An oil bag type electric grease lubrication pump and an energy-saving motor lubrication system

Abstract

The application discloses an oil bag type electric grease lubricating pump and an energy-saving motor lubricating system, relates to the technical field of lubricating pumps, and aims to solve the technical problem of fatigue cracking and sealing failure of a traditional single oil bag or diaphragm structure in high-pressure reciprocating motion, and comprises a pump shell, a hydraulic shell, a driving system and an oil bag mechanism. The oil bag mechanism is designed in an elastic linkage mode of a modular radial moving assembly and a sealing rubber ring; linear array arrangement of the oil bag assembly is matched with an anti-fatigue assembly, so that pressure is dispersed and transmitted among multiple modules, and single-point stress is reduced; a flexible connection structure of an arc-shaped sheet and a folded plate can be synchronously gathered to form overall extrusion when pressure is uniform, and can realize peristaltic self-adaptive conveying through elastic inclination of the sealing rubber ring when pressure is uneven, so that the continuity of lubricating grease conveying of an asynchronous motor is ensured, the anti-fatigue life and working condition adaptability of the oil bag are significantly improved, and early failure caused by local overload of a traditional structure is avoided.

Description

Technical Field

[0001] This invention relates to the field of lubrication pump technology, and more specifically, to an oil bladder type electric grease lubrication pump and an energy-saving electric motor lubrication system. Background Technology

[0002] The energy-saving electric motor lubrication system is an integrated lubrication solution that uses an oil-bladder electric grease pump as the core actuator and achieves precise lubrication and energy saving through intelligent control. This system combines the oil storage, pumping, and quantitative distribution functions of the oil-bladder electric grease pump with an intelligent controller. It automatically adjusts the lubrication cycle and oil injection volume based on parameters such as motor operating time, temperature, and load, ensuring that critical components such as bearings are always in optimal lubrication condition. This avoids over-lubrication or under-lubrication, significantly reducing friction loss, grease consumption, and extending equipment life, thus achieving energy-saving operation. The oil-bladder electric grease pump, as the system's power source and distribution core, is responsible for pressing grease from the oil bladder and quantitatively delivering it to each lubrication point. The energy-saving electric motor lubrication system precisely manages the working status of the lubrication pump through intelligent control strategies. The two form a close working relationship of "actuator + control system," jointly constructing a highly efficient, intelligent, and energy-saving electric motor lubrication system.

[0003] In existing technologies, high-pressure conveying equipment such as grease pumps generally use a single oil bladder or diaphragm structure as the pressure transmission and sealing element. Under long-term high-pressure reciprocating motion conditions, this type of structure has inherent defects such as material fatigue cracking and sealing failure. Due to the concentrated pressure application point and fixed deformation area, the oil bladder wall is prone to micro-cracks and expansion under repeated alternating stress, leading to early fatigue failure. At the same time, traditional diaphragm structures lack self-adaptive ability under uneven pressure, and local overload will accelerate seal wear and cause leakage. These problems seriously restrict the service life and reliability of the equipment under high-pressure and variable load conditions.

[0004] Another common technical solution is to use a rigid plunger structure. Although it can achieve high-pressure delivery, it has obvious limitations. When the system pressure distribution is uneven or the load changes abruptly, stress concentration is easily generated between the plunger and the cylinder, leading to jamming, uneven wear, or even seizure. This rigid contact method has extremely high requirements for machining accuracy and fit clearance, and cannot adapt to changes in flow characteristics or pressure fluctuations. Under variable load conditions, local pressure peaks will directly act on the plunger surface, causing excessive contact stress, accelerating wear, and reducing the overall pump efficiency. In addition, the sealing system of lubrication pumps is mostly a passive design, lacking pressure compensation capability, and is prone to leakage or power loss when pressure fluctuates.

[0005] Existing sealing systems often employ single-stage or static sealing structures, which are insufficient to meet the dynamic sealing requirements under high-pressure reciprocating motion. High frictional losses between the seals and moving parts, coupled with a lack of effective stress relief mechanisms, lead to premature seal failure. In terms of fatigue resistance design, traditional structures often rely on the fatigue strength of the materials themselves, lacking structural stress dispersion and compensation mechanisms. Stress concentration areas such as the oil bladder end and connections become initiation points for fatigue cracks, and existing technologies fail to provide active stress compensation or displacement absorption solutions. While material selection has been optimized to some extent, it has not achieved a synergistic effect with the structural design, resulting in limited improvement in overall fatigue resistance. Therefore, we propose an oil bladder-type electric grease lubrication pump and an energy-saving electric motor lubrication system. Summary of the Invention

[0006] One of the objectives of this invention is to provide an oil bladder type electric grease lubrication pump to solve the technical problems of fatigue cracking and sealing failure of traditional single oil bladder or diaphragm structures under high pressure reciprocating motion.

