Movable disc structure and compressor applying same

Abstract

The movable disc structure comprises a movable disc body, a sinking groove is formed in the exhaust center side of the movable disc body, and an oil supply assembly is arranged in the sinking groove; the oil supply assembly comprises a porous pressing plate and a lubricating medium arranged below the porous pressing plate, and the lubricating medium is configured to be softened when the central cavity of the movable disc reaches the preset temperature and the preset pressure and separate out lubricating oil drops through the porous pressing plate. A lubricating medium is arranged in the sinking groove and controlled to be released through the porous pressing plate, oil can be directly supplied to a high-pressure and high-temperature center cavity area, and the defect that the center area cannot be effectively lubricated in a traditional peripheral oil supply mode is overcome. According to the structure, oil supply is triggered through high temperature and high pressure of the working condition, the oil supply amount does not need to depend on an external oil way or increase extra oil holes, the problems that the compression energy efficiency is reduced and the oil spitting rate is increased due to excessive oil amount are solved, an oil duct system used for lubricating in a traditional movable disc is omitted, and unification of structural optimization and energy efficiency improvement is achieved.

Description

TECHNICAL FIELD

[0001] The present application belongs to the technical field of compressors, and particularly relates to a dynamic disc structure and a compressor applying the same. BACKGROUND

[0002] As a kind of high-efficiency compressor, scroll compressor is widely used in air conditioners and refrigeration systems, and its working principle relies on the meshing movement between dynamic disc and static disc to realize the suction, compression and discharge of gas. In this process, lubricating oil plays a key role, including reducing friction, enhancing sealing, cooling and cleaning internal impurities.

[0003] In the prior art, lubricating oil is usually supplied to the outer crescent-shaped chamber through the medium-pressure oil hole and the high-pressure oil hole, and it is expected that the lubricating oil will gradually move to the center during the compression process. However, due to the pressure relief hole set to avoid over-compression during the compression process, the gas and lubricating oil will escape from the center high-pressure cavity when the exhaust pressure is reached, resulting in insufficient lubricating oil in the center area. The center high-pressure cavity has high pressure and temperature, and the metal parts are prone to thermal expansion and deformation, so the demand for lubrication and sealing is more urgent. Although the problem can be alleviated by increasing the amount of oil supply, excessive oil supply will lead to reduced compression efficiency, increased power and increased oil discharge rate, and the prior art lacks a lubrication scheme that can accurately supply oil under high pressure and high temperature conditions without affecting the efficiency of the compressor. SUMMARY

[0004] Therefore, the present application provides a dynamic disc structure and a compressor applying the same, which can accurately supply oil under high pressure and high temperature conditions without affecting the efficiency of the compressor.

[0005] To solve the above problems, according to one aspect of the present application, an embodiment of the present application provides a dynamic disc structure, which comprises a dynamic disc body, a sink is arranged on the exhaust center side of the dynamic disc body, and a oil supply assembly is arranged in the sink; the oil supply assembly comprises a porous pressing plate and a lubricating medium arranged below the porous pressing plate, wherein the lubricating medium is configured to soften when the center cavity of the dynamic disc reaches a predetermined temperature and a predetermined pressure, and to release lubricating oil droplets through the holes of the porous pressing plate.

[0006] In some embodiments, the porous pressing plate comprises a mounting base and a pressing plate body, the pressing plate body has a plurality of holes, the pressing plate body is movably arranged in the mounting base, the pressing plate body is arranged above the lubricating medium, and the pressing plate body moves downward to press the lubricating medium when under pressure.

[0007] In some embodiments, the mesh number and hole diameter of the pressing plate body are configured to allow the pressed lubricating medium to pass when the center cavity of the dynamic disc body reaches the predetermined pressure.

[0008] In some embodiments, the lubricating medium comprises at least two grease modules, each of the grease modules having a different melting point.

[0009] In some embodiments, the lubricating medium comprises a first grease, a second grease and a third grease arranged horizontally and side by side, the melting points of the first, second and third greases increasing in order.

[0010] In some embodiments, the porous compression plate comprises a mounting frame having a partition plate inside, the partition plate separating the mounting frame into a first space, a second space and a third space, the first, second and third greases being located in the first, second and third spaces respectively, and the porous compression plate further comprises a first filter screen, a second filter screen and a third filter screen cooperating with the first, second and third greases in order, the pore sizes of the first, second and third filter screens increasing in order.

[0011] In some embodiments, the volume percentage of the first grease , the volume percentage of the second grease and the volume percentage of the third grease are respectively: wherein, n is the number of continuous temperature segments into which the working temperature range of the compressor is divided, is the working time percentage of the compressor in the i-th temperature segment (i = 1, 2,..., n), is the representative temperature of the i-th temperature segment; , , are the weight coefficients of the first, second and third greases respectively when they are in their dominant temperature segments; is the weight coefficient of the first and second greases when they are in a mixed temperature segment, is the weight coefficient of the second and third greases when they are in a mixed temperature segment, is the weight coefficient of the first, second and third greases when they are in a mixed temperature segment; , and are the melting points of the first, second and third greases respectively.

[0012] In some embodiments, the profile contour of the sink is adapted to the gas pressure distribution at the center of the gas exhaust of the orbiting scroll body.​​​

[0013] In some embodiments, the outer contour of the mounting base is adapted to the contour of the sink, so that the oil supply assembly can be stably mounted in the sink of different shapes.

