WO2022036784A1 - 一种水润滑的过载保护润滑油线供给系统及过载保护方法 - Google Patents

一种水润滑的过载保护润滑油线供给系统及过载保护方法 Download PDF

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Publication number
WO2022036784A1
WO2022036784A1 PCT/CN2020/115056 CN2020115056W WO2022036784A1 WO 2022036784 A1 WO2022036784 A1 WO 2022036784A1 CN 2020115056 W CN2020115056 W CN 2020115056W WO 2022036784 A1 WO2022036784 A1 WO 2022036784A1
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WIPO (PCT)
Prior art keywords
water
lubrication
lubricating oil
friction
friction pair
Prior art date
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Ceased
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PCT/CN2020/115056
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English (en)
French (fr)
Inventor
郭峰
禹涛
张晓寒
梁鹏
陈召宝
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Jian Shun Mao Test Instrument Co Ltd
Qingdao University of Technology
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Jian Shun Mao Test Instrument Co Ltd
Qingdao University of Technology
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Application filed by Jian Shun Mao Test Instrument Co Ltd, Qingdao University of Technology filed Critical Jian Shun Mao Test Instrument Co Ltd
Priority to JP2021568714A priority Critical patent/JP7253213B2/ja
Publication of WO2022036784A1 publication Critical patent/WO2022036784A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • F16N—LUBRICATING
    • F16N7/00—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated
    • F16N7/38—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated with a separate pump; Central lubrication systems
    • 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
    • F16N—LUBRICATING
    • F16N21/00—Conduits; Junctions; Fittings for lubrication apertures
    • F16N21/02—Lubricating nipples
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/20—Hydro energy

Definitions

  • the invention belongs to the technical field of water lubrication, and in particular relates to a water-lubricated overload protection lubricating oil line supply system and an overload protection method.
  • the bearing capacity of lubrication reduces friction, reduces wear, and protects friction pair materials.
  • the lubricating oil has high viscosity and high bearing capacity, and has been widely used in the lubrication of various types of equipment.
  • the environmental pollution caused by lubricating oil and the problem of non-renewable energy make people pay more attention to environmentally friendly lubricating media, and water as a typical environmentally friendly lubricating medium is becoming more and more more attention.
  • Water lubrication has the huge advantages of simple structure, green and clean, and low price. It is suitable for ship stern shaft, water pump, hydraulic turbine, mining, agricultural machinery and other fields, and has been used for decades. However, water has the disadvantages of low viscosity and poor film-forming ability, and there are always problems in practical application.
  • the anti-interference ability of water lubrication is poor.
  • the external working conditions change such as a sudden increase in the load, it is easy to cause lubrication failure.
  • the application of water-lubricated bearings is often under complex working conditions, such as the non-conformity caused by the cantilever arrangement of the ship propeller.
  • the short-term load impact of uniform load, shafting vibration and water current/ocean current can easily cause the water film in the contact area to collapse and lose the bearing capacity, resulting in increased bearing wear and even failure.
  • oil lubrication has the advantages of high viscosity and strong bearing capacity, and the amount of lubricating oil that actually participates in lubrication in the friction pair is very small.
  • a small amount of lubricating oil is continuously injected into the contact area in the form of oil lines at a certain speed, generating additional oil film bearing capacity, improving the stability of the lubrication system, maintaining a good lubrication state between the friction pairs, and helping to survive harsh working conditions.
  • this nozzle can adjust the nozzle aperture to control the diameter of the sprayed oil line. It should be pointed out that the pollution to the environment caused by the short-term injection of trace amounts of lubricating oil can be ignored. If vegetable oil or other environmentally friendly lubricating oil with high biodegradation rate is used, its market prospect will be very broad.
  • the purpose of the present invention is to overcome the defects of the prior art, seek to design a water-lubricated overload protection lubricating oil line supply system and overload protection method, provide lubricating oil line protection when water-lubricated overload, when the water-lubricated overload or variable load
  • the nozzle When the nozzle is controlled to spray a small amount of lubricating oil, it enters the contact area at a certain speed in the form of oil lines in the water in the inlet area, and the generated oil film replaces the fragile water film to carry the load, so that the friction pairs still remain between the friction pairs under severe working conditions. Maintain a good lubrication state to ensure the normal operation of the friction pair parts, and this nozzle does not need to replace the nozzle, the nozzle aperture can be adjusted freely, and the diameter of the sprayed oil line can be controlled.
  • the present invention provides a water-lubricated overload protection method, which is that when the water-lubricated friction pair is overloaded, the lubricating oil is fed into the water-lubricated friction pair in the form of an oil line in the water through the lubricating oil line supply system.
  • Lubricating oil assists lubrication to achieve the purpose of protecting water-lubricated friction pair materials.
  • the specific process steps include:
  • the measured friction coefficient curve is Reference, to set the critical value of the friction coefficient; when the friction coefficient of the water-lubricated friction pair exceeds the critical value, the lubricating oil enters the friction pair in the form of an oil line for auxiliary lubrication, and the generated oil film replaces the fragile water film to carry the load. Realize overload protection of water lubrication;
  • the lubricating oil line supply system includes a nozzle and an oil supply system.
  • the nozzle is connected to an oil supply system, and the spray speed and supply time of the lubricating oil are set through the oil supply system; the nozzle is installed at a distance from the water-lubricated friction pair.
  • the contact area is very close, and the nozzle outlet points to the surface of the moving friction part, so as to avoid the reverse flow area of the friction pair inlet and ensure that the oil line enters the contact area at a certain speed; is circular;
  • the gap increases, that is, the thickness of the lubricating film increases, the bearing capacity of the lubricating film increases, the friction coefficient decreases rapidly, and the friction pair parts are no longer in direct contact, so that the friction pairs maintain a good lubrication state under severe working conditions, greatly reducing water lubrication. material wear;
  • the lubricating oil line is supplied to the friction pair to reduce the friction coefficient and maintain a good lubrication state; when the first supply of lubrication to the friction pair After the oil line, when the friction coefficient exceeds the critical value again, it means that the lubricating effect of the micro oil line supplied for the first time is weakened or disappeared and the overload still exists.
  • the second lubricating oil line is supplied between the friction pairs to reduce the friction coefficient In order to maintain its good lubrication state; when the friction coefficient exceeds the critical value again, it means that the lubrication effect of the second supply of trace oil line has weakened or disappeared and the overload still exists.
  • overload conditions are sudden and unexpected conditions, which often last for a short time and will not last, only a few seconds or a few minutes, and each trace of the lubricating oil line is assisted
  • the lubrication effect can reach 2 hours, so usually only one supply is enough;
  • the friction pair uses water as the only lubricating medium for normal lubrication; and the residual lubricating oil in the contact area will adhere to the surface of the contact pair due to the low surface tension.
  • the micro-oil pool exists stably for a long time and plays a good lubricating role, so that the friction pair can still maintain a low friction coefficient level for a long time under the condition of pure water lubrication, so as to achieve the purpose of protecting the material of the water-lubricated friction pair.