[0007] To solve the above technical problems, the present invention provides the following technical solution: an oil bladder type electric grease lubrication pump, comprising a pump housing, a hydraulic housing, a drive system and an oil bladder mechanism, wherein an oil inlet channel and an oil outlet channel are arranged on the hydraulic housing, and an oil inlet check valve and an oil outlet check valve are respectively installed in the oil inlet channel and the oil outlet channel; The pump casing and the hydraulic casing are connected in a sealed manner to form at least one sealed chamber; The oil bladder mechanism is arranged within the sealed cavity; The oil bladder mechanism includes at least one set of oil bladder components and at least one set of fatigue-resistant components; The oil bladder assembly includes several radially moving modules arranged in a linear array between the oil inlet channel and the oil outlet channel; Each of the adjacent radial movement modules is sealed with a sealing rubber ring; Each of the radial movement modules includes several arc-shaped plates capable of synchronously converging or expanding radially; Each of the adjacent arc-shaped pieces is fixedly connected with a folding plate; When the pressure on several oil bladder components is consistent, several arc-shaped pieces converge simultaneously, and the folding plate folds inward, so that several arc-shaped pieces form a circular cylindrical structure, squeezing out the internal grease. When the pressure distribution of several oil bladder components is uneven, the arc-shaped plates in the radially moving module at the point of maximum pressure converge first. The sealing rubber rings connected to its two ends elastically tilt due to the unbalanced force, applying lateral stretching and guidance to the arc-shaped plates of adjacent modules, so that the convergence action is transmitted sequentially, forming a peristaltic conveying pattern. The oil bladder mechanism of this invention effectively solves the problems of fatigue cracking and sealing failure of traditional single oil bladder or diaphragm structures under high pressure reciprocating motion through the elastic linkage design of modular radially moving components and sealing rubber rings. At the same time, it overcomes the jamming and wear defects caused by stress concentration in rigid plungers under uneven pressure. Specifically, the linear array arrangement of oil bladder components, combined with anti-fatigue components, allows the pressure to be distributed and transmitted between multiple modules, reducing single-point stress. The flexible connection structure of the arc-shaped plates and folding plates can synchronously converge to form an overall compression when the pressure is uniform, and achieve peristaltic adaptive conveying through the elastic tilt of the sealing rubber rings when the pressure is uneven. This ensures the continuity of conveying and significantly improves the fatigue life and working condition adaptability of the oil bladder, avoiding the early failure caused by local overload in traditional structures.

[0008] Preferably, the oil bladder assembly further includes two mounting hoppers, both of which are sealed to the two end radial movement modules, and each mounting hopper is provided with a plug ring.

[0009] Preferably, any one of the radial movement modules further includes several fixing blocks, all of which are fixedly connected to the outer convex surface of the arc-shaped plate.

[0010] Preferably, each of the fixing blocks is provided with two limiting holes, and the axes of the two limiting holes are arranged in an up-down cross direction.

[0011] Preferably, guide rods are slidably fitted inside the limiting holes on two adjacent fixing blocks.

[0012] Preferably, the fatigue-resistant component includes two annular grooves, both of which are formed on the inner wall of the hydraulic housing. One of the annular grooves is axially coaxial with the oil outlet check valve, and the other annular groove is axially coaxial with the oil inlet check valve.

[0013] Preferably, the insertion ring is inserted into the annular groove, and the inner walls on both sides of the hydraulic housing are provided with a plurality of inclined holes in an annular array, and the ends of the inclined holes are all connected to the annular groove.

[0014] Preferably, a protective cap is fitted inside each of the inclined holes.

[0015] Preferably, each of the inclined holes is fitted with a secondary sealing post with a sealing ring inside, and the secondary sealing post is fitted with a primary sealing post inside, with the end of the primary sealing post passing through the protective cap.

[0016] Preferably, the insertion ring, the primary sealing post, and the secondary sealing post together form a multi-stage sealing cavity within the inclined hole and the annular groove.

[0017] An energy-saving electric motor lubrication system is characterized by comprising the aforementioned oil bladder type electric grease lubrication pump.