[0014] According to one aspect of the present application, embodiments of the present application provide a compressor comprising the above-mentioned orbiting disk structure.

[0015] Compared with the prior art, the orbiting disk structure of the present application has at least the following beneficial effects: The orbiting disk structure provided by the present application comprises an orbiting disk body, a sink is arranged on the exhaust center side of the orbiting disk body, and an oil supply assembly is arranged in the sink; the oil supply assembly comprises a porous pressing plate and a lubricating medium arranged below the porous pressing plate, wherein the lubricating medium is configured to soften when the central cavity of the orbiting disk reaches a predetermined temperature and a predetermined pressure, and to release lubricating oil drops through the holes of the porous pressing plate.

[0016] In the present application, the lubricating medium is arranged in the sink on the exhaust center side of the orbiting disk and is released through the porous pressing plate, so that oil can be directly supplied to the high-pressure and high-temperature central cavity area, which makes up for the deficiency that the traditional peripheral oil supply method cannot effectively lubricate the central area; further, the structure triggers oil supply by using the high temperature and high pressure of the working condition, without relying on complex external oil circuits or increasing additional oil holes for oil supply, which not only avoids the problems of compression energy efficiency reduction and oil discharge rate increase caused by excessive oil amount, but also simplifies the overall structure of the orbiting disk, eliminates the complex oil channel system for lubrication in the traditional orbiting disk, and realizes the unification of structure optimization and energy efficiency improvement.

[0017] The compressor provided by the present application is designed based on the above-mentioned orbiting disk structure, and its beneficial effects are the same as those of the orbiting disk structure, which will not be repeated here.

[0018] The above description is only a summary of the technical solutions of the present application, in order to more clearly understand the technical means of the present application, and to implement the content of the description, the following will describe the preferred embodiments of the present application in detail with reference to the accompanying drawings. BRIEF DESCRIPTION OF DRAWINGS

[0019] In order to more clearly illustrate the technical solutions of the embodiments of the present application, the following will briefly introduce the drawings needed in the embodiment description. Obviously, the drawings in the following description are some embodiments of the present application, and other drawings can also be obtained by those skilled in the art without creative labor.

[0020] Figure 1 is a transverse sectional view of an orbiting disk structure provided by an embodiment of the present application; Figure 2 is Figure 1 is a sectional view in the A-A direction in Figure 3 is a transverse sectional view of a dynamic disc structure in another working condition provided by an embodiment of the present application; Figure 4 is a longitudinal sectional view of a dynamic disc structure provided by an embodiment of the present application; Figure 5 is a transverse sectional view of a dynamic disc structure in another form of a sink provided by an embodiment of the present application; Figure 6 is a sectional view of an oil supply assembly when the oil supply assembly is in an initial state in a dynamic disc structure provided by an embodiment of the present application; Figure 7 is a sectional view of an oil supply assembly when a pressing plate body in the oil supply assembly moves downward in a dynamic disc structure provided by an embodiment of the present application; Figure 8 is a sectional view of an oil supply assembly when the oil supply assembly includes three kinds of oil in a dynamic disc structure provided by an embodiment of the present application; Figure 9 is a sectional view of an oil supply assembly when a plurality of spaces are provided in a mounting frame in a dynamic disc structure provided by an embodiment of the present application.

[0021] wherein: 1, dynamic disc body; 2, sink; 3, oil supply assembly; 31, porous pressing plate; 32, lubricating medium; 311, mounting base; 312, pressing plate body; 321, first oil; 322, second oil; 323, third oil; 3101, mounting frame; 3102, partition; 3103, first space; 3104, second space; 3105, third space; 3106, first filter screen; 3107, second filter screen; 3108, third filter screen. DETAILED DESCRIPTION

[0022] To further explain the technical means and effects taken by the present application to achieve the predetermined purposes, the specific embodiments, structures, features and effects according to the present application are described in detail below in combination with the drawings and preferred embodiments. In the following description, different "an embodiment" or "embodiments" do not necessarily refer to the same embodiment. In addition, the specific features, structures, or characteristics in one or more embodiments can be combined in any suitable form.

[0023] In the description of the present application, it should be clear that the terms "first", "second" and the like in the description of the present application and claims and the above-mentioned drawings are used to distinguish similar objects, and do not necessarily describe a specific order or sequence; the terms "vertical", "transverse", "longitudinal", "front", "back", "left", "right", "up", "down", "horizontal" indicate the orientation or positional relationship shown in the drawings, and are only for the convenience of describing the present application, and do not mean that the devices or elements referred to must have a specific orientation or position, so it cannot be understood as a limitation on the present application.

[0024] In the description of the present application, it should be noted that unless otherwise specified and limited, the terms "mounting", "connecting", "connecting" should be understood broadly, for example, it can be fixedly connected, or it can be detachably connected, or integrally connected; it can be mechanically connected, or it can be electrically connected; it can be directly connected, or it can be indirectly connected through an intermediate medium. For those skilled in the art, the specific meaning of the above terms in the present application can be understood according to the specific circumstances.

[0025] Embodiment 1 The present embodiment provides a kind of runner structure, as shown in Figures 1-9 The runner structure includes runner body 1, the exhaust center side of the runner body 1 is provided with sink 2, sink 2 has oil supply assembly 3 in it;The oil supply assembly 3 includes porous pressing plate 31 and lubricating medium 32 arranged below the porous pressing plate 31, wherein the lubricating medium 32 is configured to soften when the central cavity of the runner body 1 reaches a predetermined temperature and pressure, and to release lubricating oil drops through the holes of the porous pressing plate 31.