  • the specific measurement method of the friction coefficient curve in step S1 involved in the present invention is as follows: the material, structure, size and other related parameters of the friction pair used in the experiment are consistent with the friction pair parameters under actual working conditions. Different components have different effects on friction and wear. Therefore, the water in the water area under actual working conditions is used as the lubricating medium to immerse the friction pair, and the friction coefficient of the friction pair at different speeds is measured. changing curve.
  • the inner surface of the nozzle involved in the present invention is subjected to partial oleophobic treatment, the inner surface of the lubricating oil inlet is treated with oleophobic treatment, the inner surface of the outlet is not treated with oleophobic treatment, and the lubricating oil flows from the inlet area where the surface oleophobic treatment has been carried out to the
  • the outlet area without surface oleophobic treatment increases the pressure of the lubricating oil at the outlet, making the sprayed lubricating oil in the water more stable in the form of oil lines.
  • the lubricating oil involved in the present invention is an emulsified oil, which is prepared from an environment-friendly lubricating oil as a base oil. Auxiliary lubrication.
  • the nozzle involved in the invention is a variable diameter nozzle, and its main structure includes a casing, a coil spring, an elastic vertebral body and an inner cylinder, the inner cylinder is a hollow structure with a circular cross-section, the inner cylinder has an external thread, and the inner surface of the inner cylinder is plated The surface of perfluorodecyltrimethoxysilane is oleophobic.
  • One end of the outer surface of the inner cylinder is cylindrical with an external thread, the other end of the outer surface of the inner cylinder is conical, and the cylindrical end of the inner cylinder is connected to the oil supply system.
  • the conical end of the inner cylinder is connected to the elastic vertebral body;
  • the elastic vertebral body is a hollow conical cylinder, the diameter of the cavity circle at the end with the larger cross-section of the elastic vertebral body is the same as the cavity circle diameter of the inner cylinder, and the cross-section of the elastic vertebral body is the same as that of the inner cylinder.
  • the large end is bonded or embedded with the inner cylinder, and the connection is further connected, fixed and sealed with a sealing material;
  • the coil spring with memory function is inserted into the elastic vertebral body by pre-rolling, and the width of the coil spring is It is close to the length of the elastic vertebral body, and is curled along the axis in the elastic vertebral body for close to one circle without end-to-end contact;
  • the shell is in the shape of a hollow cylinder, one end of the cavity of the shell is conical, and the other end is cylindrical.
  • the cylindrical cavity part has an inner thread that matches with the outer thread of the inner cylinder, the inner cylinder is installed in the outer casing through the cooperation of the outer thread and the inner thread of the outer casing, and the inner surface of the conical cavity part of the outer casing is connected with the elastic vertebral body.
  • the outer surfaces of the shells are attached together, and the length of the conical cavity portion of the shell is shorter than the length of the elastic cone.
  • the outer casing of the present invention can move left and right relative to the inner cylinder by rotating relative to the inner cylinder.
  • the elastic vertebral body connected to the inner cylinder will be exposed, and the outer casing moving to the left will be exposed. The longer the distance is, the more the elastic vertebral body is exposed.
  • the radial size of the coil spring becomes smaller after being squeezed, and the elastic vertebral body returns to its unstretched state.
  • the aperture of the elastic cone is stretched to the maximum due to the recovery of the radial size of the inner coil spring; the free change of the aperture of the nozzle outlet can be achieved by the left and right movement of the outer casing relative to the inner cylinder.
  • the elastic vertebral body involved in this embodiment is made of fluororubber elastic material or flexible PVC elastic material, and the elastic material used is required to have good resilience and oil resistance.
  • the oil supply system involved in the invention includes a syringe barrel, a stepping motor, a lead screw, an L-shaped plate and a sliding table, the syringe barrel is connected to a nozzle, the end of the injection core is connected to the L-shaped plate, and the syringe barrel is filled with lubricating oil; It is located above the sliding table; the sliding table and the L-shaped plate are connected by screws; the lead screw and the sliding table are connected by a ball screw pair, and the stepping motor and the lead screw are connected by a coupling, and the stepping motor controls the rotation rate of the lead screw and the rotation time to control the moving speed and stroke of the sliding table, push the injection core forward through the L-shaped plate, and then realize the control of the supply rate and supply amount of the lubricating oil line.
  • the oil supply system involved in the present invention can also be a commercially available micro oil pump and control system, and the supply rate and supply amount of the lubricating oil line can be controlled by the commercially available micro oil pump and control system.
  • the water-lubricated friction pair material involved in the present invention is a friction pair with water as the lubricating medium, and has universality.
  • the present invention has the following beneficial effects:
  • the water-lubricated overload protection method of the present invention can improve the bearing capacity of the lubricating film, solve the problems of high friction coefficient and severe wear of water-lubricated materials under heavy load or impact load conditions, reduce the friction coefficient within 2s, and reach the lowest value within 10s.
  • the friction coefficient, the auxiliary lubrication effect of each lubricating oil line can reach 2 hours; the effect is rapid and the friction reduction range is large, which is unmatched by the existing lubrication technology;
  • variable diameter nozzle structure involved in the present invention can control the diameter of the sprayed oil line by adjusting the inner diameter of the nozzle according to specific working conditions; the variable diameter nozzle structure adopts materials that do not rust in water, and the inner surface is subjected to local oleophobic treatment , No oleophobic treatment is performed at the outlet, and the lubricating oil flows from the area after the oleophobic treatment to the outlet area without the oleophobic treatment, which will increase the pressure of the lubricating oil at the outlet and make the sprayed lubricating oil in the water.
  • the shape of the oil line is more stable, and the nozzle outlet points to the moving parts in the friction pair, which helps the lubricating medium to be drawn into the contact area by the movement of the parts;
  • the supply of the lubricating oil line involved in the present invention is a short-term trace supply, which is green and environmentally friendly, and the pollution can be ignored;
  • the problem of poor lubrication of water-lubricated materials under sudden load conditions is solved, and auxiliary lubrication is carried out for sudden overload conditions to ensure that the water-lubricated friction pair materials remain well under sudden conditions.
  • the lubricating state of the machine reduces material wear, prolongs the service life, and greatly improves the operation stability; the effect is rapid, the structure is simple, the design concept is ingenious, the manufacturing cost is low, the application environment is friendly, and the market prospect is broad.
  • FIG. 1 is a schematic diagram of the structure and principle of the water-lubricated overload protection lubricating oil line supply system according to Embodiment 1 of the present invention.
  • FIG. 2 is a schematic diagram of the state principle of the small-diameter structure of the nozzle outlet involved in the present invention
  • FIG. 3 is a schematic diagram of the principle of the large-diameter structure state of the nozzle outlet involved in the present invention
  • FIG. 4 is a schematic diagram of the structure principle of the coil spring involved in the present invention.
  • FIG. 5 is a schematic diagram of the oleophobic treatment of FAS (perfluorodecyltrimethoxysilane) plating on the inner surface of the nozzle involved in the present invention.
