Compressor and air conditioning system

Abstract

The application relates to a compressor and an air conditioning system in the technical field of compressors, and belongs to the high-efficiency energy-saving industry. The compressor comprises a static disc and an end cover buckled on the static disc, an exhaust cavity is formed between the static disc and the end cover, an exhaust cavity inlet is arranged on the static disc, an exhaust cavity outlet is arranged on the end cover, an oil return structure is formed in the exhaust cavity and located on the side wall opposite to the static disc, and the oil return structure comprises a plurality of main oil grooves. The first ends of the plurality of main oil grooves are in communication with the exhaust cavity outlet, and the second ends of the plurality of main oil grooves extend radially along the side wall with the exhaust cavity outlet as the center. The oil return structure can absorb and guide the retained oil accumulated in the exhaust cavity, so that the oil flows out of the exhaust cavity outlet and returns to the bottom oil pool, thereby reducing the risk of compressor oil shortage and lubrication failure caused by the retention and accumulation of oil in the corner of the cavity under the microgravity environment.

Description

Technical Field

[0001] This invention relates to the field of compressor technology, and more particularly to a compressor and an air conditioning system. Background Technology

[0002] In the field of compressor-related technologies, such as scroll compressors, when a scroll compressor is working, the refrigerant carries lubricating oil from the compressor pump body and enters the exhaust chamber. The oil droplets in the refrigerant impact the internal parts in the exhaust chamber, are gradually filtered, and accumulate and are stored in the exhaust chamber. Traditionally, the exhaust chamber relies solely on gravity for natural return, but under microgravity conditions or when the oil is easily trapped in the corners of the chamber, the problem of oil accumulation is prominent, resulting in a reduction in the amount of usable oil in the compressor, which affects the compressor's lubrication performance and energy efficiency. Summary of the Invention

[0003] The technical problem to be solved by the present invention is that in the prior art, oil accumulates in the exhaust chamber of the scroll compressor, which leads to a reduction in the amount of oil available in the compressor, affecting the lubrication performance and energy efficiency of the compressor. To address this issue, a compressor and an air conditioning system are provided.

[0004] This invention aims to provide a compressor, including a stationary plate and an end cover fastened to the stationary plate, wherein an exhaust chamber is formed between the stationary plate and the end cover, the stationary plate has an exhaust chamber inlet, and the end cover has an exhaust chamber outlet, characterized in that: An oil return structure is provided on the side wall of one end cap of the exhaust chamber, the oil return structure comprising: Multiple main oil tanks, the first end of each of the multiple main oil tanks is connected to the exhaust chamber outlet, and the second end of each of the multiple main oil tanks extends radially along the side wall with the exhaust chamber outlet as the center.

[0005] In some embodiments, the depth of the main oil tank gradually decreases from the first end to the second end.

[0006] In some embodiments, the depth of the main oil tank ranges from 1 mm to 2 mm.

[0007] In some embodiments, the main oil tank is configured as a straight strip-shaped tank; A first preset angle α is formed between two adjacent main oil tanks, where α satisfies: 5°≤α≤15°.

[0008] In some embodiments, the second end of the main oil tank is connected to at least one branch oil tank; The branch oil tank and the corresponding main oil tank form a second preset angle β, where β satisfies: 15°≤β≤25°.

[0009] In some embodiments, the width of the main oil tank ranges from 0.8 mm to 1.0 mm, and the width of the branch oil tank ranges from 0.5 mm to 1.0 mm.

[0010] In some embodiments, the oil return structure further includes: an oil collection trough; The oil collecting groove is disposed through the outlet of the exhaust chamber, and the oil collecting groove is connected to the outlet of the exhaust chamber. Of the plurality of main oil tanks, one of the main oil tanks is connected to the exhaust chamber outlet; A portion of the remaining main oil tanks is connected to the converging oil tank and is located on one side of the exhaust chamber outlet, while another portion of the remaining main oil tanks is connected to the converging oil tank and is located on the other side of the exhaust chamber outlet.

[0011] In some embodiments, the connection points between the plurality of main oil tanks, the converging oil tank, and the exhaust chamber outlet are all constructed as arc-shaped transition structures.

[0012] In some embodiments, an oil return channel is formed inside the end cover, and the exhaust chamber outlet is connected to the bottom oil sump inside the compressor through the oil return channel; The compressor further includes a gas-liquid separator, which is connected to the exhaust chamber outlet. The liquid phase outlet of the gas-liquid separator is connected to the bottom oil sump inside the compressor through the oil return channel, and the gas phase outlet is connected to the outside of the end cover.

