H-shaped hydrostatic oil groove, friction pair component, and hydraulic device

Abstract

The application provides an H-shaped static pressure oil groove, a friction pair component and a hydraulic device, and belongs to the technical field of hydraulic transmission equipment. The H-shaped static pressure oil groove has an H-shaped unfolded shape and comprises two longitudinal groove bodies which are both semicircular and inwardly curved and are distributed along the curved surface of a plunger-roller friction pair; and a transverse groove body which is linear and is connected to the middle positions of the two longitudinal groove bodies to form a through fluid channel. The H-shaped static pressure oil groove plays a key role in providing lubrication and bearing functions. Compared with a conventional static pressure oil groove, the friction torque can be reduced by 88% at most, the bearing capacity is greatly improved, and the service life of the plunger is greatly improved. The global optimal distribution of the lubricating oil film is realized, and the performance bottleneck of the conventional oil groove is broken through.

Description

Technical Field

[0001] This invention belongs to the technical field of hydraulic transmission equipment, specifically relating to a hydrostatic oil groove structure for a piston-roller friction pair in a hydraulic motor, which is particularly suitable for medium and high pressure hydraulic motor friction pair systems that require high load capacity, low friction, and long service life. Background Technology

[0002] Hydrostatic grooves are key structures affecting the load-bearing, lubrication, and wear performance of friction pairs. They provide necessary hydrostatic support to the friction pair, reducing the contact pressure of local micro-protrusions at the interface. Furthermore, they promote lubricating oil film formation and heat dissipation, thereby reducing friction and improving wear characteristics. Existing hydrostatic groove structures are mostly circular, and relying solely on the designer's experience makes it difficult to obtain a globally optimal configuration. Therefore, designing a hydrostatic groove with high load-bearing capacity that satisfies the globally optimal solution is the technical problem this invention aims to solve. Summary of the Invention

[0003] In view of this, to obtain a hydrostatic oil groove with high load-bearing capacity and that satisfies the global optimal solution, this invention provides an H-shaped hydrostatic oil groove, friction pair components, and hydraulic equipment. This H-shaped hydrostatic oil groove plays a crucial role in providing lubrication and load-bearing functions. Compared to traditional hydrostatic oil grooves, it can reduce frictional torque by up to 88%, significantly improving load-bearing capacity and greatly extending plunger life. It achieves the global optimal distribution of the lubricating oil film, breaking through the performance bottleneck of traditional oil grooves.

[0004] To achieve the above objectives, the present invention provides the following technical solution: In a first aspect, the present invention provides an H-shaped hydrostatic oil groove for a hydraulic motor plunger-roller friction pair, wherein the unfolded shape of the H-shaped hydrostatic oil groove is H-shaped, comprising: Both longitudinal grooves are curved inward in a semi-circular shape and distributed along the arc surface of the plunger-roller friction pair; A transverse trough, in a straight line, connects the two longitudinal troughs at their midpoint, forming a through fluid channel.

[0005] Secondly, the present invention provides a friction pair component, comprising the H-shaped hydrostatic oil groove of the above-mentioned hydraulic motor plunger-roller friction pair.

[0006] Thirdly, the present invention also provides a hydraulic device comprising the aforementioned friction pair components.

[0007] Compared with the prior art, the present invention has the following beneficial effects: The H-shaped configuration, optimized through a self-evolutionary design method, enhances lubricant distribution characteristics and load-bearing capacity, achieving globally optimal lubricant film distribution and overcoming the performance bottlenecks of traditional oil grooves. Compared to traditional hydrostatic oil grooves, this configuration can reduce frictional torque by up to 88%, while effectively increasing load-bearing capacity and significantly extending plunger life. Its optimized structural design ensures more uniform lubricant distribution, providing more stable hydrostatic support for the friction pair.

[0008] Other specific technical advantages of the present invention will be described in detail in the following specific embodiments. Attached Figure Description

[0009] Figure 1 This is a schematic diagram showing the unfolded shape of the H-shaped hydrostatic oil groove of the hydraulic motor plunger-roller friction pair of the present invention; Figure 2 This is a front view of the H-shaped hydrostatic oil groove on the curved surface of the hydraulic motor plunger-roller friction pair; Figure 3 This is a left view of the H-shaped hydrostatic oil groove on the curved surface of the hydraulic motor plunger-roller friction pair; Figure 4 This is an isometric view of the H-shaped hydrostatic oil groove on the curved surface of the hydraulic motor plunger-roller friction pair; Figure 5 A comparison diagram of the shapes of traditional hydrostatic oil tanks; Figure 6 A comparison of the simulated surface contact force of the H-shaped hydrostatic oil tank and the traditional hydrostatic oil tank under the same load is shown. The left side shows the simulated contact force of the H-shaped hydrostatic oil tank of the present invention, while the right side shows the simulated contact force of the traditional hydrostatic oil tank. Figure 7 The graphs show the changes in pressure and frictional torque in an H-shaped hydrostatic oil tank and a conventional hydrostatic oil tank under varying torque and speed. (a) shows the pressure variation, and (b) shows the frictional torque variation.

