to its shortest length and the stress reaches its peak, the upper and lower support planes of the bias spring remain parallel. This directly eliminates the huge additional bending stress caused by the non-parallelism of the two end faces when the bias spring is under maximum load, greatly improving the reliability of the bias spring under extreme conditions. The optimized angle design achieves full-cycle improvement of the bias spring's stress state, significantly smoothing the bending stress fluctuations of the bias spring wire throughout the swing process, effectively avoiding repeated impacts of stress peaks, fundamentally solving the problem of early fatigue fracture of the bias spring, thus significantly extending the service life of the bias spring and improving the working efficiency and durability of the entire rocker arm system. Attached Figure Description

[0013] Figure 1 This is a schematic diagram showing the positional relationship between this utility model and the rocker arm and rocker arm shaft when they are in conjunction; Figure 2 This is a schematic diagram of the overall structure of this utility model.

[0014] The components in the attached diagram are labeled as follows: 1. Spring rod; 11. Mounting part; 111. Bolt mounting hole; 12. Functional part; 121. Boss; 13. Torsion part; 2. Bias spring; 3. Rocker arm. Detailed Implementation

[0015] To make the above-mentioned objects, features, and advantages of this utility model more apparent and understandable, the specific embodiments of this utility model will be described in detail below with reference to the accompanying drawings. Many specific details are set forth in the following description to provide a full understanding of this utility model. However, this utility model can be implemented in many other ways different from those described herein, and those skilled in the art can make similar modifications without departing from the spirit of this utility model. Therefore, this utility model is not limited to the specific embodiments disclosed below.

[0016] In the description of this utility model, it should be understood that the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc., indicating the orientation or positional relationship are based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this utility model and simplifying the description, and are not intended to indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this utility model.

[0017] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this utility model, "a plurality of" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0018] In this utility model, unless otherwise explicitly specified and limited, the terms "installation," "connection," "joining," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components, unless otherwise explicitly limited. Those skilled in the art can understand the specific meaning of the above terms in this utility model according to the specific circumstances.

[0019] In this utility model, unless otherwise explicitly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature is in indirect contact with the second feature through an intermediate medium. Furthermore, "above," "on top of," and "over" the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0020] It should be noted that when an element is referred to as being "fixed to" or "set on" another element, it can be directly on the other element or there may be an intervening element. When an element is considered to be "connected to" another element, it can be directly connected to the other element or there may be an intervening element. The terms "vertical," "horizontal," "upper," "lower," "left," "right," and similar expressions used herein are for illustrative purposes only and do not represent the only possible implementation.

[0021] Unless otherwise specified, physical quantities in formulas should be understood as basic quantities of SI base units, or derived quantities derived from basic quantities through mathematical operations such as multiplication, division, differentiation, or integration.

[0022] Example: refer to Figure 1 and Figure 2An engine rocker arm bias spring rod includes a mounting portion 11 and a functional portion 12. The mounting portion 11 has bolt mounting holes 111, through which the spring rod 1 is threadedly connected to the rocker arm shaft via bolts, allowing the spring rod 1 to be mounted on the rocker arm shaft. The functional portion 12 has a boss 121 extending outwards from its plane. The boss 121 is used to press against one end of a bias spring 2. The outer circumferential surface of the boss 121 is a cylindrical guide surface, used to mate with the inner ring of the bias spring 2 to limit the radial displacement of the bias spring 2. The effective guide height of the boss 121 is 0.5-1 times the diameter of the spring wire of the bias spring 2, preferably 0.8 times, thereby achieving precise guidance and stability optimization of the bias spring 2. This proportional relationship ensures that the boss 121 provides a sufficient length of contact and support surface for the inner ring of the bias spring 2, effectively preventing radial displacement, bending, or instability of the bias spring 2 under high axial pressure. This ensures that the bias spring 2 always compresses and rebounds stably and reliably along the preset axial direction. Furthermore, this guide height optimizes the stress state of the bias spring 2, avoiding uneven bending stress inside the spring wire due to insufficient guidance, thus promoting a more uniform stress distribution, significantly delaying material fatigue, and extending the spring's service life. The 0.5-1 ratio range achieves a good balance between functionality and compactness. It avoids guide function failure due to excessively low height and material waste and space occupation due to excessively high height, aligning with the design trend of lightweight and highly integrated engines.