[0026] The exhaust center side of the runner body 1 is machined with a sink 2, which is used to accommodate the oil supply assembly 3;The oil supply assembly 3 is composed of a porous pressing plate 31 and a lubricating medium 32, wherein the porous pressing plate 31 covers the opening part of the sink 2, and the lubricating medium 32 is filled inside the sink 2 and below the porous pressing plate 31;The porous pressing plate 31 and the inner wall of the sink 2 can be fixed by mechanical buckle or threaded connection, so as to encapsulate the lubricating medium 32 in the sink 2, so as to keep it stable in non-working state.

[0027] The sink 2 provides installation space for the oil supply assembly 3 and fixes it in the exhaust center area of the runner body 1;The oil supply assembly 3 serves as a whole unit, responsible for providing lubrication to the runner central cavity under certain working conditions;The porous pressing plate 31 not only plays a closing and supporting role, but also allows the lubricating medium 32 to be released in the form of oil drops under pressure;The lubricating medium 32 is a solid grease that can soften at high temperature and high pressure, which is essentially converted into a flowable lubricating phase when a certain temperature and pressure condition is reached, realizing on-demand lubrication.

[0028] During normal operation of the compressor, when the pressure and temperature of the central cavity of the moving disc rise to a certain level, the lubricating medium 32 begins to soften. At the same time, the high-pressure gas acts on the porous pressure plate 31, which applies pressure to the lubricating medium 32. Under the combined action of temperature and pressure, the lubricating medium 32 gradually changes from a solid to a semi-fluid state and is squeezed out through the holes of the porous pressure plate 31, forming fine oil droplets. These oil droplets are sent into the high-pressure area where the moving disc and the stationary disc mesh, playing a role in lubrication, sealing and cooling. More specifically, when the operating conditions ease and the temperature and pressure of the central cavity drop, the lubricating medium 32 solidifies again, and the oil supply process automatically stops, thus realizing a passive oil supply mechanism that only starts under harsh operating conditions.

[0029] In this embodiment, since the lubricating medium 32 is placed in the sink 2 on the exhaust center side of the moving disc and released under the control of the porous pressure plate 31, it can directly supply oil to the high-pressure and high-temperature central cavity area, making up for the shortcomings of the traditional peripheral oil supply method that cannot effectively lubricate the central area. Furthermore, this structure uses the high temperature and high pressure of the working condition to trigger the oil supply, without relying on complex external oil circuits or adding extra oil holes to supply oil. This avoids the problems of reduced compression efficiency and increased oil discharge rate caused by excessive oil volume, and simplifies the overall structure of the moving disc, eliminating the complex oil passage system used for lubrication in the traditional moving disc, and achieving the unity of structural optimization and energy efficiency improvement.

[0030] In a specific embodiment, such as Figure 6 and Figure 7 As shown, the porous pressure plate 31 includes a mounting base 311 and a pressure plate body 312. The pressure plate body 312 has multiple holes. The pressure plate body 312 is movably disposed within the mounting base 311. The pressure plate body 312 is located above the lubricating medium 32 and moves downward to squeeze the lubricating medium 32 when under pressure.

[0031] The porous pressure plate 31 structure consists of two main parts: the mounting base 311 and the pressure plate body 312. The mounting base 311 is a ring-shaped or frame-type fixing component whose outer contour matches the inner wall shape of the recess 2 on the moving disc body 1, and is fixedly installed inside the recess 2 by interference fit, threaded connection, or snap-fit ​​connection. The pressure plate body 312 is a plate-shaped component with multiple micro-holes, independent of the mounting base 311. It is placed inside the cavity of the mounting base 311, and its dimensions allow for a small range of axial movement within the confined space of the mounting base 311. The pressure plate body 312 is located directly above the lubricating medium 32, in direct contact with the upper surface of the lubricating medium 32. Its position is constrained by the side walls and top structure of the mounting base 311, ensuring that it can only move in the direction towards the lubricating medium 32 when under pressure.

[0032] In this structure, the mounting base 311 first reliably installs and fixes the entire oil supply assembly 3 in the groove 2 of the moving plate body 1, realizing modular assembly; secondly, it provides a precise guide and moving track for the movable pressure plate body 312, restricting the pressure plate body 312 to move up and down within a preset range, preventing it from tilting or deviating, and ensuring the stability and directionality of the movement. The core function of the pressure plate body 312 is to directly bear the pressure from the high-pressure gas in the compression chamber and transmit this pressure to the lubricating medium 32 below; furthermore, the multiple holes distributed on the pressure plate body 312 are the only channels for the lubricating medium 32 to precipitate after softening into lubricating oil, and the size and distribution of these holes determine the amount and dispersion of lubricating oil droplets.