[0010] In the figure, 1 is the first longitudinal channel; 2 is the second longitudinal channel; and 3 is the transverse channel. Detailed Implementation

[0011] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. All other embodiments obtained by those skilled in the art based on the embodiments of the present invention without creative effort are within the scope of protection of the present invention.

[0012] In the description of this invention, it should be noted that the terms "upper", "lower", "inner", "outer", "top / bottom", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this invention.

[0013] In the description of this invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "installed," "equipped with," "sleeved / connected," "connected," etc., should be interpreted broadly. For example, "connection" can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium; it can be a connection within two components. Those skilled in the art can understand the specific meaning of the above terms in this invention based on the specific circumstances.

[0014] like Figure 1-7 As shown, the present invention provides an H-shaped hydrostatic oil groove for a hydraulic motor plunger-roller friction pair. The unfolded shape of the H-shaped hydrostatic oil groove is H-shaped, comprising: Both longitudinal grooves (first longitudinal groove 1 and second longitudinal groove 2) are curved inward in a semi-circular shape and distributed along the arc surface of the plunger-roller friction pair. A transverse groove 3, in a straight line, connects the two longitudinal grooves at their midpoint, forming an "I"-shaped, continuous fluid channel structure that traverses the central region of the friction pair. The outer edges of the two longitudinal grooves are always equidistant from the outer edge of the plunger-roller friction pair, preferably at a distance of 3-6 mm, ensuring uniform lubricant film coverage of the friction area and maximizing coverage. The semi-circular longitudinal grooves adapt to the arc-shaped contact characteristics of the friction pair, and combined with the 3-6 mm equidistant outer edge design, the lubricant film coverage area is significantly increased compared to traditional circular oil grooves, avoiding dry friction in the edge areas.

[0015] In this invention, the two longitudinal tanks are symmetrical about the longitudinal and transverse central axes of the unfolded plane, which is used for balanced pressure distribution. The symmetrical structure ensures that the flow rate of the two longitudinal tanks is consistent, and the transverse tank 3 acts as the "main distribution channel" to balance the pressure difference, thus significantly reducing the fluctuation range of oil film pressure compared to traditional oil tanks.

[0016] The transverse grooves 3 are of equal width, preferably 2-4 mm. The ratio of the width to depth of the longitudinal and transverse grooves in the H-shaped hydrostatic oil grooves is 0.5-0.8. The ratio of the width of the transverse groove 3 to the width of the longitudinal groove is 0.6-0.8, ensuring a balanced flow distribution of lubricating oil between the transverse and longitudinal grooves, avoiding energy loss caused by excessive local flow, and improving lubricating oil utilization. The two longitudinal grooves exhibit a trend of being narrow in the middle and gradually widening at both ends. The gradually widening design at both ends of the longitudinal grooves guides the lubricating oil to flow towards the edge of the friction pair, solving the edge wear problem. This complements the equal-width structure of the transverse groove 3, optimizing the distribution of lubricating oil in the edge and center areas of the friction pair. All inner surface corners of the H-shaped hydrostatic oil groove are rounded, preferably with a radius of not less than 0.5 mm. The connection between the longitudinal groove and the transverse groove 3 is preferably rounded to form a smooth fluid channel, preferably with a radius of not less than 1 mm, to avoid lubricating oil flow resistance caused by right-angle corners and to form a smooth "longitudinal-transverse-longitudinal" through channel.

[0017] In this invention, the semi-arc structure of the first longitudinal groove 1 and the second longitudinal groove 2 is adapted to the arc surface contact characteristics of the friction pair. The gradually widening design at both ends can guide the lubricating oil to flow towards the edge of the friction pair, avoiding local wear in the edge area due to insufficient lubrication. The positioning of the outer edge at equal intervals of 3-6mm ensures that the coverage area of ​​the lubricating oil film is accurately matched with the actual contact area of ​​the friction pair, thereby increasing the load-bearing area.

[0018] The straight channel of the transverse groove 3 connects the two longitudinal grooves, serving as the "main distribution channel" for lubricating oil. It evenly delivers high-pressure oil to the longitudinal grooves while balancing the pressure difference between the two longitudinal grooves, thus preventing the oil film from rupturing due to excessive local pressure.

[0019] The rounded corners of all inner surfaces and the rounded transitions at the connections between the longitudinal and transverse grooves reduce eddy current losses during lubricant flow, lower pressure losses, and increase the oil film establishment speed. The groove configuration optimized by a self-evolutionary algorithm can adaptively adjust the lubricant flow rate according to the force distribution of the friction pair, achieving a dynamic balance of "more oil supply in high-pressure areas and less oil supply in low-pressure areas," avoiding localized over- or under-lubrication caused by traditional empirical designs.