[0013] In some embodiments, an air conditioning system is provided, characterized in that it includes the compressor described above.

[0014] The solution provided by this invention has the following advantages compared with the prior art: In this compressor, by designing an oil return structure, multiple main oil grooves with capillary action are arranged radially and interconnected on the side wall of the end cover located inside the exhaust chamber. This can absorb and guide the stagnant oil accumulated in the exhaust chamber, allowing the oil to flow out from the exhaust chamber outlet and return to the bottom oil sump. This reduces the risk of oil stagnation and accumulation in the corners of the cavity under microgravity, which could lead to compressor oil shortage and lubrication failure. At the same time, this oil return structure does not require additional new components, thus reducing the compressor's production cost and failure rate. Attached Figure Description

[0015] The accompanying drawings, as part of this invention, are used to provide a further understanding of the invention. The illustrative embodiments and descriptions of the invention are used to explain the invention, but do not constitute an undue limitation of the invention. Obviously, the drawings described below are merely some embodiments, and those skilled in the art can obtain other drawings based on these drawings without creative effort. In the drawings: Figure 1 This is a partial cross-sectional view of the compressor shown in an embodiment of the present invention; Figure 2 This is a schematic diagram of the oil return structure on the end cap as shown in an embodiment of the present invention; Figure 3 This is a schematic diagram of the oil return structure shown in an embodiment of the present invention; Figure 4 This is a schematic diagram of the static disk structure shown in an embodiment of the present invention; Figure 5 This is a cross-sectional view of the oil return structure on the end cap as shown in an embodiment of the present invention; Figure 6 This is a simulation diagram of the oil accumulation area on the side wall of the end cap, as shown in an embodiment of the present invention. (The blue area represents the refrigerant, and the red area represents the lubricating oil.) In the diagram: 1-Stationary plate, 101-Exhaust chamber, 102-Exhaust chamber inlet, 103-Sealing strip, 2-End cover, 201-Exhaust chamber outlet, 202-Side wall, 203-Return oil channel, 3-Main oil tank, 301-Branch oil tank, 4-Gathering oil tank, 5-Gas-liquid separator, 501-Liquid phase outlet, 502-Gas phase outlet, 6-Limit valve plate.

[0016] It should be noted that these accompanying drawings and textual descriptions are not intended to limit the scope of the invention in any way, but rather to illustrate the concept of the invention to those skilled in the art by referring to specific embodiments. Detailed Implementation

[0017] In the description of this invention, it should be noted that the terms "inner" and "outer", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings. They are only for the convenience of describing this invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limiting this invention.

[0018] In the description of this invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," "linking," "contact," and "communication" should be interpreted broadly. For example, they can refer to fixed connections, detachable connections, or integral connections; they can refer to mechanical connections or electrical connections; they can refer to direct connections or indirect connections through an intermediate medium. Those skilled in the art can understand the specific meaning of the above terms in this invention based on the specific circumstances.

[0019] When a scroll compressor is operating, refrigerant carrying lubricating oil is discharged from the pump body and enters the exhaust chamber. Oil droplets in the refrigerant impact internal components within the exhaust chamber, gradually being filtered and accumulating there. This reduces the amount of usable oil in the compressor, affecting lubrication performance and energy efficiency. Oil accumulation is a significant problem in existing technologies. For example, traditional exhaust chambers rely solely on gravity for natural return flow, but under microgravity conditions or when oil tends to stagnate in the corners of the chamber.

[0020] Based on this, the following embodiments are proposed.

[0021] Example 1: like Figure 1 and Figure 2 As shown, this embodiment provides a compressor, including a stationary plate 1 and an end cover 2 fastened to the stationary plate 1. An exhaust chamber 101 is formed between the stationary plate 1 and the end cover 2. An exhaust chamber inlet 102 is provided on the stationary plate 1, and an exhaust chamber outlet 201 is provided on the end cover 2. An oil return structure is provided on the side wall 202 of the end cover 2 on one side of the exhaust chamber 101. The oil return structure includes: Multiple main oil tanks 3, the first end of each of the multiple main oil tanks 3 is connected to the exhaust chamber outlet 201, and the second end of each of the multiple main oil tanks 3 extends radially along the side wall 202 with the exhaust chamber outlet 201 as the center.