[0018] Compared with the prior art, the beneficial effects of the present invention are: 1. The oil bladder mechanism of this invention effectively solves the problems of fatigue cracking and sealing failure in traditional single oil bladder or diaphragm structures under high pressure reciprocating motion through the elastic linkage design of modular radial moving components and sealing rubber rings. At the same time, it overcomes the jamming and wear defects caused by stress concentration in rigid plungers under uneven pressure. Specifically, the linear array arrangement of the oil bladder components, combined with the anti-fatigue components, allows the pressure to be distributed and transmitted among multiple modules, reducing single-point stress. The flexible connection structure of the arc-shaped plate and the folded plate can synchronously gather to form an overall compression when the pressure is uniform, and achieve peristaltic adaptive conveying through the elastic tilting of the sealing rubber ring when the pressure is uneven. This ensures the continuity of conveying and significantly improves the fatigue life and working condition adaptability of the oil bladder, avoiding the early failure caused by local overload in traditional structures.

[0019] 2. The core innovation of this invention lies in its unique multi-modal grease bladder design. This design enables the pump to achieve efficient, synchronous, and extrusive delivery, similar to traditional lubrication pumps, even under uniform pressure. More importantly, when uneven pressure distribution occurs due to flow channel characteristics or load variations, the system automatically triggers a "creep wave" type intelligent coordinated delivery mode. That is, the module with the highest pressure acts first, and the action is sequentially transmitted to adjacent modules through the elastic tilt of the flexible sealing ring. This mode greatly enhances the pump's adaptability to complex operating conditions, effectively avoiding seal failure or component overload caused by local pressure peaks. It achieves a leap from a "rigid" to a "flexible and intelligent" delivery mode, thus ensuring a stable and continuous grease supply under wide pressure ranges and variable load conditions.

[0020] 3. This invention solves the problem of fatigue failure caused by alternating stress in traditional lubrication pumps through a series of innovative structural designs, achieving excellent durability. This is mainly reflected in three aspects: First, in the oil bladder assembly, the precise fit between the guide rod and the cross-limiting hole ensures the high synchronicity and trajectory accuracy of the arc-shaped plate movement, fundamentally eliminating internal stress caused by asynchronous movement. Second, the anti-fatigue components at both ends of the oil bladder constitute an active multi-stage dynamic sealing and compensation system. This system can not only absorb axial displacement when the oil bladder deforms, but also generate an "adsorption and recovery force" on the plug ring by establishing a controllable negative pressure, actively offsetting the stress concentration at the end, and transforming the fatigue-prone connection area into a "flexible joint" with self-adjustment and buffering capabilities. Third, key components use advanced oil-resistant and fatigue-resistant elastomer materials, providing a guarantee for long service life from the material level. These measures work synergistically to significantly inhibit the initiation and propagation of material fatigue cracks.

[0021] 4. The sealing system of this invention exhibits multi-layered and dynamically adaptive characteristics, achieving zero leakage while reducing frictional losses. Inside the oil bladder, modules are sealed through fatigue-resistant elastic sealing rings, which rely on the material's self-tightening effect to maintain reliable contact during periodic deformation. At the interface between the oil bladder and the hydraulic housing, the plug-in ring and the fatigue-resistant components together form the core dynamic sealing hub. In particular, the "multi-stage sealing cavity" formed by the plug-in ring, primary and secondary sealing columns works on a principle similar to a miniature hydraulic buffer and compensator. It not only achieves zero-leakage sealing of the sliding interface under high pressure, but also actively compensates for changes in the length of the oil bladder through intelligent adjustment of the negative pressure inside the cavity, generating an adsorption force that resets the plug-in ring. This design transforms traditional passive sealing into active compensation sealing, significantly reducing power loss caused by scratching and squeezing of the sealing components, and improving the mechanical efficiency and reliability of the entire pump. Attached Figure Description

[0022] Figure 1 This is a schematic diagram of the overall structure of the present invention.

[0023] Figure 2 This is a schematic cross-sectional view of the overall structure of the present invention.

[0024] Figure 3 For the present invention Figure 2 A magnified structural diagram at point A in the diagram.

[0025] Figure 4 This is a partial cross-sectional structural diagram of the present invention, illustrating the cross-sectional structure of the oil bladder mechanism.

[0026] Figure 5 This is a three-dimensional structural diagram of the oil bladder mechanism of the present invention, to illustrate the three-dimensional structure of the oil bladder assembly.

[0027] Figure 6This is a three-dimensional structural diagram of the radial movement module of the present invention.

[0028] Figure 7 This is a schematic cross-sectional view of the radial movement module of the present invention.

[0029] Figure 8 This is a schematic cross-sectional view of the radial moving module of the present invention, illustrating the folding structure of the folding plate.

[0030] Figure 9 This is a three-dimensional cross-sectional view of the anti-fatigue component of the present invention.

[0031] Figure 10 This is a schematic cross-sectional view of the annular groove of the present invention.

[0032] Figure 11 This is a three-dimensional structural diagram of the asynchronous motor of the present invention.