  • Area A is the inner surface of the inner cylinder after being modified by FAS;
  • area B is the elastic cone without FAS modification. body surface;
  • Fig. 6 is the friction coefficient of 316 stainless steel ring and nitrile rubber block under the heavy load condition of 350N involved in the present invention as a function of speed variation curve;
  • Figure 7 shows the results of the 0.5h friction experiment at 350N, 50r/min, and pure water for 10min, supplying 100 ⁇ L of lubricating oil to the lubricating oil line, and the supply rate being 10 ⁇ L/s;
  • Figure 8 shows the results of a 3-hour long-rubbing experiment involving 350N, 50r/min and pure water for 10min, supplying 100 ⁇ L of lubricating oil to the lubricating oil line, and a supply rate of 10 ⁇ L/s.
  • This embodiment relates to a water-lubricated overload protection method.
  • the method is that when the water-lubricated friction pair is overloaded, lubricating oil enters the water-lubricated friction pair in the form of an oil line in water to perform lubricating oil auxiliary lubrication, so as to protect the water-lubricated friction pair.
  • the purpose of the friction pair material taking the ring block testing machine as an example, the specific steps are described as follows:
  • the ring block testing machine According to the load W between the water-lubricated friction pair materials and the viscosity ⁇ of the lubricating medium, use the ring block testing machine to measure the curve of the friction coefficient changing with the speed of the steel ring.
  • the specific measurement method is: use the common water-lubricating material nitrile rubber As the counter-grinding block 1, its surface roughness is 0.4; as the counter-grinding ring 2, the surface roughness of 316 stainless steel is 0.3; tap water is used as a lubricating medium to immerse the friction pair, and the friction pair load is set to a heavy load of 350N.
  • the friction coefficient between the friction pairs under the condition of pure water lubrication at the rotating speed, the curve of the friction coefficient changing with the rotating speed of the grinding ring 2 is drawn from the measured data, as shown in Figure 6, because of the large load, even if the rotating speed is If the friction coefficient is increased within a large range, the corresponding friction coefficient is still very high; here, the friction coefficient is set to 0.07 as the critical value of the friction coefficient, and the rotation speed of the anti-grinding ring 2 is selected as 50r/min as the typical test condition. It can be seen that the friction coefficient at this time is Very high, the friction pairs are in a state of mixed lubrication or even boundary lubrication, and the lubrication state is relatively poor;
  • lubricating oil line supply system includes nozzle 3 and oil supply system, nozzle 3 is installed as close as possible to the contact area, the lubricating medium passing through nozzle 3 will be ejected in the form of continuous oil line, and nozzle 3 is directed to move the surface of the friction parts, so that the lubricating oil avoids the reverse flow area as much as possible, the inner surface of the nozzle 3 near the outlet (area B) does not do oleophobic treatment, and the inner surface of the nozzle far from the outlet (area A) is plated with FAS (perfluorodecyl) Trimethoxysilane) for surface oleophobic treatment, the lubricating oil flows through the oleophobic treated area A to the B area without oleophobic treatment, which will increase the pressure of the lubricating oil at the outlet and make the sprayed lubricating oil in the water.
  • FAS perfluorodecyl
  • the friction pair can still maintain a low level of friction coefficient for a long time; as shown in Figure 8, under the same conditions, the friction time is extended to 3h, even if it always runs under a heavy load of 350N, a single trace oil line
  • the auxiliary lubrication effect can last for more than 2 hours, and its effect is very long-lasting, which can significantly improve the bearing capacity of the bearing and achieve the purpose of protecting the water-lubricating material.
  • Step S1 involved in this embodiment also includes wiping all the parts inside the cavity of the ring block testing machine with dust-free paper dipped in absolute ethanol and petroleum ether successively to ensure that the inside of the cavity is clean; For leveling, adjust the bolts to make the opposite grinding blocks on the clamp fit well with the outer surface of the steel ring during operation to ensure that there is no inclination of the wear scars; by ensuring that the water inlet flow of the cavity is the same as the water outlet flow, to maintain The liquid level in the cavity remains unchanged; the control of the water flow in and out is realized by commercially available flow adjustment equipment.
  • the lubricating oil sprayed in the water environment exists in the form of oil lines in the water, and its main structure includes a nozzle and an oil supply system.
  • the main structure of the nozzle includes a casing 11, a coil spring 12.
  • the elastic vertebral body 13 and the inner cylinder 14, the inner cylinder 14 is a hollow structure with a circular cross section, the inner cylinder 14 has an external thread, and the inner surface (A area) of the inner cylinder 14 is plated with FAS (perfluorodecyl trimethoxyl base silane) for surface oleophobic treatment, one end of the outer surface of the inner cylinder 14 is cylindrical with an external thread, the other end of the outer surface of the inner cylinder 14 is conical, the cylindrical end of the inner cylinder 14 is connected to the oil supply system, and the inner cylinder 14 is connected to the oil supply system.
  • FAS perfluorodecyl trimethoxyl base silane
  • the conical end of 14 is connected to the elastic vertebral body 13;
  • the elastic vertebral body 13 is a hollow conical cylinder, and the diameter of the cavity circle of the large end (tail end) of the elastic vertebral body 13 is the same as the diameter of the cavity circle of the inner cylinder 14 , the tail end of the elastic vertebral body 13 is bonded or embedded fixedly connected with the inner cylinder 14, and the joint is further connected, fixed and sealed with a sealing material;
  • the coil spring 12 with memory function is inserted into the elastic vertebral body by pre-rolling In the body 13, the width of the coil spring 12 is close to the length of the elastic vertebral body 13, and in the elastic vertebral body 13, it is curled approximately one circle along the axis without end-to-end contact;
  • One end of the cavity is conical, and the other end is cylindrical.
  • the cylindrical cavity part of the outer casing 11 has an inner thread which is matched with the outer thread of the inner cylinder 14.
  • the inner surface of the conical cavity portion of the housing 11 is attached to the outer surface of the elastic vertebral body 13, and the length of the conical cavity portion of the housing 11 is shorter than that of the elastic vertebral body 13; the housing 11 can By rotating relative to the inner cylinder 14, the left and right movement relative to the inner cylinder 14 is realized.
  • the elastic vertebral body 13 connected to the inner cylinder 14 is exposed, and the outer casing 11 moves to the left. The longer the distance is, the more the elastic vertebral body 13 is exposed.
  • the elastic vertebral body 13 When the outer casing 11 moves to the left at the maximum distance, the radial size of the coil spring becomes smaller after being squeezed, and the elastic vertebral body 13 returns to the state where it is not stretched.
  • the diameter of the inner hole is the smallest, and the coil spring 12 in it is in a curled state with a smaller radial size; when the outer casing 11 moves to the right relative to the inner cylinder 14, as shown in FIG. 4, the elastic cone 13 is in the outer casing 11.
  • the space becomes larger, the pre-rolled coil spring 12 tends to restore the original radial size, and the radial size becomes larger, so that the elastic vertebral body 13 is enlarged, and its inner hole diameter, that is, the diameter of the nozzle outlet, will also be enlarged.
  • the elastic vertebral body 13 involved in this embodiment is made of fluororubber elastic material, and other commercially available elastic materials such as rubber and flexible PVC can also be used, and the elastic material used is required to have good resilience and oil resistance.
  • the purpose of inserting the coil spring 12 into the elastic vertebral body 13 involved in this embodiment is to ensure that the outlet of the elastic vertebral body 13 is always in a stable circle, because if the elastic cone 13 is simply used to control the aperture of the outlet, when the aperture changes Small, that is, when the elastic cone 13 is compressed, the shape of the hole cannot maintain a stable circular shape.