[0033] The mounting base 311 and the pressure plate body 312 work together through a movable mating relationship, producing significant technical effects. When the pressure in the central cavity of the moving plate increases, the high-pressure gas acts on the upper surface of the pressure plate body 312, pushing it downwards. Because the mounting base 311 provides stable support and precise guidance, the pressure plate body 312 can smoothly and vertically compress the lubricating medium 32 below. This design efficiently converts the pressure energy of the gas into mechanical compression energy on the lubricating medium 32, enhancing the compression effect and ensuring continuous and stable compression force even under pressure fluctuations. More specifically, compared to a fixed cover plate, this movable pressure plate design is more sensitive and rapid in its pressure response, more promptly converting pressure changes into oil supply actions, thereby achieving precise control of on-demand oil supply. The resulting technical benefits are twofold. On one hand, it optimizes pressure transmission efficiency, making lubricant precipitation more controllable and uniform, avoiding fluctuations in oil volume. On the other hand, this modular, movable design enhances adaptability to different working conditions, ensuring that the oil supply component 3 can be immediately activated and work effectively when the pressure in the central cavity increases, and that the pressure plate body 312 may return to its original position due to its own elasticity or grease rebound when the pressure decreases, thereby reducing unnecessary oil precipitation. Ultimately, this improves the overall accuracy, responsiveness, and system efficiency of lubrication. Of course, to ensure timely reset of the pressure plate body 312, a spring can also be installed under the pressure plate body 312. When the pressure plate body 312 moves downward, the spring is compressed and stores potential energy; when the pressure disappears, the restoring force of the spring allows the pressure plate body 312 to quickly reset.

[0034] In a specific embodiment, the mesh size and aperture of the pressure plate body 312 are configured to allow the squeezed lubricating medium 32 to pass through when the central cavity of the moving disc body 1 reaches the predetermined pressure.

[0035] The size and density of the holes on the pressure plate body 312 are precisely designed and selected. Mesh count refers to the number of holes per unit area, while aperture refers to the diameter of each hole. This configuration means that the optimal combination of mesh count and aperture required for the pressure plate body 312 needs to be calculated and determined in reverse, based on the physical properties of the lubricating medium 32, especially its viscosity, flowability, and compressibility after softening, as well as the target pressure value that the moving disc center cavity needs to achieve under specific harsh operating conditions. For example, if the target trigger pressure is high, a configuration with a smaller mesh count and finer aperture may be chosen to increase the resistance to grease passage and ensure that the extrusion effect can only be achieved under sufficiently high pressure; conversely, if a system that is more sensitive to pressure is desired, a design with a larger mesh count and slightly larger aperture may be used.

[0036] This embodiment achieves precise pressure triggering and quantitative control of oil supply behavior. By matching the physical characteristics of the pressure plate body 312 with the system's target operating pressure point, it ensures that the oil supply component 3 will not malfunction under non-target pressures, thereby avoiding waste of lubricating oil and reduction in energy efficiency. More specifically, only when the compression process truly enters the harsh conditions of high pressure and high temperature, and the pressure in the central cavity precisely reaches the preset predetermined pressure value, is the force acting on the pressure plate body 312 just sufficient to overcome the flow resistance of its orifices to the softened lubricating medium 32, thus starting to stably precipitate oil droplets. This design synchronizes the lubricating oil supply with the actual load and demand of the compressor. Furthermore, by restricting the precipitation channel, it essentially acts as a metering valve, ensuring that the amount of oil supplied with each trigger is controlled and uniform, preventing problems of excessive or insufficient oil supply, and ultimately optimizing lubrication efficiency. While ensuring that the high-pressure cavity is fully lubricated and sealed, it minimizes the negative impact on the compressor's energy efficiency.

[0037] In a specific embodiment, the lubricating medium 32 includes at least two types of grease modules, each of which has a different melting point.

[0038] The lubricating medium 32 comprises at least two types of grease modules, each with a different melting point. This characteristic means that the lubricating medium 32 is not composed of a single-component grease, but rather of two or more physically independent or coexisting grease units. Each grease unit is a grease module, and these different grease modules each possess a specific melting temperature distinct from the others. For example, a grease module with a lower melting point and a grease module with a higher melting point can be placed together in the settling tank 2 in a partitioned filling manner to form an integral composite lubricating medium 32.

[0039] Because compressors may experience a wide range of temperature variations during actual operation, a single lubricating grease may only be effective near a specific temperature point. However, by employing multiple grease modules with different melting points, a gradient response system covering a wider temperature range can be constructed. When the temperature of the central cavity begins to rise but has not yet reached its maximum value, the grease module with the lower melting point softens first and begins to release lubricating oil through the holes in the pressure plate body 312, providing initial lubrication assurance. As the operating conditions further deteriorate and the temperature continues to rise and reaches a higher threshold, the grease module with the higher melting point then begins to soften and participate in oil supply, thereby providing additional lubricant to cope with more extreme pressure and thermal loads. This staged triggering oil supply mechanism ensures that the lubricating oil supply can be more smoothly and continuously matched with actual needs throughout the entire temperature rise process, avoiding sudden changes in the oil supply near the critical temperature point, thus achieving a more stable and reliable lubrication effect.

[0040] In a specific embodiment, such as Figure 8 As shown, the lubricating medium 32 includes a first grease 321, a second grease 322, and a third grease 323 arranged horizontally side by side, with the melting points of the first grease 321, the second grease 322, and the third grease 323 increasing sequentially.

[0041] More specifically, the first grease 321 can be a refined paraffin wax or certain low-melting-point synthetic waxes, which typically begin to soften and exhibit good lubricity in the 100°C-110°C range. The second grease 322 can be a microcrystalline wax with an intermediate melting point or a specially formulated composite wax with a melting point range designed between 110°C and 120°C to fill the transition gap between low-temperature and high-temperature lubrication. The third grease 323 can be a polyethylene wax with a melting point greater than 120°C, capable of providing reliable lubrication at the highest operating temperature.