[0033] The following are the labels in the diagram: 1. Pump housing; 12. Hydraulic housing; 121. Oil inlet passage; 122. Oil outlet passage; 123. Oil inlet check valve; 124. Oil outlet check valve; 13. Drive system; 2. Oil bladder mechanism; 21. Oil bladder assembly; 211. Radial movement module; 2111. Arc-shaped plate; 2112. Fixing block; 2113. Guide rod; 2114. Folding plate; 212. Sealing rubber ring; 213. Mounting bucket; 2131. Insertion ring; 22. Fatigue resistance component; 221. Annular groove; 222. Inclined hole; 223. Protective cap; 224. Secondary sealing column; 225. Primary sealing column; 3. Asynchronous motor. Detailed Implementation

[0034] Example 1, such as Figures 1-4 and Figure 10 As shown, the present invention relates to an oil bladder type electric grease lubrication pump, which includes a pump housing 1, a hydraulic housing 12, a drive system 13, and an oil bladder mechanism 2.

[0035] Combination Figures 1-4 As shown, the drive system 13 includes a motor, a cam mechanism, and a plunger assembly. The motor is located on one side of the pump housing 1 and drives the cam in the cam mechanism to drive the plunger to reciprocate within the hydraulic chamber. The pump housing 1 and the hydraulic housing 12 are connected by a sealing connection to form at least one sealed chamber. The oil bladder mechanism 2 is located inside the hydraulic housing 12, i.e., within the hydraulic chamber. The hydraulic housing 12 is provided with an oil inlet channel 121 and an oil outlet channel 122, which are used for the intake and discharge of lubricating grease, respectively. An oil inlet check valve 123 is provided at the oil inlet channel 121, and an oil outlet check valve 124 is provided at the oil outlet channel 122. The oil inlet check valve 123 and the oil outlet check valve 124 are respectively arranged on the inner walls of both sides of the hydraulic housing 12 (e.g., ...). Figure 2 and Figure 4 As shown in the figure, the unidirectional intake and discharge of lubricating grease are controlled respectively.

[0036] Specifically, the reciprocating motion of the plunger compresses the hydraulic oil in the hydraulic chamber, and the hydraulic oil then transmits the pressure to the outer wall of the oil bladder mechanism 2, forcing the oil bladder to undergo periodic elastic deformation. When the oil bladder expands under hydraulic pressure, its internal volume increases, creating a negative pressure. The inlet check valve 123 opens, while the outlet check valve 124 closes, and external grease is drawn into the inner cavity of the oil bladder through the inlet channel 121. When the oil bladder is compressed, its internal volume decreases, and the pressure increases. The inlet check valve 123 closes, while the outlet check valve 124 opens, and the grease is metered and continuously expelled from the system through the outlet channel 122.

[0037] like Figure 3 and Figures 5-10 As shown, the oil bladder mechanism 2 in this embodiment includes at least one set of oil bladder assemblies 21 and at least one set of anti-fatigue components 22. Both the oil bladder assemblies 21 and the anti-fatigue components 22 are arranged inside the sealed cavity. The oil bladder assemblies 21 can periodically and orderly contract or expand, while the anti-fatigue components 22 are correspondingly arranged in the stress concentration area of ​​the oil bladder assemblies 21 (i.e., the connection between the two ends of the oil bladder assemblies 21) to enhance structural strength, absorb alternating stress, and suppress material fatigue.

[0038] Combination Figure 3 and Figure 5 As shown, in this embodiment, the oil bladder assembly 21 includes several radially moving modules 211, which are arranged in a linear array between the inlet check valve 123 and the outlet check valve 124. Each adjacent radially moving module 211 is sealed with a sealing rubber ring 212. Each of the two end radially moving modules 211 is sealed with a mounting hopper 213 on one side, and each mounting hopper 213 is equipped with a plug-in ring 2131. Specifically, the sealing rubber ring 212, mounting hopper 213, and plug-in ring 2131 are all made of oil-resistant and fatigue-resistant fluororubber or hydrogenated nitrile rubber, forming a reliable seal with the end face of the radially moving module 211 through interference fit or bonding. During the periodic deformation of the oil bladder, the sealing rubber ring 212 compensates for the phase deformation through elastic deformation. The relative displacement between adjacent modules, along with the material self-tightening effect, achieves reliable sealing. The plug ring 2131 has a piston function. When the oil bladder assembly 21 is working, the plug ring 2131 is displaced due to the contraction or expansion of the sealing rubber ring 212 and the radial movement module 211. By sliding the plug ring 2131 in the installation position, it compensates for the contraction of the sealing rubber ring 212 and the radial movement module 211, and performs shape compensation for the convergence of the sealing rubber ring 212 and the radial movement module 211, ensuring the stability and coaxiality of the overall deformation process of the oil bladder. At the same time, through the sliding fit between the plug ring 2131 and the interface of the hydraulic housing 12, dynamic sealing is achieved and the axial displacement caused by end deformation is absorbed, thereby effectively reducing the stress concentration at the oil bladder connection and extending the overall service life.