  • the inner hole tends to be wrinkled, and the greater the degree of compression of the elastic cone 13, The more obvious the inner hole is wrinkled, which leads to problems such as uneven oil flow outflow and unstable shape; on the contrary, from the mechanical analysis, when the inner hole of the elastic cone 13 is enlarged, it will be easier and more stable to keep the inner hole as Therefore, the force of expansion and recovery after the coil spring 12 is pre-rolled into the elastic cone 13 is used to expand the elastic cone 13, and the recovery of the coil spring 12 makes the outlet aperture become a circle with a larger diameter, and when When the coil spring 12 is compressed and curled, the elastic cone 13 gradually returns to the initial state that is not stretched, and the aperture of the outlet becomes smaller.
  • the oil supply system includes a syringe barrel 4, a stepping motor 8, a lead screw 9, an L-shaped plate 6 and a sliding table 7, the syringe barrel 4 is connected to the nozzle 3, the end of the injection core 5 is connected to the L-shaped plate 6, and the syringe barrel 4 is connected to the L-shaped plate 6.
  • the L-shaped plate 6 is located above the sliding table 7; the sliding table 7 and the L-shaped plate 6 are connected by screws; 9 is connected by a coupling, the stepping motor 8 controls the rotation rate and rotation time of the lead screw 9 to control the moving speed and stroke of the slide table 7, and pushes the injection core 5 forward through the L-shaped plate, thereby realizing the lubricating oil line supply rate and For the control of the supply amount, the lubricating oil is sprayed out through the nozzle 3, and the sprayed lubricating oil exists in the form of an oil line.
  • the outlet diameter of the nozzle involved in this embodiment is 0.4 mm when spraying lubricating oil.
  • the lubricating oil involved in this embodiment is emulsified oil, which is prepared from vegetable oil or other environmentally friendly lubricating oil as base oil. Access to the contact zone for assisted lubrication.
  • variation range of the diameter of the nozzle 3 involved in this embodiment is determined by the actual taper and size of the threaded housing and the elastic material.
  • water-lubricated overload lubricating oil line protection technology involved in this embodiment is universal.
  • the inner cylinder of the nozzle involved in this embodiment utilizes local oleophobic treatment to improve the surface oleophobic treatment agent of oil line stability, including but not limited to FAS.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Lubricants (AREA)
  • Sliding-Contact Bearings (AREA)
  • Application Of Or Painting With Fluid Materials (AREA)

Abstract