[0042] The lubricating medium 32 in this embodiment includes a first grease 321, a second grease 322, and a third grease 323 arranged horizontally side by side, with their melting points increasing sequentially. That is to say, the three greases with different melting points are not mixed together, but are physically arranged side by side and filled together in the sink 2. They can be separated into independent blocks by partitions, or they can be different areas that are in close contact but not fully mixed, thus forming three parallel lubrication units in space.

[0043] Because the three types of grease are arranged horizontally side by side, their positions correspond to slight temperature distribution differences or pressure transmission paths that may exist within the central cavity of the moving disc. When high-temperature, high-pressure gas acts on the pressure plate body 312, the three greases react simultaneously according to the local operating conditions directly above them. The first grease 321, with the lowest melting point, responds first to the temperature of the area directly below it and begins supplying oil. As the overall operating conditions worsen and the temperature continues to rise, the second grease 322 and the third grease 323 sequentially begin supplying oil to their corresponding areas. This ensures that the lubricant precipitation does not start from a single point, but rather from multiple areas, starting almost simultaneously and gradually increasing according to actual needs. Furthermore, this design greatly enhances the coverage of lubrication requirements within complex cavities, ensuring that regardless of the local micro-temperature distribution across the vast surface of the central compression cavity of the moving disc, grease modules with corresponding melting points can provide timely lubrication. This avoids the uneven coverage problems that may occur with single-point oil supply, thereby improving the overall reliability of the high-pressure seal and the uniformity of its anti-wear performance, while maintaining the high-efficiency characteristics of the system's on-demand oil supply.

[0044] In a specific embodiment, such as Figure 8 and Figure 9 As shown, the porous pressure plate 31 includes a mounting frame 3101, and the mounting frame 3101 has a partition 3102. The partition 3102 divides the mounting frame 3101 into a first space 3103, a second space 3104, and a third space 3105. The first grease 321, the second grease 322, and the third grease 323 are located in the first space 3103, the second space 3104, and the third space 3105, respectively. The porous pressure plate 31 also includes a first filter screen 3106, a second filter screen 3107, and a third filter screen 3108 that cooperate sequentially with the first grease 321, the second grease 322, and the third grease 323. The pore sizes of the first filter screen 3106, the second filter screen 3107, and the third filter screen 3108 increase sequentially.

[0045] The mounting frame 3101 constitutes the main structure of the entire assembly. Inside the mounting frame 3101, the internal volume is divided into three independent sub-spaces by a built-in partition 3102: a first space 3103, a second space 3104, and a third space 3105. This separation ensures that the three greases with different melting points, the first grease 321, the second grease 322, and the third grease 323, can be physically isolated and contained within their respective designated spaces, preventing them from mixing or migrating during solid-state storage. Furthermore, this embodiment equips each independent grease space with a dedicated filter: a first filter 3106 that works with the first grease 321, a second filter 3107 that works with the second grease 322, and a third filter 3108 that works with the third grease 323. Most importantly, the pore sizes of these three filters are designed to increase in a gradient relationship, which means that the first filter 3106 has the finest pores, the second filter 3107 has slightly larger pores, and the third filter 3108 has the sparsest pores.

[0046] In this embodiment, firstly, the physical partitioning achieved by the partition 3102 ensures the independence of the chemical and physical properties of the three greases with different characteristics under a fixed state, preventing the low-melting-point grease from prematurely affecting the performance of the high-melting-point grease, thus laying a reliable material foundation for staged oil supply. Secondly, customizing filters with different pore sizes for different greases is the essence of controlling lubricant precipitation behavior. The low-melting-point first grease 321 is the easiest to soften and flow, so using the first filter 3106 with the smallest pore size can effectively limit its rapid and excessive precipitation, preventing excessive oil supply when the operating conditions initially increase. Conversely, the high-melting-point third grease 323 is the most difficult to liquefy and requires greater extrusion pressure to pass through the filter. Therefore, using the third filter 3108 with the largest pore size helps to promote the smooth and sufficient precipitation of the softened grease when extremely high temperatures and pressures are reached, ensuring sufficient lubrication even under the worst operating conditions. This strategy of reversing the filter mesh size and grease melting point from low to high cleverly balances the contradiction between oil supply sensitivity and oil supply volume, enabling the entire system to automatically, smoothly, and proportionally increase the total supply of lubricating oil according to the severity of the working conditions.

[0047] In a specific embodiment, the volume percentage of the first grease 321 The volume percentage of the second grease 322 and the volume percentage of the third grease 323 They are respectively: The compressor's operating temperature range is divided into n consecutive temperature segments. For the compressor in the first The percentage of working time in each temperature range ( =1,2,...,n), For the first The representative temperature of each temperature range; , , These are the weighting coefficients of the first grease 321, the second grease 322, and the third grease 323 in their respective dominant temperature ranges; The weighting coefficients for the first grease 321 and the second grease 322 in the mixing temperature range. The weighting coefficients for the second grease 322 and the third grease 323 in the mixing temperature range. The weighting coefficients for the first grease 321, the second grease 322, and the third grease 323 in the mixing temperature range; , as well as These are the melting points of the first grease 321, the second grease 322, and the third grease 323, respectively.