[0020] The working principle of this invention is as follows: High-pressure lubricating oil enters the transverse groove 3 through the oil supply hole, and is then distributed to the longitudinal grooves on both sides. It then flows along the semi-circular path of the longitudinal grooves towards the edge of the friction pair. Due to the gradual design of the longitudinal grooves, which are narrower in the middle and wider at both ends, the lubricating oil has a high flow velocity and low pressure in the middle region, and a low flow velocity and high pressure at both ends, forming a pressure distribution of "high pressure at the edges and balanced pressure in the center." This ensures continuous oil film coverage across the entire friction pair, achieving "zero-contact" lubrication.

[0021] In summary, the H-shaped hydrostatic oil groove provided by this invention fundamentally solves the defects of traditional oil grooves such as "uneven distribution, low load capacity, and high friction" through the above-mentioned technical means, and provides an efficient and reliable lubrication solution for hydraulic motor friction pair systems.

[0022] The H-shaped hydrostatic oil groove of this invention is optimized through a self-evolutionary design method. Its configuration provides superior lubricating oil distribution characteristics and load-bearing capacity compared to conventionally shaped hydrostatic oil grooves. Simulation comparisons of the H-shaped and conventional hydrostatic oil grooves under the same load are shown below. Figure 6 As shown in the attached diagrams on the left and right, the surface contact force of the new oil tank is superior to that of the traditional oil tank. A comparison of the contact force and frictional torque of the traditional circular oil tank and the new H-shaped hydrostatic oil tank under varying pressure and velocity is shown in the diagram below. Figure 7 As shown in (a) and (b), it can be seen that the new H-type oil tank has smaller frictional torque and contact force under different speeds and static pressures, and thus has a longer service life.

[0023] The above description is merely a preferred embodiment of the present invention. However, the scope of protection of the present invention is not limited thereto. Any equivalent substitutions or modifications made by those skilled in the art within the scope of the technology disclosed in the present invention should be covered within the scope of protection of the present invention.

Claims

1. An H-shaped hydrostatic oil groove for a hydraulic motor plunger-roller friction pair, characterized in that, The H-shaped hydrostatic oil tank has an H-shaped unfolded shape and includes: Both longitudinal grooves are curved inward in a semi-circular shape and are distributed along the edge of the arc surface of the plunger-roller friction pair; A transverse trough, in a straight line, connects the two longitudinal troughs at their midpoint, forming a through fluid channel; The outer edges of the two longitudinal grooves are always equidistant from the outer edge of the plunger-roller friction pair; The two longitudinal grooves exhibit a trend of being narrow in the middle and gradually widening at both ends; The distance between the outer edges of the two longitudinal grooves and the outer side of the plunger-roller friction pair is 3-6 mm; High-pressure lubricating oil enters the transverse groove through the oil supply hole, and is distributed to the longitudinal grooves on both sides through the transverse groove. Then, it flows towards the edge of the friction pair along the semi-arc path of the longitudinal groove. The lubricating oil has a high flow velocity and low pressure in the middle area of ​​the longitudinal groove, and a low flow velocity and high pressure at both ends, forming a pressure distribution with high pressure at the edges and a balanced pressure in the center.

2. The H-shaped hydrostatic oil groove of the hydraulic motor plunger-roller friction pair according to claim 1, characterized in that, The two longitudinal grooves are symmetrical about the longitudinal and transverse central axes of the unfolded plane.

3. The H-shaped hydrostatic oil groove of the hydraulic motor plunger-roller friction pair according to claim 1, characterized in that, The transverse grooves are of equal width.

4. The H-shaped hydrostatic oil groove of the hydraulic motor plunger-roller friction pair according to claim 3, characterized in that, The width of the transverse groove is 2-4 mm.

5. The H-shaped hydrostatic oil groove of the hydraulic motor plunger-roller friction pair according to claim 1, characterized in that, The ratio of the width to depth of the longitudinal and transverse sections of the H-shaped hydrostatic oil tank is both in the range of 0.5-0.

8.

6. The H-shaped hydrostatic oil groove of the hydraulic motor plunger-roller friction pair according to claim 1, characterized in that, All inner surface corners of the H-shaped hydrostatic oil tank are rounded.

7. The H-shaped hydrostatic oil groove of the hydraulic motor plunger-roller friction pair according to claim 6, characterized in that, The radius of the fillet should not be less than 0.5mm.

8. The H-shaped hydrostatic oil groove of the hydraulic motor plunger-roller friction pair according to claim 1, characterized in that, The connection between the longitudinal and transverse channels is rounded to form a smooth fluid channel.

9. The H-shaped hydrostatic oil groove of the hydraulic motor plunger-roller friction pair according to claim 8, characterized in that, The radius of the fillet should be no less than 1mm.

10. The H-shaped hydrostatic oil groove of the hydraulic motor plunger-roller friction pair according to any one of claims 1-9, characterized in that, The ratio of the width of the transverse groove to the width of the longitudinal groove is in the range of 0.6-0.

8.

11. A friction pair component, characterized in that, The hydraulic motor plunger-roller friction pair includes an H-shaped hydrostatic oil groove as described in any one of claims 1-10.

12. A hydraulic device, characterized in that, It includes the friction pair component as described in claim 11.

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