一种水润滑的过载保护方法，当水润滑摩擦副的摩擦系数超过临界值时，通过润滑油线供给系统将润滑油在水中以油线的形态进入水润滑摩擦副进行润滑油辅助润滑，产生的油膜取代脆弱的水膜进行承载，实现水润滑的过载保护；每次润滑油线的辅助润滑效果达到2小时。该方法结构简单、起效迅速、减摩幅度大，解决了水润滑材料在载荷突变工况下润滑不良的难题，针对突发过载工况进行辅助润滑，保证了水润滑摩擦副材料在突发工况下保持良好的润滑状态，减少了材料磨损，延长了使用寿命、大大提高了运转稳定性；且制造成本低，应用环境友好，市场前景广阔。还公开了一种水润滑的过载保护润滑油线供给系统。

Description

一种水润滑的过载保护润滑油线供给系统及过载保护方法 技术领域：
本发明属于水润滑技术领域，具体涉及一种水润滑的过载保护润滑油线供给系统及过载保护方法，当水润滑摩擦副过载时，利用临时提供的润滑油线进入水润滑摩擦副，提高水润滑的承载力，减小摩擦，降低磨损，保护摩擦副材料。
背景技术：
润滑油粘度大、承载能力高，已经广泛应用于各类装备的润滑中。然而随着人类环保意识逐渐增强和环境立法的完善，润滑油引起的环境污染以及能源不可再生问题使得人们把更多的目光转向环保型的润滑介质，而水作为典型的环保型润滑介质越来越受重视。水润滑具有结构简单、绿色清洁、价格低廉的巨大优点，适用于船舶艉轴、水泵、水轮机以及矿山、农业机械等领域，已有几十年的应用历史。但水具有粘度低、成膜能力差等缺点，在实际应用中始终存在问题。水润滑抗干扰能力差，当外界工况发生变化，比如载荷突然升高，就很容易造成润滑失效，而水润滑轴承的应用场合往往处于复杂工况下，比如船舶螺旋桨的悬臂布置产生的非均匀载荷、轴系振动和水流/洋流等的短时载荷冲击，容易使接触区水膜崩溃、失去承载能力，导致轴承磨损加剧、甚至失效。
人们从轴承结构、材料等方面进行研究，设计了矩形、圆弧形、三角形、螺旋形的表面沟槽，研制出丁腈橡胶、赛龙、飞龙、安高等各种系列的产品以提高耐磨性，然而都没有改变水作为润滑剂的固有缺陷。水膜承载力低、抗干扰性差，当载荷出现波动时，润滑状态容易从弹流润滑变为边界润滑甚至干摩擦，当载荷波动消失后，水膜可能无法重建，不能恢复到正常的润滑状态，继而导致震动、噪声、磨损失效等问题。一旦变为干摩擦状态，往往必须要在几十秒内解决润滑不良的问题，不然就会导致烧瓦。比如赛龙水润滑材料在无水工况下只能运行30-60s，在水中运行温度超过60℃就会水解；安高水润滑材料在无水工况下运行不能超过2分钟。这些已算是水润滑材料中的佼佼者。因此，为了提高水润滑在突发工况下的润滑稳定性和抗干扰能力，有必要采取一种新方法，来迅速提高载荷突变时摩擦副间润滑膜的承载力、保证润滑状态的稳定性。
如前所述油润滑具有粘度高、承载能力强等优点，且摩擦副中实际参与润滑的润滑油量很小。现急需设计一种水润滑的过载保护润滑油线供给系统，实现水润滑的过载保护，将水润滑与微量油润滑结合在一起，当水润滑条件下遇到重载、振动、冲击等突发工况时，将微量的润滑油以油线的形式按一定速度连续注入接触区，产生附加的油膜承载力，提高润滑系 统的稳定性、维持摩擦副间良好的润滑状态，帮助度过恶劣工况，而且此喷嘴可以调节喷嘴孔径以控制喷出油线的直径。需要指出的是，短时注入微量的润滑油对环境的污染可以忽略不计，若所用为植物油或其它生物降解率高的环保型润滑油，其市场前景会十分广阔。
发明内容：
本发明的目的在于克服现有技术的缺陷，寻求设计一种水润滑的过载保护润滑油线供给系统和过载保护方法，在水润滑过载时提供润滑油线保护，当水润滑重载或变载时，控制喷嘴喷出微量的润滑油，使其在入口区水中以油线的形式按一定速度进入接触区，产生的油膜取代脆弱的水膜进行承载，使得在恶劣工况下摩擦副间仍然保持良好的润滑状态，保证摩擦副零件的正常工作，而且此喷嘴不用替换喷头，可以自由调节喷嘴孔径，控制喷出油线的直径。
为达到上述目的，本发明提供一种水润滑的过载保护方法，该方法是在水润滑摩擦副过载时，通过润滑油线供给系统将润滑油在水中以油线的形态进入水润滑摩擦副进行润滑油辅助润滑，达到保护水润滑摩擦副材料的目的，具体工艺步骤包括：
S1、根据实际工况下水润滑摩擦副材料间的载荷W和润滑介质的粘度μ，利用市售的相关摩擦磨损仪器，测量摩擦系数随转速变化的曲线；水润滑摩擦副经常处于混合润滑的工况下，当遇到载荷冲击时水膜难以提供足够的承载力，摩擦副材料之间容易出现直接接触，摩擦系数会迅速升高，导致磨损严重；因此，以所测得的摩擦系数曲线为参考，来设定磨擦系数临界值；当水润滑摩擦副的摩擦系数超过临界值时，将润滑油以油线的形式进入摩擦副间进行辅助润滑，产生的油膜取代脆弱的水膜进行承载，实现水润滑的过载保护；
S2、安装润滑油线供给系统，润滑油线供给系统包括喷嘴和供油系统，喷嘴外接供油系统，通过供油系统设置润滑油的喷出速度和供给时间；喷嘴安装在距离水润滑摩擦副接触区很近的位置，且喷嘴出口指向运动的摩擦零件表面，以避免摩擦副入口的逆流区，确保油线按一定的速度进入接触区；喷嘴采用水中不生锈的材料，喷腔横截面为圆形；
S3、实时监测工作状态下的水润滑摩擦副的载荷和摩擦系数，当水润滑摩擦副载荷在正常情况，摩擦系数低于临界值时，以水作为唯一的润滑介质，对摩擦副材料进行正常润滑；当水润滑摩擦副过载，摩擦系数超过临界值时，开启供油系统，润滑油按照设定的喷出速度和供给时间经喷嘴连续喷出，喷出后的润滑油在水中以稳定的油线形式突破摩擦副入口的逆流区，随着摩擦副零件的运动卷入接触区，其产生的油膜将取代脆弱的水膜进行承载，使得原来存在局部直接接触情况的两个零件之间的间隙增大，即润滑膜的厚度增加，润滑膜承载力提高，摩擦系数迅速下降，摩擦副零件之间不再直接接触，使得恶劣工况下摩擦副间保持良好的润滑状态，大大降低水润滑材料的磨损；
S4、在水润滑摩擦副工作状态下，只要摩擦系数超过临界值，就向摩擦副间进行润滑油线供给，以降低摩擦系数，维持良好的润滑状态；当第一次向摩擦副间供给润滑油线后，摩擦系数再次超过临界值时，说明第一次供给的微量油线润滑效果减弱或消失而过载依然存在，此时对摩擦副间进行第二次润滑油线供给，降低摩擦系数，以维持其良好的润滑状态；当摩擦系数又一次超过临界值时，说明第二次供给的微量油线润滑效果减弱或消失而过载依然存在，此时对摩擦副进行第三次微量润滑油线供给；以此类推，以维持其良好的润滑状态；过载工况属于突发意外工况，往往持续时间短暂，并不会持久，只有几秒或几分钟，而每次微量润滑油线的辅助润滑效果能够达到2小时，因此通常只需供给一次便足够；
S5、当载荷恢复正常，摩擦系数低于临界值时，摩擦副以水作为唯一的润滑介质，进行正常润滑；而接触区内残余润滑油因表面张力较低的缘故会黏附在接触副表面形成微油池，并在较长时间内稳定存在，发挥良好的润滑作用，使得在纯水润滑条件下摩擦副间仍然能够长时间保持低摩擦系数水平，达到保护水润滑摩擦副材料的目的。