[0048] First formula calculation This refers to the volume percentage of the first grease 321. The proportion of the first grease 321 should cover all operating temperature ranges where it may play a role. More specifically, the formula divides its contribution into three parts: when the system temperature is in its dominant range ( to When ), its weight is When the temperature rises to to In the mixing zone, the first oil 321 still acts together with the second oil 322, and their weights are... When the temperature reaches the highest range (exceeding) When all three factors work together, their weights are: .in, The compressor is represented in the first The percentage of operating time in each temperature range is an important statistic, ensuring that the lubricant configuration is based on the actual operation of the compressor, rather than ideal conditions. It is the representative temperature for each temperature range, and the median value of that range can usually be taken. , The equal weighting coefficients, determined experimentally, reflect the relative efficacy and importance of different oils at different temperature ranges. The second formula calculates... That is, the volume percentage of the second oil 322, its calculation logic is the same as Similarly, but only considering its dominant interval ( to Weight ) and the mixing range with the third oil 323 (more than Weight ), because when the temperature is lower At that time, the second oil 322 had not yet been activated. The third formula calculation... The volume percentage of the third oil 323 is the simplest to calculate, considering only the volume percentage above its melting point. Contribution (weight) within the highest temperature range This is because it is only needed to provide lubrication under these extreme operating conditions. The overall effect of these formulas is to transform the complex operating temperature range and time distribution of the compressor into a scientific and quantitative lubricating grease formula. This makes the final lubricating medium 32 no longer a simple mixture based on experience, but a smart material that can accurately match the actual operating conditions of the compressor, thereby maximizing lubrication efficiency and minimizing grease waste and energy loss in a statistical sense.

[0049] The compressor's total lubrication requirement is a time-weighted combination of the requirements for each temperature range. Within each temperature range, the lubrication requirement is shared by one or more active greases according to specific weighting coefficients. Therefore, for any given temperature range, the sum of the weighting coefficients of all active greases must be 1 (i.e., 100%) to ensure a self-consistent lubrication ratio within that range. More specifically, the weighting coefficients ( , , , , , The definition of ) needs to satisfy the following constraints to ensure consistency of calculations: To explain the formula more clearly, let's assume the following: The operating temperature range of a compressor is divided into three temperature segments: Segment 1: 95℃-105℃, represented by temperature T1=100℃. The compressor operates under these mild conditions for 70% of its time. Segment 2: 105℃-115℃, represented by temperature T2=110℃. The compressor operates under these moderate conditions for 25% of its time. Segment 3: ≥115℃, represented by temperature T3=120℃. The compressor operates under these extremely harsh conditions for 5% of its time.

[0050] The melting points of three types of oils are known: the melting point of the first oil, 321. =100℃, melting point of the second grease 322 =110℃, melting point of the third oil 323 =120℃.

[0051] Define weighting coefficients: ≤ < The weight of (i.e., the dominant range of the first oil 321) is such that only the first oil 321 is active in this range, therefore =1. (Second oil 322 and third oil 323 are inactive in this range, contributing 0). In ≤ < The weight of the mixture of first grease 321 and second grease 322 (i.e., the mixing zone) is where both are active. Experience shows that in this zone, first grease 321 still bears the main lubrication responsibility, and its weight... =0.7, then the weight of the second oil 322 is naturally 0.3. ≤ The weights of the three components (i.e., the mixed range) are determined, where all three are active. Experience shows that under these extreme conditions, the third oil (323) with the highest melting point is the most important, and its weights should be allocated accordingly. = 0.5. The second most important oil is 322, with a weight of [missing value]. =0.3. The first oil (321) has the smallest contribution, with a weight of 0.3. =0.2.

[0052] Determine the temperature range for each element: T1=100℃: Satisfied ≤100℃< The conditions are met. Therefore, it belongs to the dominant region of the first oil 321. T2=110℃: satisfies the condition. ≤110℃< Therefore, it falls within the mixing range of the first and second oils. T3 = 120℃: satisfies the condition. The condition is ≤120℃. Therefore, it belongs to the mixed range of the three.

[0053] Calculate the volume percentage of the first oil 321 : First summation: Only T1 belongs to this interval. Contribution: P1* =70%*1=0.70.

[0054] The second summation: Only T2 belongs to this interval. The contribution is: P2* =25%*0.7=0.175.

[0055] The third summation: Only T3 belongs to this interval. The contribution is: P3* =5%*0.2=0.01.

[0056] therefore, =0.70+0.175+0.01=0.885 (i.e. 88.5%).

[0057] Calculate the volume percentage of the second grease 322. : First summation: Only T2 belongs to this interval. Contribution: P2* =25%*0.3=0.075.

[0058] The second summation: Only T3 belongs to this interval. The contribution is: P3 * = 5% * 0.3 = 0.015.

[0059] therefore, =0.075+0.015=0.09 (i.e. 9.0%).

[0060] Calculate the volume percentage of the third oil 323. : Summation: Representing temperature T3 = 120℃ satisfies the condition. ≤120℃, falls within this range. Contribution: P3* =5%*0.5=0.025.

[0061] therefore, =0.025 (i.e., 2.5%).

[0062] This example demonstrates how to scientifically calculate the precise volume ratio of three lubricating greases based on the compressor's actual operating temperature distribution and a self-consistently defined set of weighting coefficients. The results clearly indicate that since the compressor operates at a relatively low temperature (100°C) for the vast majority of the time, a large quantity of the first grease 321, which is effective at this temperature, is required; while the third grease 323, needed only under a few extreme conditions, is required in very small quantities. This calculation method achieves a high degree of optimization in lubricant configuration, enabling on-demand distribution, thereby maximizing cost savings and minimizing potential performance losses while ensuring lubrication effectiveness.

[0063] In a specific embodiment, the profile of the sink 2 is adapted to the gas pressure distribution at the exhaust center of the moving disc body 1.