[0023] refer to Figure 1 and Figure 2The plane of the functional part 12 with the extended boss 121 forms a preset non-90° angle with the axis of the bolt mounting hole 111, so that when the rocker arm 3 swings to the limit working position where the bias spring 2 is compressed to its shortest length, the plane of the functional part 12 remains parallel to the plane of the spring mounting seat on the rocker arm 3. The angle between the plane of the functional part 12 with the extended boss 121 and the axis of the bolt mounting hole 111 actively and precisely compensates for the inherent spatial non-parallelism between the rocker arm shaft fixed mounting surface and the dynamically swinging spring mounting seat plane on the rocker arm 3. This transforms the spring rod 1 from a passive connector into an intelligent "space adapter." It ensures that when the rocker arm 3 swings to the limit working position where the bias spring 2 is compressed to its shortest length and the internal stress reaches its peak, the upper and lower support planes of the bias spring 2 remain parallel. This precise alignment at the most critical stress point directly eliminates the enormous additional bending stress caused by the non-parallelism of the two end faces of the bias spring 2 when bearing maximum load, thereby greatly improving the reliability and durability of the bias spring 2 under extreme conditions. Moreover, this optimized design of the preset included angle achieves full-cycle improvement of the stress state of the bias spring 2, significantly smoothing the bending stress fluctuation curve experienced by the bias spring 2 wire during the entire swing of the rocker arm 3, avoiding repeated impacts of periodic stress peaks, fundamentally solving the main cause of early fatigue fracture of the spring, and thus improving the working efficiency and lifespan of the entire rocker arm 3 system.

[0024] refer to Figure 1 and Figure 2 The system also includes a torsion section 13, which connects the mounting section 11 and the functional section 12. The torsion section 13 creates a preset angle (not 90°) between the plane of the boss 121 and the axis of the bolt mounting hole 111, thus also constituting the torsion angle of the spring rod 1. This angle is between 20° and 25°, preferably 22.8°. This set angle minimizes the amplitude of bending stress fluctuations in the wire of the bias spring 2 throughout the entire swing cycle of the rocker arm 3. The torsion section 13 serves as a dedicated physical structure for achieving the preset angle. It rigidly connects the mounting section 11 and the functional section 12 into a single unit, precisely and stably maintaining the angle through its integrally formed torsional geometry. Compared to methods that form angles through secondary processing such as welding or assembly, the integral torsion section 13 offers higher structural rigidity and reliability, effectively preventing angle changes under long-term vibration and alternating loads, thus ensuring the durability of product performance.

[0025] refer to Figure 1 and Figure 2The mounting section 11 is arranged at one or both ends of the functional section 12, thereby better supporting the spring rod 1 and the supporting strength of the functional section 12. Multiple functional sections 12 can be arranged as needed. This gives the spring rod 1 assembly greater structural adaptability and functional integration capabilities. Arranging the mounting section 11 at one end of the functional section 12 is suitable for cantilever support scenarios, offering a simple structure and convenient installation. Arranging the mounting section 11 at both ends of the functional section 12 creates a simply supported beam structure. This design significantly improves the overall stiffness and resistance to bending deformation of the functional section 12, especially when its span is large, ensuring the preset included angle remains stable under stress. This is particularly suitable for harsh working conditions with large supporting forces or long installation spans. Furthermore, multiple functional sections 12 can be arranged on the spring rod 1 as needed, allowing a single spring rod 1 part to simultaneously provide mounting and pressing points for multiple bias springs 2, resulting in high integration, effectively reducing the total number of parts in the engine compartment, simplifying the assembly process, and optimizing the utilization efficiency of limited space.

[0026] The above description is merely an embodiment of this utility model and does not limit the patent scope of this utility model. Any equivalent structural or procedural transformations made based on the description and drawings of this utility model, or direct or indirect applications in other related technical fields, are similarly included within the patent protection scope of this utility model.

Claims

1. An engine rocker arm bias spring rod, characterized in that, include: The mounting part (11) and the functional part (12) are provided. The mounting part (11) is provided with bolt mounting holes (111). The spring rod (1) is mounted on the rocker arm (3) shaft through the bolt mounting holes (111). The functional part (12) has a boss (121) on its plane, and the boss (121) is used to press against one end of the bias spring (2); The plane of the functional part (12) with the boss (121) extends to form a preset non-90° angle with the axis of the bolt mounting hole (111), so that when the rocker arm (3) swings to the shortest limit working position where the bias spring (2) is compressed, the plane of the functional part (12) remains parallel to the plane of the spring mounting seat on the rocker arm (3).

2. The engine rocker arm bias spring rod according to claim 1, characterized in that: It also includes a torsion part (13), through which the mounting part (11) and the functional part (12) are connected. The torsion part (13) makes the plane of the boss (121) form a preset non-90° angle with the axis of the bolt mounting hole (111).

3. The engine rocker arm bias spring rod according to claim 2, characterized in that: The mounting part (11) is arranged at the end of the functional part (12).

4. The engine rocker arm bias spring rod according to claim 3, characterized in that: The functional unit (12) is arranged in multiple ways.

5. An engine rocker arm bias spring rod according to claim 1 or 2, characterized in that: The included angle is 20°-25°.

6. The engine rocker arm bias spring rod according to claim 1, characterized in that: The outer circumferential surface of the boss (121) is a cylindrical guide surface, which is used to cooperate with the inner ring of the bias spring (2) to limit the radial displacement of the bias spring (2).

7. The engine rocker arm bias spring rod according to claim 1, characterized in that: The effective guide height of the boss (121) is 0.5-1 times the wire diameter of the bias spring (2).

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