本发明涉及的步骤S1的摩擦系数曲线的具体测量方法为：实验所用摩擦副的材料、结构、尺寸等相关参数均与实际工况下的摩擦副参数一致，因海水、河水等不同水域的水成分不同对摩擦磨损的影响也不同，因此取实际工况下水域的水作为润滑介质浸没摩擦副，测量不同转速下摩擦副的摩擦系数，由测得的数据绘制出其摩擦系数随钢环转速变化的曲线。
本发明涉及的喷嘴的内表面进行局部疏油处理，润滑油进口处的内表面做疏油处理，出口处内表面不做疏油处理，润滑油由做过表面疏油处理的进口区域流至未做过表面疏油处理的出口区域，提高了润滑油在出口处的压力，使喷出的润滑油在水中以油线的形态存在更稳定。
本发明涉及的润滑油为乳化油，由环保型润滑油为基础油配制而成，从喷嘴喷出时有利于保持油线状态，有利于突破摩擦副入口处的逆流区，从而进入接触区实现辅助润滑。
本发明涉及的喷嘴为变径喷嘴，其主体结构包括外壳、卷簧、弹性椎体和内筒，内筒为横截面为圆形的中空结构，内筒具有外螺纹，内筒的内表面镀全氟癸基三甲氧基硅烷做表面疏油处理，内筒的外表面一端为具有外螺纹的圆柱形，内筒的外表面另一端为圆锥形，内筒的圆柱形一端连接供油系统，内筒的圆锥形一端连接弹性椎体；弹性椎体为中空圆锥柱体，弹性椎体的横截面大的一端的空腔圆直径与内筒的空腔圆直径相同，弹性椎体的横截面大的一端与内筒粘合式或嵌入式固定连接，连接处用密封材料进行进一步的连接固定和密封；具有记忆功能的卷簧通过预卷曲的方式插在弹性椎体内，卷簧的宽度接近弹性椎体的长度，并在弹性椎体内沿着轴线卷曲接近一圈但不会首尾接触；外壳为空腔圆柱体形状，外壳的空腔一端为圆锥形，另一端为圆柱形，外壳的圆柱形空腔部分具有与内筒的外螺纹相配合的内螺 纹，内筒通过外螺纹与外壳的内螺纹的配合安装在外壳内，外壳的圆锥形空腔部分的内表面与弹性椎体的外表面贴附在一起，外壳的圆锥形空腔部分的长度比弹性椎体的长度短。
本发明涉及的外壳能够通过相对于内筒旋转实现相对于内筒的左右移动，当外壳相对于内筒向左移动时，与内筒连接的弹性椎体便会暴露出来，外壳向左移动的距离越长，弹性椎体暴露出来的越多，外壳向左移动的距离最大时，卷簧受到挤压径向尺寸变小，而弹性椎体恢复到未被撑大的状态，其内孔直径为最小，其内的卷簧为径向尺寸变小的卷曲状态；当外壳相对于内筒向右移动时，弹性椎体在外壳内的空间变大，预卷曲的卷簧有恢复原来径向尺寸的趋势而使径向尺寸变大，使得弹性椎体被撑大，其内孔直径即喷嘴出口的孔径也会被撑大，使得喷嘴喷出的润滑油线的直径相应变大，当外壳向右移动的距离达到最大时，弹性椎体的孔径因内部卷簧径向尺寸的恢复被撑开到最大；通过外壳相对于内筒的左右移动能够实现喷嘴出口孔径的自由变化。
本实施例涉及的弹性椎体采用氟橡胶弹性材料或柔性PVC弹性材料，采用的弹性材料要求有良好的回弹性和耐油性。
本发明涉及的供油系统包括注射器筒、步进电机、丝杠、L型板和滑台，注射器筒连接喷嘴，注射器芯的末端与L型板连接，注射器筒内装有润滑油；L型板位于滑台上方；滑台与L型板通过螺钉连接；丝杠与滑台之间通过滚珠丝杠副连接，步进电机与丝杠通过联轴器连接，步进电机控制丝杠的转动速率和转动时间来控制滑台的移动速度和行程，通过L型板推动注射器芯前进，进而实现润滑油线供给速率和供给量的控制，润滑油经过喷嘴喷出，喷出后的润滑油以油线形态存在。
本发明涉及的供油系统还能够是市售的微量油泵和控制系统，通过市售的微量油泵和控制系统来控制润滑油线的供给速率和供给量。
本发明涉及的水润滑摩擦副材料为以水作为润滑介质的摩擦副，具有普适性。
本发明与现有技术相比，取得的有益效果如下：
1.本发明的水润滑的过载保护方法能够提高润滑膜的承载力、解决重载或冲击载荷工况下水润滑材料摩擦系数高、磨损剧烈的问题，在2s内降低摩擦系数，10s内达最低摩擦系数，每次润滑油线的辅助润滑效果可以达到2小时；起效迅速、减摩幅度大，是现有润滑技术所不能比拟的；
2.本发明涉及的变径喷嘴结构，可以针对具体工况，通过调节喷嘴内径来控制喷出油线的直径大小；变径喷嘴结构采用水中不生锈的材料，内表面进行局部疏油处理，出口处不做疏油处理，润滑油由进行过疏油处理后的区域流至未进行疏油处理的出口区域，会提高润滑油在出口处的压力、使喷出的润滑油在水中以油线的形态存在更稳定，喷嘴出口指向摩擦副 中运动的零件，有助于润滑介质借助零件的运动卷入接触区；
3.本发明涉及的润滑油线供给为短时微量供给，绿色环保，污染可以忽略不计；
4.通过设计润滑油线喷嘴，解决了水润滑材料在载荷突变工况下润滑不良的难题，针对突发过载工况进行辅助润滑，保证了水润滑摩擦副材料在突发工况下保持良好的润滑状态，减少了材料磨损，延长了使用寿命、大大提高了运转稳定性；起效迅速、结构简单，设计构思巧妙，制造成本低，应用环境友好，市场前景广阔。
附图说明：
图1为本发明涉及的实施例1的水润滑的过载保护润滑油线供给系统的结构原理示意图。
图2为本发明涉及的喷嘴出口小口径结构状态原理示意图；
图3为本发明涉及的喷嘴出口大口径结构状态原理示意图；
图4为本发明涉及的卷簧结构原理示意图；
图5为本发明涉及的喷嘴内表面镀FAS(全氟癸基三甲氧基硅烷)疏油处理示意图，A区为经过FAS修饰后的内筒内表面；B区为未经FAS修饰的弹性椎体内表面；
图6为本发明涉及的350N重载条件下，316不锈钢钢环与丁腈橡胶块对磨的摩擦系数随速度变化曲线；
图7为本发明涉及的350N、50r/min下，纯水条件下对磨10min后，供给100μL润滑油线，供给速率为10μL/s的0.5h摩擦实验结果；
图8为本发明涉及的350N、50r/min下，纯水条件下对磨10min后，供给100μL润滑油线，供给速率为10μL/s的3h长摩实验结果。
具体实施方式：
下面通过具体实施例并结合附图对本发明进行详细说明。
实施例1
本实施例涉及一种水润滑的过载保护方法，该方法是在水润滑摩擦副过载时，通过将润滑油在水中以油线的形态进入水润滑摩擦副进行润滑油辅助润滑，达到保护水润滑摩擦副材料的目的，以环块试验机为例，具体步骤说明如下：
S1、根据水润滑摩擦副材料间的载荷W和润滑介质的粘度μ，用环块试验机测得摩擦系数随钢环转速变化的曲线，具体测量方法为：用常见的水润滑材料丁腈橡胶作为对磨块1，其表面粗糙度为0.4；316不锈钢作为对磨环2，其表面粗糙度为0.3；自来水作为润滑介质浸没摩擦副，将摩擦副载荷设为350N的重载载荷，测量不同转速下纯水润滑条件下摩擦副间的摩擦系数，由测得的数据绘制出其摩擦系数随对磨环2转速变化的曲线，如图6所示，因为载荷较大的缘故，即便转速在较大范围内提高，对应的摩擦系数仍然很高；这里设定摩擦系数为0.07作 为摩擦系数临界值，选取对磨环2转速为50r/min作为典型测试条件，可以看出此时的摩擦系数很高，摩擦副间处于混合润滑甚至边界润滑状态，润滑状态比较恶劣；