[0064] The shape and orientation of the outer edge of the recess machined on the end face of the moving disc body 1 in the groove 2 are not simple circles or regular geometric shapes, but are specially designed, such as... Figure 5As shown, this is designed to match the gas pressure distribution in the central region of the compressor's moving disk during operation. More specifically, during compression, due to the complex motion of the rotating disk meshing, the gas pressure at different locations in the central cavity is not uniform, typically forming specific high-pressure zones and pressure gradients. Here, "matching" means that the profile of the groove 2 follows this natural pressure distribution. For example, in areas of higher gas pressure, the boundary of the groove 2 may extend outwards or its profile may approximately coincide with the shape of the isobars, thus ensuring that the area covered by the groove 2 corresponds to the high-pressure points that most require enhanced lubrication.

[0065] Because the contour of the settling tank 2 matches the actual gas pressure distribution, the oil supply component 3 housed within it is directly positioned in the high-pressure core operating area. This means that when the local pressure increases, the force acting on the corresponding area above the porous pressure plate 31 becomes more concentrated and intense, thus more effectively squeezing the lubricating medium 32 below and causing it to precipitate lubricating oil through the holes of the porous pressure plate 31. Furthermore, this adaptive design ensures that the release of lubricating oil is spatially highly synchronized with the actual pressure demand within the compression chamber; that is, the higher the pressure, the stronger the driving force for oil supply, and the more timely and sufficient the supply of lubricating oil. Its effects are twofold: firstly, it optimizes the utilization efficiency of lubricating oil, ensuring that every unit of lubricating grease is used where it is most needed, greatly enhancing the sealing effect and wear resistance in high-pressure areas; secondly, it avoids unnecessary slight leakage of grease that may occur in low-pressure areas, thereby saving the consumption of lubricating medium 32 at the system level and reducing the potential negative impact on compression efficiency due to excessive oil volume, ultimately achieving a balance between lubrication performance and operational economy.

[0066] In a specific embodiment, the outer contour of the mounting base 311 is adapted to the contour of the sink 2 so that the oil supply assembly 3 can be stably installed in the sink 2 of different shapes.

[0067] The mounting base 311, as the core support structure of the oil supply assembly 3, is specially designed with an external shape that mirrors the cavity shape inside the sink 2. This means that if the machining outline of the sink 2 is circular, then the shape of the mounting base 311 will be correspondingly made circular; if the sink 2 is designed with an irregular and complex shape to accommodate pressure distribution, then the shape of the mounting base 311 will also be precisely machined to perfectly match its complex shape. This fit ensures that when the mounting base 311 is placed into the sink 2, the contact surfaces between the two can fit together to the maximum extent, thus achieving a tight fit.

[0068] Because different scroll compressor models have different gas force distributions and structural designs at the center of the moving plate, the shape of the slot 2 may vary. By adapting the outer contour of the mounting base 311 to these different slot 2 contours, the same core oil supply concept and component design can be quickly and securely installed into slots 2 of various shapes simply by replacing a customized mounting base 311. More specifically, this tight shape fit first provides excellent mechanical stability, preventing any unnecessary movement or loosening of the oil supply component 3 within the slot 2 under high-speed operation and strong vibration, ensuring its precise and constant working position. Furthermore, it optimizes force transmission, because the tight fit ensures that the gas pressure in the compression chamber can be transmitted more effectively and without loss to the internal pressure plate body 312 and lubricating medium 32 through the mounting base 311, thereby ensuring consistent oil supply response.

[0069] The wear-resistant moving disc uses the moving disc body 1 as its core carrier. A groove 2 with a specific profile is machined on its exhaust center side, the design of which matches the gas pressure distribution in this area during compression. The groove 2 houses the entire oil supply assembly 3, which is securely installed by the tight fit between the shape of its mounting base 311 and the profile of the groove 2. The core of the oil supply assembly 3 consists of a lubricating medium 32 and a porous pressure plate 31. The lubricating medium 32 is composed of grease modules with different melting points (such as first grease 321, second grease 322, and third grease 323) mixed or packaged according to a scientifically calculated volume ratio, and these are filled inside the mounting base 311. The pressure plate body 312 of the porous pressure plate 31 is movably disposed within the mounting base 311, above the lubricating medium 32. Its mesh size and pore size are precisely configured, and depending on the grease module, it may be equipped with filters of different pore sizes, such as a first filter 3106, a second filter 3107, and a third filter 3108.

[0070] When the compressor starts up and operates under normal conditions, the temperature and pressure of the central cavity of the moving plate body 1 are low, failing to reach the melting point threshold of any grease module in the lubricating medium 32. Therefore, the lubricating medium 32 remains solid, and its high viscosity prevents it from passing through the holes of the pressure plate body 312. At this time, the oil supply system is in a dormant state and does not affect the compression process, ensuring that the compressor's energy efficiency is not compromised.

[0071] When the compressor load increases and enters harsh operating conditions, the gas in the central cavity of the moving plate body 1 is compressed to extremely high pressure and temperature. This high-temperature environment causes the temperature of the lubricating medium 32 to gradually rise through heat conduction. The heat first causes the first grease 321, which has the lowest melting point, to soften. As the temperature further rises, the second grease 322 and the third grease 323 successively reach their melting points and begin phase change. At the same time, the high-pressure gas applies enormous pressure to the upper surface of the pressure plate body 312. This pressure is evenly transmitted to the pressure plate body 312 through the guidance of the mounting base 311, causing it to move downwards and mechanically compress the softened lubricating medium 32.