[0039] Combination Figure 3 and Figures 6-8 As shown, in this embodiment, the structures and functions of several radial movement modules 211 are identical. Therefore, the composition is described using any one of them as an example: The radial movement module 211 includes four arc-shaped pieces 2111 arranged in a circular array. Each arc-shaped piece 2111 has a fixed block 2112 fixedly connected to its convex surface. Each fixed block 2112 has two limiting holes arranged on it. The axes of the two limiting holes are arranged vertically and intersectingly. Guide rods 2113 are slidably fitted inside the limiting holes of two adjacent fixed blocks 2112. Folded plates 2114 are fixedly connected between adjacent arc-shaped pieces 2111; specifically, the arc-shaped pieces 2111 are composed of a metal substrate (such as aluminum alloy or stainless steel) and a surface elastic coating layer (such as polyurethane or nitrile rubber), and the fixing blocks 2112 are made of the same or similar metal material as the substrate of the arc-shaped pieces 2111 (such as cast aluminum or stainless steel), and are fixed to the convex surface of the arc-shaped pieces 2111 by welding or bolting; the guide rods 2113 are made of high-strength stainless steel bars or surface-hardened carbon steel, and the surface can be chrome-plated or specially treated. Fluoropolymer coating is used to reduce the coefficient of friction; the folded plate 2114 is made of the same material as the sealing rubber ring 212 (i.e., oil-resistant and fatigue-resistant fluororubber or hydrogenated nitrile rubber); at the same time, during the oil discharge process, the specific response mode of the oil bladder assembly 21 depends on the distribution of its surface pressure: when the pressure at each point is uniform, several radial moving modules 211 work synchronously, and several arc-shaped plates 2111 within them converge towards the center simultaneously and with the same amplitude, achieving a smooth, continuous and efficient discharge of grease; when the surface pressure distribution is uneven (for example, due to flow channel characteristics or transient loads), the radial moving module 211 bearing the maximum pressure will start first, and its internal arc-shaped plates 2111 will begin to converge. This causes the sealing rubber ring 212 connected to its two ends to have an elastic tilting tendency due to the unbalanced force, which in turn applies a lateral stretching and guiding effect to the arc-shaped plates 2111 of the adjacent modules, thereby triggering the adjacent modules to converge inward in sequence and gradually, ultimately forming a self-coordinated and sequentially transmitted compression motion pattern similar to a creeping wave on the surface of the oil bladder.

[0040] Specifically, when several arc-shaped pieces 2111 converge, the guide rod 2113 slides inside the limiting hole on the fixing block 2112 to limit the arc-shaped pieces 2111, causing them to move radially synchronously. The folding plate 2114 follows pre-set folding marks on the plate (such as...). Figure 8As shown in the figure (the dotted line in the figure is the folding line), the folding causes several arc-shaped pieces 2111 to gather into a cylindrical shape. The folding plate 2114 protrudes into the cylindrical shape, reducing the flow space inside and discharging the grease. When the several arc-shaped pieces 2111 unfold, the guide rod 2113 limits the arc-shaped pieces 2111, causing the several arc-shaped pieces 2111 to move radially and reset synchronously. The folding plate 2114 returns to its initial position (i.e., the state when the several arc-shaped pieces 2111 unfold), and the internal volume increases to form a negative pressure, which can draw the lubricating grease from the oil inlet channel 121 into it.

[0041] This invention solves the problem of fatigue failure caused by alternating stress in traditional lubrication pumps through a series of innovative structural designs, achieving excellent durability. This is mainly reflected in three aspects: First, in the oil bladder assembly 21, the precise fit between the guide rod 2113 and the cross-limiting hole ensures the high synchronicity and trajectory accuracy of the arc-shaped plate 2111's movement, fundamentally eliminating internal stress caused by asynchronous movement. Second, the anti-fatigue components 22 at both ends of the oil bladder constitute an active multi-stage dynamic sealing and compensation system. This system not only absorbs axial displacement when the oil bladder deforms, but also generates an "adsorption and recovery force" on the insertion ring 2131 by establishing a controllable negative pressure, actively offsetting end stress concentration and transforming the fatigue-prone connection area into a "flexible joint" with self-adjusting and buffering capabilities. Third, key components use advanced oil-resistant and fatigue-resistant elastomer materials, providing a guarantee for long service life from a material perspective. These measures work synergistically to significantly inhibit the initiation and propagation of material fatigue cracks.