S2、选取载荷350N、转速为50r/min，考虑磨合过程中摩擦系数可能不稳定，可能会出现下降的情况，为了排除是由于磨合过程中摩擦系数不稳定导致的摩擦系数下降，先使丁腈橡胶块与316不锈钢环对磨10min，使摩擦系数稳定，如图7所示，发现稳定后的摩擦系数值超过0.07这一临界值，因此朝接触区供给润滑油线进行辅助润滑，总共对磨时间30min；润滑油线供给系统包括喷嘴3和供油系统，喷嘴3安装在距接触区尽可能近的位置，通过喷嘴3的润滑介质会以连续油线的形式喷出，并且喷嘴3指向运动的摩擦零件表面，使得润滑油尽量避过逆流区，喷嘴3内表面靠近出口的地方(B区)不做疏油处理，喷嘴内表面远离出口的地方(A区)镀FAS(全氟癸基三甲氧基硅烷)做表面疏油处理，润滑油通过疏油处理后的A区流至未进行疏油处理的B区，会提高润滑油在出口处的压力、使喷出的润滑油在水中以油线的形态存在更稳定；通过供油系统设定油线按10μL/s的速度喷出，并进入接触区，设定供给时间为10s，累计供给100μL润滑油，10s后停止供给；润滑油线进入接触区后，其产生的油膜将取代脆弱的水膜进行承载，使得原来存在局部直接接触情况的两个零件之间的间隙增大，即润滑膜的厚度增加，润滑膜承载力提高，摩擦系数迅速下降，摩擦副零件之间不再直接接触，润滑膜承载力提高，摩擦系数会迅速下降，使得重载工况下摩擦副间可以保持良好的润滑状态，其结果如图7所示；
S3、当转为纯水润滑后，接触区内残余润滑油因表面张力较低的缘故会黏附在接触副表面形成微油池，并在较长时间内稳定存在，发挥良好的润滑作用，使得在纯水润滑条件下摩擦副间仍然可以长时间保持低摩擦系数水平；如图8所示，相同的条件将对磨时间延长至3h，即便始终在350N重载下运行，单次微量油线的辅助润滑效果可以持续2小时之上，其效果非常持久，能够明显提高轴承的承载力，达到保护水润滑材料的目的。
本实施例涉及的步骤S1还包括对环块试验机腔体内部所有零件先后用无尘纸蘸取无水乙醇、石油醚进行擦拭，确保腔体内部干净清洁；对环块试验机块夹进行调平，通过调节螺栓使工作时夹上的对磨块与钢环外表面很好地贴合，确保不出现磨痕倾斜的情况；通过保证腔体的进水流量与出水流量相同，来保持腔体内液位不变；其进出水流量的控制通过市售的流量调节设备实现。
本实施例涉及的润滑油线供给系统，其在水环境中喷射出的润滑油在水中以油线的形态存在，其主体结构包括喷嘴和供油系统，喷嘴的主体结构包括外壳11、卷簧12、弹性椎体13和内筒14，内筒14为横截面为圆形的中空结构，内筒14具有外螺纹，内筒14的内表面(A区)镀FAS(全氟癸基三甲氧基硅烷)做表面疏油处理，内筒14的外表面一端为具有外螺纹的圆柱 形，内筒14的外表面另一端为圆锥形，内筒14的圆柱形一端连接供油系统，内筒14的圆锥形一端连接弹性椎体13；弹性椎体13为中空圆锥柱体，弹性椎体13的横截面大的一端(尾端)的空腔圆直径与内筒14的空腔圆直径相同，弹性椎体13的尾端与内筒14粘合式或嵌入式固定连接，连接处用密封材料进行进一步的连接固定和密封；具有记忆功能的卷簧12通过预卷曲的方式插在弹性椎体13内，卷簧12的宽度接近弹性椎体13的长度，并在弹性椎体13内沿着轴线卷曲接近一圈但不会首尾接触；外壳11为空腔圆柱体形状，外壳11的空腔一端为圆锥形，另一端为圆柱形，外壳11的圆柱形空腔部分具有与内筒14的外螺纹相配合的内螺纹，内筒14通过外螺纹与外壳11的内螺纹的配合安装在外壳11内，外壳11的圆锥形空腔部分的内表面与弹性椎体13的外表面贴附在一起，外壳11的圆锥形空腔部分的长度比弹性椎体13的长度短；外壳11能够通过相对于内筒14旋转实现相对于内筒14的左右移动，当外壳11相对于内筒14向左移动时，与内筒14连接的弹性椎体13便会暴露出来，外壳11向左移动的距离越长，弹性椎体13暴露出来的越多，外壳11向左移动的距离最大时，卷簧受到挤压径向尺寸变小，而弹性椎体13恢复到未被撑大的状态，其内孔直径为最小，其内的卷簧12为径向尺寸变小的卷曲状态；当外壳11相对于内筒14向右移动时，如图4所示，弹性椎体13在外壳11内的空间变大，预卷曲的卷簧12有恢复原来径向尺寸的趋势而使径向尺寸变大，使得弹性椎体13被撑大，其内孔直径即喷嘴出口的孔径也会被撑大，使得喷嘴喷出的润滑油线的直径相应变大，当外壳11向右移动的距离达到最大时，弹性椎体13的孔径因内部卷簧12径向尺寸的恢复被撑开到最大；通过外壳11相对于内筒14的左右移动能够实现喷嘴出口孔径的自由变化。
本实施例涉及的弹性椎体13采用氟橡胶弹性材料，亦可采用其他种类的橡胶、柔性PVC等市售的弹性材料，采用的弹性材料要求有良好的回弹性和耐油性。
本实施例涉及的将卷簧12插在弹性椎体13内的目的是为了保证弹性椎体13的出口处始终为稳定的圆形，因为如果单纯利用弹性锥体13控制出口孔径，当孔径变小即弹性体锥体13被压缩时，孔的形状不能保持稳定的圆形，随着弹性锥体13被压缩，其内孔往往会产生褶皱，并且弹性椎体13被压缩的程度越大，内孔褶皱越明显，导致油线流出不均匀、形状不稳定等问题；相反地，从力学上分析，弹性锥体13内孔被撑大时会更容易、也能更稳定地保持内孔为圆形，因此采用了利用卷簧12预卷曲装入弹性锥体13后膨胀回复的力来撑大弹性锥体13，卷簧12的回复使出口孔径变为直径更大的圆形，而当卷簧12受压缩卷曲时，弹性锥体13则逐渐恢复为未被撑大的初始状态，出口孔径会变小。
所述供油系统包括注射器筒4、步进电机8、丝杠9、L型板6和滑台7，注射器筒4连接喷嘴3，注射器芯5的末端与L型板6连接，注射器筒4内装有润滑油；L型板6位于滑台7上方；滑台7与L型板6通过螺钉连接；丝杠9与滑台7之间通过滚珠丝杠副连接，步进电机8与丝杠9通过联 轴器连接，步进电机8控制丝杠9的转动速率和转动时间来控制滑台7的移动速度和行程，通过L型板推动注射器芯5前进，进而实现润滑油线供给速率和供给量的控制，润滑油经过喷嘴3喷出，喷出后的润滑油以油线形态存在。
本实施例涉及的喷嘴在喷射润滑油时的出口直径是0.4mm。
本实施例涉及的润滑油为乳化油，由植物油或其它环保型润滑油为基础油配制而成，从喷嘴喷出时有利于保持油线状态，有利于突破摩擦副入口处的逆流区，从而进入接触区实现辅助润滑。
进一步地，本实施例涉及的喷嘴3的直径的变化范围由螺纹外壳和弹性材料的实际锥度与尺寸等决定。
进一步地，本实施例涉及的水润滑过载的润滑油线保护技术，包括但不限于本实施例所使用的水润滑材料，具有普适性。
进一步地，本实施例涉及的喷嘴的内筒利用局部疏油处理来提高油线稳定性的表面疏油处理试剂，包括但不限于FAS。

Claims (9)

  1. 一种水润滑的过载保护方法，其特征在于，该方法是在水润滑摩擦副过载时，通过润滑油线供给系统将润滑油在水中以油线的形态进入水润滑摩擦副进行润滑油辅助润滑，达到保护水润滑摩擦副材料的目的，具体工艺步骤包括：