[0072] Under the combined effects of thermal softening and mechanical extrusion, the lubricating grease, now in a semi-fluid state, is forced through precisely calculated apertures on the pressure plate body 312, or through matching filters (such as the first filter 3106, the second filter 3107, and the third filter 3108). More specifically, the grease precipitation process is staged and controlled, with low-melting-point grease precipitating first, followed by high-melting-point grease, and the pore size gradient of the filters ensures that the precipitation amount of different greases matches the operating conditions. The precipitated lubricating oil forms fine droplets, which are directly transported to the high-pressure, high-temperature region where the moving and stationary discs mesh.

[0073] These oil droplets immediately take effect, lubricating the sidewalls and end faces of the vortex teeth to reduce friction and wear; simultaneously, they form an oil film in the crescent-shaped chamber, enhancing the sealing effect and preventing high-pressure gas leakage; and they can absorb some of the heat of compression, aiding in cooling. Once the operating conditions ease, the temperature and pressure of the central cavity decrease, the lubricating medium 32 loses its heat source, cools and solidifies again, its viscosity returns to normal, and the oil supply process automatically stops, awaiting the next trigger.

[0074] Example 2 This embodiment provides a compressor, which includes the moving disc structure described in Embodiment 1.

[0075] The compressor provided in this embodiment achieves an intelligent and passive on-demand lubrication capability by integrating the oil supply component on the exhaust center side of its core component, the moving disc body 1. This means that lubricating oil is precisely released into the central cavity only when the compressor operates under harsh conditions of high pressure and high temperature, and when the lubrication demand is most urgent. Under most other normal operating conditions, oil supply is completely stopped. This working mode solves the dilemma in traditional compressor design: it ensures that the meshing area between the moving and stationary discs is adequately lubricated and effectively sealed under extreme conditions, greatly reducing the risk of wear and gas leakage, and improving the durability and reliability of the compressor; it also completely avoids the negative impact of excessive oil supply over the years to ensure extreme operating conditions, significantly reducing the compression power loss and efficiency decline caused by excessive lubricating oil, while effectively controlling the system's oil discharge rate.

[0076] In summary, it is readily understood by those skilled in the art that, without conflict, the aforementioned advantageous technical features can be freely combined and superimposed.

[0077] The above are merely preferred embodiments of the present invention and are not intended to limit the present invention in any way. Any simple modifications, equivalent changes and alterations made to the above embodiments based on the technical essence of the present invention shall still fall within the scope of the technical solution of the present invention.

Claims

1. A moving disk structure, characterized in that, The moving disc structure includes a moving disc body, and a sink groove is provided on the exhaust center side of the moving disc body. The sink groove contains an oil supply component. The oil supply component includes a porous pressure plate and a lubricating medium disposed below the porous pressure plate. The lubricating medium is configured to soften when the central cavity of the moving disc reaches a predetermined temperature and a predetermined pressure, and to precipitate lubricating oil droplets through the holes of the porous pressure plate.

2. The moving disk structure according to claim 1, characterized in that, The porous pressure plate includes a mounting base and a pressure plate body. The pressure plate body has multiple holes and is movably disposed in the mounting base. The pressure plate body is located above the lubricating medium and moves downward to squeeze the lubricating medium when under pressure.

3. The moving disk structure according to claim 2, characterized in that, The mesh size and aperture of the pressure plate body are configured to allow the compressed lubricating medium to pass through when the predetermined pressure is reached in the central cavity of the moving disc body.

4. The moving disk structure according to claim 1, characterized in that, The lubricating medium includes at least two types of grease modules, each with a different melting point.

5. The moving disk structure according to claim 1, characterized in that, The lubricating medium includes a first grease, a second grease, and a third grease arranged horizontally side by side, with the melting points of the first grease, the second grease, and the third grease increasing sequentially.

6. The moving disk structure according to claim 5, characterized in that, The porous pressure plate includes a mounting frame with a partition that divides the mounting frame into a first space, a second space, and a third space. The first grease, the second grease, and the third grease are located in the first space, the second space, and the third space, respectively. The porous pressure plate also includes a first filter screen, a second filter screen, and a third filter screen that cooperate sequentially with the first grease, the second grease, and the third grease. The pore sizes of the first filter screen, the second filter screen, and the third filter screen increase sequentially.

7. The moving disk structure according to claim 5, characterized in that, Volume percentage of the first oil The volume percentage of the second oil and the volume percentage of the third oil. They are respectively: The compressor's operating temperature range is divided into n consecutive temperature segments. For the compressor in the first The percentage of working time in each temperature range ( = , 2, ..., n), For the first The representative temperature of each temperature range; , , These are the weighting coefficients for the first, second, and third oils in their respective dominant temperature ranges; The weighting coefficients for the first and second oils in the mixing temperature range are: The weighting coefficients for the second and third oils in the mixing temperature range. The weighting coefficients for the first, second, and third oils in the mixing temperature range; , as well as These are the melting points of the first, second, and third greases, respectively.

8. The moving disk structure according to claim 1, characterized in that, The profile of the settling groove is adapted to the gas pressure distribution at the exhaust center of the moving disc body.

9. The moving disk structure according to claim 2, characterized in that, The outer contour of the mounting base is adapted to the contour of the sink, so that the oil supply assembly can be stably installed in the sink of different shapes.

10. A compressor, characterized in that, The compressor includes the moving disc structure as described in any one of claims 1-9.

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