[0042] Combination Figure 3 and Figures 9-10 As shown, in this embodiment, the fatigue-resistant component 22 includes two annular grooves 221, both of which are formed on the inner wall of the hydraulic housing 12. One annular groove 221 is axially coaxial with the oil outlet check valve 124, and the other annular groove 221 is axially coaxial with the oil inlet check valve 123. A plug-in ring 2131 is inserted into the annular groove 221. Several inclined holes 222 are formed in an annular array on both sides of the inner wall of the hydraulic housing 12, and the ends of the inclined holes 222 are connected to the annular grooves 221. A protective cap 223 is fitted inside each inclined hole 222, and a secondary sealing post 224 with a sealing ring is slidably fitted inside each inclined hole 222. A primary sealing post 225 is slidably fitted inside the secondary sealing post 224, and the end of the primary sealing post 225 passes through the protective cap 223. Specifically, the plug-in ring 2131, the primary sealing post 225, and the secondary sealing post 224 together form a multi-stage sealing cavity in the inclined holes 222 and the annular grooves 221.

[0043] Specifically, when the hydraulic system is working, the oil pressure is transmitted through the annular groove 221 to each inclined hole 222, fixing the primary sealing column 225 and the secondary sealing column 224 within the inclined holes 222 and keeping them stationary. This also compresses several arc-shaped plates 2111, causing them to converge (oil outlet state). Meanwhile, the mounting bucket 213 deforms, and the insertion ring 2131 moves towards the mounting bucket 213, compensating for the change in length of the oil bladder assembly 21 in the converged state. At this time, the multi-stage sealing cavity formed by the insertion ring 2131, the primary sealing column 225, and the secondary sealing column 224 within the inclined holes 222 and the annular groove 221 is under negative pressure due to its increased volume. When the oil pressure is transmitted through the annular groove 221 to each inclined hole 222, the primary sealing column 225 and the secondary sealing column 224 slide, and the secondary sealing column 224 contacts the protective cap 223, further increasing the multi-stage sealing... The negative pressure state of the cavity causes the displaced insertion ring 2131 to return to its initial state and tightly adhere to the insertion ring 2131. When the plunger returns, the hydraulic system pressure is released or reduced, the hydraulic oil pressure acting on the outer wall of the oil bladder assembly 21 decreases accordingly. Under the combined action of its own elasticity (especially the elasticity of the sealing rubber ring 212 and the folding plate 2114) and the negative pressure formed by the internal lubricating grease, the oil bladder assembly 21 begins to elastically expand and reset. At this time, the installation bucket 213, which was deformed during the compression process, also recovers, causing the insertion ring 2131 to slide away from the installation bucket 213. Furthermore, the first-stage sealing column 225 and the second-stage sealing column 224 move (reverse movement) in the inclined hole 222 due to hydraulic pressure, resulting in the multi-stage sealing cavity being in a negative pressure state due to the increase in volume, forming a stable negative pressure adsorption force, which continuously acts on the end of the insertion ring 2131, stabilizing it.

[0044] The sealing system of this invention exhibits multi-layered and dynamically adaptive characteristics, achieving zero leakage while reducing frictional losses. Inside the oil bladder, modules are sealed through fatigue-resistant elastic sealing rings, which rely on the material's self-tightening effect to maintain reliable contact during periodic deformation. At the interface between the oil bladder and the hydraulic housing 12, the plug ring 2131 and the fatigue-resistant component 22 together constitute the core dynamic sealing hub. In particular, the "multi-stage sealing cavity" formed by the plug ring 2131 and the first and second stage sealing pillars 224 works on a principle similar to a miniature hydraulic buffer and compensator. It not only achieves zero-leakage sealing of the sliding interface under high pressure, but also actively compensates for changes in the length of the oil bladder through intelligent adjustment of the negative pressure inside the cavity, and generates an adsorption force that resets the plug ring 2131. This design transforms traditional passive sealing into active compensation sealing, significantly reducing power loss caused by scratching and squeezing of the sealing components, and improving the mechanical efficiency and reliability of the entire pump.