    S1、根据实际工况下水润滑摩擦副材料间的载荷W和润滑介质的粘度μ，利用市售的相关摩擦磨损仪器，测量摩擦系数随转速变化的曲线；水润滑摩擦副经常处于混合润滑的工况下，当遇到载荷冲击时水膜难以提供足够的承载力，摩擦副材料之间容易出现直接接触，摩擦系数会迅速升高，导致磨损严重；因此，以所测得的摩擦系数曲线为参考，来设定磨擦系数临界值；当水润滑摩擦副的摩擦系数超过临界值时，将润滑油以油线的形式进入摩擦副间进行辅助润滑，产生的油膜取代脆弱的水膜进行承载，实现水润滑的过载保护；
    S2、安装润滑油线供给系统，润滑油线供给系统包括喷嘴和供油系统，喷嘴外接供油系统，通过供油系统设置润滑油的喷出速度和供给时间；喷嘴安装在距离水润滑摩擦副接触区很近的位置，且喷嘴出口指向运动的摩擦零件表面，以避免摩擦副入口的逆流区，确保油线按一定的速度进入接触区；喷嘴采用水中不生锈的材料，喷腔横截面为圆形；
    S3、实时监测工作状态下的水润滑摩擦副的载荷和摩擦系数，当水润滑摩擦副载荷在正常情况，摩擦系数低于临界值时，以水作为唯一的润滑介质，对摩擦副材料进行正常润滑；当水润滑摩擦副过载，摩擦系数超过临界值时，开启供油系统，润滑油按照设定的喷出速度和供给时间经喷嘴连续喷出，喷出后的润滑油在水中以稳定的油线形式突破摩擦副入口的逆流区，随着摩擦副零件的运动卷入接触区，其产生的油膜将取代脆弱的水膜进行承载，使得原来存在局部直接接触情况的两个零件之间的间隙增大，即润滑膜的厚度增加，润滑膜承载力提高，摩擦系数迅速下降，摩擦副零件之间不再直接接触，使得恶劣工况下摩擦副间保持良好的润滑状态，大大降低水润滑材料的磨损；
    S4、在水润滑摩擦副工作状态下，只要摩擦系数超过临界值，就向摩擦副间进行润滑油线供给，以降低摩擦系数，维持良好的润滑状态；当第一次向摩擦副间供给润滑油线后，摩擦系数再次超过临界值时，说明第一次供给的微量油线润滑效果减弱或消失而过载依然存在，此时对摩擦副间进行第二次润滑油线供给，降低摩擦系数，以维持其良好的润滑状态；当摩擦系数又一次超过临界值时，说明第二次供给的微量油线润滑效果减弱或消失而过载依然存在，此时对摩擦副进行第三次微量润滑油线供给；以此类推，以维持其良好的润滑状态；过载工况属于突发意外工况，往往持续时间短暂，并不会持久，只有几秒或几分钟，而每次微量润滑油线的辅助润滑效果能够达到2小时，因此通常只需供给一次便足够；
    S5、当载荷恢复正常，摩擦系数低于临界值时，摩擦副以水作为唯一的润滑介质，进行正常润滑；而接触区内残余润滑油因表面张力较低的缘故会黏附在接触副表面形成微油池， 并在较长时间内稳定存在，发挥良好的润滑作用，使得在纯水润滑条件下摩擦副间仍然能够长时间保持低摩擦系数水平，达到保护水润滑摩擦副材料的目的。
  2. 根据权利要求1所述的水润滑的过载保护方法，其特征在于，步骤S1的摩擦系数曲线的具体测量方法为：实验所用摩擦副的材料、结构、尺寸等相关参数均与实际工况下的摩擦副参数一致，因海水、河水等不同水域的水成分不同对摩擦磨损的影响也不同，因此取实际工况下水域的水作为润滑介质浸没摩擦副，测量不同转速下摩擦副的摩擦系数，由测得的数据绘制出其摩擦系数随钢环转速变化的曲线。
  3. 根据权利要求1所述的水润滑的过载保护方法，其特征在于，喷嘴的内表面进行局部疏油处理，润滑油进口处的内表面做疏油处理，出口处内表面不做疏油处理，润滑油由做过表面疏油处理的进口区域流至未做过表面疏油处理的出口区域，提高了润滑油在出口处的压力，使喷出的润滑油在水中以油线的形态存在更稳定。
  4. 根据权利要求1所述的水润滑的过载保护方法，其特征在于，润滑油为乳化油，由环保型润滑油为基础油配制而成，从喷嘴喷出时有利于保持油线状态，有利于突破摩擦副入口处的逆流区，从而进入接触区实现辅助润滑。
  5. 根据权利要求1所述的水润滑的过载保护方法，其特征在于，喷嘴为变径喷嘴，其主体结构包括外壳、卷簧、弹性椎体和内筒，内筒为横截面为圆形的中空结构，内筒具有外螺纹，内筒的内表面镀全氟癸基三甲氧基硅烷做表面疏油处理，内筒的外表面一端为具有外螺纹的圆柱形，内筒的外表面另一端为圆锥形，内筒的圆柱形一端连接供油系统，内筒的圆锥形一端连接弹性椎体；弹性椎体为中空圆锥柱体，弹性椎体的横截面大的一端的空腔圆直径与内筒的空腔圆直径相同，弹性椎体的横截面大的一端与内筒粘合式或嵌入式固定连接，连接处用密封材料进行进一步的连接固定和密封；具有记忆功能的卷簧通过预卷曲的方式插在弹性椎体内，卷簧的宽度接近弹性椎体的长度，并在弹性椎体内沿着轴线卷曲接近一圈但不会首尾接触；外壳为空腔圆柱体形状，外壳的空腔一端为圆锥形，另一端为圆柱形，外壳的圆柱形空腔部分具有与内筒的外螺纹相配合的内螺纹，内筒通过外螺纹与外壳的内螺纹的配合安装在外壳内，外壳的圆锥形空腔部分的内表面与弹性椎体的外表面贴附在一起，外壳的圆锥形空腔部分的长度比弹性椎体的长度短。
  6. 根据权利要求5所述的水润滑的过载保护方法，其特征在于，喷嘴的外壳能够通过相对于内筒旋转实现相对于内筒的左右移动，当外壳相对于内筒向左移动时，与内筒连接的弹性椎体便会暴露出来，外壳向左移动的距离越长，弹性椎体暴露出来的越多，外壳向左移动的距离最大时，卷簧受到挤压径向尺寸变小，而弹性椎体恢复到未被撑大的状态，其内孔直径为最小，其内的卷簧为径向尺寸变小的卷曲状态；当外壳相对于内筒向右移动时，弹性椎 体在外壳内的空间变大，预卷曲的卷簧有恢复原来径向尺寸的趋势而使径向尺寸变大，使得弹性椎体被撑大，其内孔直径即喷嘴出口的孔径也会被撑大，使得喷嘴喷出的润滑油线的直径相应变大，当外壳向右移动的距离达到最大时，弹性椎体的孔径因内部卷簧径向尺寸的恢复被撑开到最大；通过外壳相对于内筒的左右移动能够实现喷嘴出口孔径的自由变化。
  7. 根据权利要求5所述的水润滑的过载保护方法，其特征在于，弹性椎体采用氟橡胶弹性材料或柔性PVC弹性材料，采用的弹性材料要求有良好的回弹性和耐油性。
  8. 根据权利要求1所述的水润滑的过载保护方法，其特征在于，供油系统包括注射器筒、步进电机、丝杠、L型板和滑台，注射器筒连接喷嘴，注射器芯的末端与L型板连接，注射器筒内装有润滑油；L型板位于滑台上方；滑台与L型板通过螺钉连接；丝杠与滑台之间通过滚珠丝杠副连接，步进电机与丝杠通过联轴器连接，步进电机控制丝杠的转动速率和转动时间来控制滑台的移动速度和行程，通过L型板推动注射器芯前进，进而实现润滑油线供给速率和供给量的控制，润滑油经过喷嘴喷出，喷出后的润滑油以油线形态存在。
  9. 根据权利要求1所述的水润滑的过载保护方法，其特征在于，供油系统还能够是市售的微量油泵和控制系统，通过市售的微量油泵和控制系统来控制润滑油线的供给速率和供给量。
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