[0022] In this embodiment, the compressor can be a scroll compressor. The oil return structure is designed to be directly integrated into the side wall 202 of the end cover 2 inside the exhaust chamber 101. Oil and other liquid fluids will return to the oil sump at the bottom of the compressor along the guide of the oil return structure. There is no need to add an oil distribution device, flow guide pipe and power transmission components in the compressor exhaust chamber 101. This simplifies the overall structure of the compressor and reduces the assembly difficulty and overall size of the compressor.

[0023] Specifically, multiple main oil tanks 3 extend radially along the sidewall 202 of the end cap 2, with the exhaust chamber outlet 201 as the center point. The first end of each main oil tank 3, the end closest to the exhaust chamber outlet 201, is interconnected with the exhaust chamber outlet 201. This radial layout allows the tanks of the multiple main oil tanks 3 to cover most of the sidewall 202 of the end cap 2, which is the main oil accumulation area within the exhaust chamber 101. This allows more oil to be guided into the main oil tanks 3 for backflow. Because the main oil tanks 3 have a grooved structure, capillary channels with guiding properties are formed inside the tanks. When oil accumulates on the surface of the sidewall 202 of the end cap 2 and forms a continuous oil film or droplets, the oil on the sidewall 202 is actively adsorbed into the main oil tank 3 by the capillary action of the liquid itself. The radially arranged main oil grooves 3 become multiple channels for collecting oil, absorbing the oil that is stagnant in various positions on the side wall 202 of the exhaust chamber 101 into the multiple grooves. This allows the oil that was originally stagnant in the corners of the chamber due to its inability to return due to gravity to flow, and under the guidance of the main oil grooves 3, it flows towards the exhaust chamber outlet 201 located in the center. When the oil in the exhaust chamber 101 continues to flow and converges to the exhaust chamber outlet 201, this oil will enter the oil return channel 203 inside the end cover 2 from the exhaust chamber outlet 201 and flow directly back to the oil sump at the bottom of the compressor, thus completing the return circulation of the lubricating oil. This oil return structure relies entirely on the active flow guidance system formed by the main oil groove 3 located on the side wall 202 of the end cover 2, combined with capillary action, to actively absorb, collect, and direct the oil flow. Regardless of whether the compressor is in a normal gravity environment or a microgravity environment, it can stably collect oil from various locations within the exhaust chamber 101, preventing oil accumulation and the formation of an oil pool inside the exhaust chamber 101. Simultaneously, the available oil inside the compressor can be continuously replenished, ensuring sufficient lubrication for all components, effectively improving the compressor's lubrication performance, reducing dry friction between components, lowering operating losses, and thus improving the overall operating efficiency of the compressor. The entire oil return process does not require additional power components to drive the oil flow, thereby reducing the compressor's manufacturing cost and also lowering the failure rate of components.

[0024] In one embodiment, the main oil groove 3 is integrally formed by milling, and the width of multiple main oil grooves 3 is completely consistent to ensure that the oil flow rate within the groove is consistent. The length of the main oil groove 3 can be adapted to different spaces at different locations on the side wall 202 of the end cap 2. For example, when the side wall 202 of the end cap 2 has a circular outline, the main oil groove 3 near the edge of the side wall 202 will be longer and extend to the outermost edge of the side wall 202, while the main oil groove 3 near the center of the side wall 202 will be shorter. The edge of the circular side wall 202 is the area where oil is most likely to accumulate in large areas. The longer main oil groove 3 can fully cover the oil retention area, while the shorter main oil groove 3 is responsible for guiding the small amount of oil in the center of the side wall 202, thereby ensuring that the oil on the entire side wall 202 of the end cap 2 can be successfully absorbed and collected, and guiding this oil to flow continuously towards the exhaust port outlet 201, thus avoiding the continuous retention of oil in the dead corners at the edge of the side wall 202 of the end cap 2.

[0025] The oil return structure has multiple main oil grooves 3 arranged radially and interconnectedly on the side wall 202 of the end cover 2 located inside the exhaust chamber 101. This structure can absorb and guide the oil that accumulates in the exhaust chamber 101, allowing the oil to flow out from the exhaust chamber outlet 201 and back to the bottom oil pool. This reduces the risk of oil accumulating in the corners of the cavity under microgravity conditions, which could lead to compressor oil shortage and lubrication failure. At the same time, this oil return structure does not require any additional new components, thus reducing the compressor's production cost and failure rate.

[0026] Optionally, in one implementation of this embodiment, such as Figures 1 to 3 , Figure 5 As shown, the depth of the main oil tank 3 gradually decreases from the first end to the second end.