[0045] Example 2, as follows Figure 11As shown in this embodiment, the present invention provides an energy-saving electric motor lubrication system, including an asynchronous motor 3, which is connected to an oil outlet channel. Specifically, the working principle of the asynchronous motor (induction motor) is as follows: three-phase alternating current is applied to the stator winding to generate a rotating magnetic field, the rotor conductor cuts the magnetic lines of force to generate an induced current, and the induced current interacts with the rotating magnetic field to generate an electromagnetic torque, driving the rotor to rotate. When the motor bearings (rolling or sliding bearings) rotate at high speed, friction and wear will occur. It is necessary to form an oil film with grease or lubricating oil to reduce the coefficient of friction, reduce wear, dissipate heat and cool down, and prevent corrosion. The oil bladder type electric grease lubrication pump delivers grease to the lubrication points such as the motor bearings in a timed and quantitative manner through the oil pipeline to achieve automatic lubrication, ensure long-term stable operation of the motor, extend its service life, and reduce maintenance costs.

[0046] Working principle: This embodiment provides an oil bladder type electric grease lubrication pump. In use, the motor drives the cam mechanism and the plunger assembly, causing the plunger to reciprocate in a closed chamber composed of the pump housing 1 and the hydraulic housing 12. The direct action of the plunger is the hydraulic oil filling the chamber, not the grease. When the plunger moves forward (compressing), the hydraulic oil is squeezed, and its pressure is transmitted through the inner wall of the hydraulic housing 12 to the outer surface of the oil bladder mechanism 2 located therein, forcing the oil bladder mechanism 2 to undergo compression deformation. Conversely, when the plunger moves backward (returning), the hydraulic oil pressure is released, and the oil bladder mechanism 2 expands and resets under the combined action of its own elasticity and external hydraulic changes.

[0047] When the pressure on the oil bladder assemblies 21 is uniform, the radial movement modules 211 work synchronously. Several arc-shaped pieces 2111 slide within the limiting holes on the fixed block 2112 via guide rods 2113, limiting the arc-shaped pieces 2111. This causes the arc-shaped pieces 2111 to converge towards the center simultaneously and with the same amplitude, achieving stable, continuous, and efficient grease extrusion. Furthermore, the folding plate 2114 follows the pre-set folding marks on the plate (such as...). Figure 8 As shown in the figure (the dotted line is the folding line), the folding causes several arc-shaped pieces 2111 to gather into a cylindrical shape. The folding plate 2114 protrudes into the cylindrical shape, reducing the flow space inside and discharging the grease. When the plunger moves backward (return stroke), the hydraulic oil pressure is released. Under the combined action of the elasticity of the folding plate 2114, the sealing rubber ring 212, and the mounting bucket 213, as well as the external hydraulic pressure changes, the several arc-shaped pieces 2111 are driven to reset.

[0048] When the pressure distribution of several oil bladder assemblies 21 is uneven, the radial moving module 211 bearing the maximum pressure will start first, and its internal arc-shaped pieces 2111 will begin to converge. This causes the sealing rubber rings 212 connected to its two ends to have an elastic tilting tendency due to the unbalanced force, which in turn applies a lateral stretching and guiding effect to the arc-shaped pieces 2111 of the adjacent modules. The arc-shaped pieces 2111 in the remaining radial moving modules 211 will then converge, and can exhibit a creeping motion when delivering grease.

[0049] During grease transport, the oil pressure is transmitted through the annular groove 221 to each inclined hole 222, fixing the primary sealing column 225 and the secondary sealing column 224 within the inclined holes 222 and keeping them stationary. This also compresses several arc-shaped pieces 2111, causing them to converge. The mounting hopper 213 deforms, and the insertion ring 2131 moves towards the mounting hopper 213, compensating for the change in length of the oil bladder assembly 21 in the converged state. At this time, the multi-stage sealing cavity formed by the insertion ring 2131, the primary sealing column 225, and the secondary sealing column 224 within the inclined holes 222 and the annular groove 221 is under negative pressure due to its increased volume. When the oil pressure is transmitted through the annular groove 221 to each inclined hole 222, the primary sealing column 225 and the secondary sealing column 224 slide, and the secondary sealing column 224 contacts the protective cap 223, further increasing the negative pressure of the multi-stage sealing cavity. This causes the displaced insertion ring 2131 to return to its initial state and tightly adhere to the insertion ring 2131. When the plunger returns, or the hydraulic system pressure is released or reduced, the hydraulic oil pressure acting on the outer wall of the oil bladder assembly 21 decreases accordingly. Under the combined action of its own elasticity (especially the elasticity of the sealing rubber ring 212 and the folding plate 2114) and the negative pressure formed by the internal lubricating grease, the oil bladder assembly 21 begins to elastically expand and reset. At this time, the installation bucket 213, which was deformed during the compression process, also recovers, causing the insertion ring 2131 to slide away from the installation bucket 213. Furthermore, the first-stage sealing column 225 and the second-stage sealing column 224 move (reverse movement) in the inclined hole 222 due to hydraulic pressure, causing the multi-stage sealing cavity to be in a negative pressure state due to the increase in volume, forming a stable negative pressure adsorption force, which continuously acts on the end of the insertion ring 2131, stabilizing it.

[0050] The embodiments disclosed in this invention are preferred embodiments, but are not limited thereto. Those skilled in the art can easily understand the spirit of this invention based on the above embodiments and make different extensions and variations, but as long as they do not depart from the spirit of this invention, they are all within the protection scope of this invention.

Claims

1. A bladder-type electric grease lubrication pump, comprising a pump housing (1), a hydraulic housing (12), a drive system (13), and a bladder mechanism (2), characterized in that, The hydraulic housing (12) is provided with an oil inlet channel (121) and an oil outlet channel (122), and an oil inlet check valve (123) and an oil outlet check valve (124) are respectively installed in the oil inlet channel (121) and the oil outlet channel (122). The pump housing (1) and the hydraulic housing (12) are connected by a sealed connection to form at least one sealed chamber; The oil bladder mechanism (2) is arranged in the sealed cavity; The oil bladder mechanism (2) includes at least one set of oil bladder components (21) and at least one set of anti-fatigue components (22). The oil bladder assembly (21) includes a plurality of radially moving modules (211) arranged in a linear array between the oil inlet channel (121) and the oil outlet channel (122). Each of the adjacent radial moving modules (211) is sealed with a sealing rubber ring (212). Each of the radial movement modules (211) includes a plurality of arc-shaped pieces (2111) capable of synchronously converging or expanding radially. Each of the adjacent arc-shaped pieces (2111) is fixedly connected with a folding plate (2114). When the pressure on several oil bladder assemblies (21) is consistent, several arc-shaped pieces (2111) converge simultaneously, and the folding plate (2114) folds inward, so that several arc-shaped pieces (2111) form a circular cylindrical structure, squeezing out the internal grease. When the pressure distribution of several oil bladder components (21) is uneven, several arc-shaped pieces (2111) in the radial moving module (211) at the point of maximum pressure first gather together. The sealing rubber ring (212) connected to its two ends produces elastic tilting due to the unbalanced force, which applies lateral stretching and guidance to the arc-shaped pieces (2111) of adjacent modules, so that the gathering action is transmitted in sequence, forming a peristaltic conveying pattern.

2. The oil-bladder type electric grease lubrication pump according to claim 1, characterized in that, The oil bladder assembly (21) also includes two mounting hoppers (213), both of which are sealed to the two end radial moving modules (211), and each mounting hopper (213) is provided with a plug ring (2131).

3. The oil-bladder type electric grease lubrication pump according to claim 2, characterized in that, Each of the radial moving modules (211) further includes several fixing blocks (2112), and the fixing blocks (2112) are all fixedly connected to the outer convex surface of the arc-shaped piece (2111).

4. The oil-bladder type electric grease lubrication pump according to claim 3, characterized in that, Each of the fixed blocks (2112) is provided with two limiting holes, and the axial directions of the two limiting holes are arranged in an up-down cross pattern.

5. The oil-bladder type electric grease lubrication pump according to claim 4, characterized in that, Guide rods (2113) are slidably fitted inside the limiting holes on the two adjacent fixing blocks (2112).

6. The oil-bladder type electric grease lubrication pump according to claim 5, characterized in that, The fatigue-resistant component (22) includes two annular grooves (221), both of which are formed on the inner wall of the hydraulic housing (12). One of the annular grooves (221) is axially coaxial with the oil outlet check valve (124), and the other annular groove (221) is axially coaxial with the oil inlet check valve (123).

7. A bladder-type electric grease lubrication pump according to claim 6, characterized in that, The insertion ring (2131) is inserted into the annular groove (221). The inner walls on both sides of the hydraulic housing (12) are provided with a number of inclined holes (222) in an annular array, and the ends of the inclined holes (222) are all connected to the annular groove (221).

8. The oil-bladder type electric grease lubrication pump according to claim 7, characterized in that, Each of the inclined holes (222) is fitted with a protective cap (223), and each of the inclined holes (222) is fitted with a secondary sealing post (224) with a sealing ring. The secondary sealing post (224) is fitted with a primary sealing post (225), and the end of the primary sealing post (225) passes through the protective cap (223).

9. A bladder-type electric grease lubrication pump according to claim 8, characterized in that, The insertion ring (2131), the primary sealing post (225) and the secondary sealing post (224) together form a multi-level sealing cavity in the inclined hole (222) and the annular groove (221).

10. An energy-saving electric motor lubrication system, characterized in that, Including the oil-bladder type electric grease lubrication pump as described in any one of claims 1-9.

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