[0027] In this embodiment, the main oil tank 3 is configured with a linearly varying depth. The end furthest from the exhaust outlet 201 (the second end) has a shallower tank depth, while the end closest to the exhaust outlet 201 (the first end) has a deeper tank depth. For example... Figure 5As shown in the cross-sectional view of the main oil tank 3, the bottom wall of the main oil tank 3, or the top wall of the tank, has an angle γ with the horizontal plane. The depth of the main oil tank 3 gradually decreases from the first end to the second end. At the shallower depth of the tank, the adsorption force generated by capillary action is stronger, which can firmly adsorb the oil droplets and oil film stuck on the edge of the side wall 202, and collect the scattered oil so that it can smoothly enter the main oil tank 3. As the oil flows towards the exhaust port outlet 201, the depth of the tank gradually increases, and the flow cross-sectional area inside the tank also increases. The flow space of the oil becomes more abundant. The deeper tank can also increase the driving force of the oil flow and reduce the probability of the oil flow stagnation due to the velocity decay caused by long-distance flow, ensuring that the oil can maintain a stable and smooth flow state throughout the main oil tank 3. When the amount of residual oil at different locations on the side wall 202 of the exhaust chamber 101 varies, the shallower tank can accurately absorb the small amount of dispersed oil at the edge of the side wall 202 of the end cap 2, while the deeper tank can accommodate a larger flow of oil flowing into the main oil tank 3, thus avoiding oil blockage inside the tank and achieving a combination of capillary action and oil flow.

[0028] In one embodiment, the depth of the main oil tank 3 changes linearly and gradually. The depth of the tank increases uniformly at a fixed ratio from the outlet end far from the exhaust chamber 101 to the end near the exhaust chamber outlet 201, and the depth change curve of the entire main oil tank 3 is a straight line. The linearly gradual tank allows the resistance to oil flow to change smoothly, keeping the oil flow rate stable and avoiding sudden changes in flow rate. This ensures a stable oil return effect over a long period, extends the service life of the tank structure, and makes the linearly gradual tank depth easier to process, with smaller dimensional errors and lower production costs. Therefore, it is suitable for small and medium-sized scroll compressors with stable operating conditions and small oil flow fluctuations.

[0029] By setting the main oil tank 3 to a gradually decreasing depth from near the exhaust chamber outlet 201 to far away from the exhaust chamber outlet 201, the shallow tank enhances the capillary adsorption capacity at the far end, and the deep tank improves the oil flow and driving capacity at the near end. This effectively solves the problems of speed decay, oil stagnation in the tank, and congestion during long-distance oil transportation. It further optimizes the oil transportation effect of the radial main oil tank 3, allowing the lubricating oil in the exhaust chamber 101 to flow smoothly throughout the process, and continuously ensuring the oil supply and lubrication effect of the compressor.

[0030] Optionally, in one implementation of this embodiment, such as Figures 1 to 3 , Figure 5 As shown, the depth of the main oil tank 3 ranges from 1 mm to 2 mm.

[0031] In this embodiment, the overall depth of the main oil tank 3 is between 1 mm and 2 mm. When the depth of the main oil tank 3 is between 1 mm and 2 mm, the spatial dimensions of the tank body are exactly matched with the surface tension and capillary action characteristics of the compressor refrigeration oil. In terms of oil reflux, controlling the tank depth within the range of 1 mm to 2 mm ensures that the tank body has a stable and strong capillary adsorption capacity, which can effectively and actively capture and collect the thin oil film and scattered oil droplets on the side wall 202 of the end cover 2, while avoiding the tank body being blocked by tiny impurities in the oil, and ensuring the tank body's ability to guide the flow of large flow of oil. In terms of structural strength, controlling the tank depth within the range of 1 mm to 2 mm ensures that the side wall 202 of the end cover 2 has sufficient thickness to resist the operating vibration of the compressor and the air pressure impact inside the exhaust chamber 101, reducing the risk of the end cover 2 cracking and deforming due to vibration during long-term high-speed operation of the compressor.

[0032] In one embodiment, the depth of the main oil tank 3 at the end furthest from the exhaust outlet 201 is 1 mm. The capillary adsorption effect is strongest when the tank depth is 1 mm, which can accurately and efficiently adsorb a thin oil film, prevent the oil from flowing randomly along the side wall 202, and avoid oil splashing. The depth of the main oil tank 3 at the end near the exhaust outlet 201 is 2 mm. This makes the internal flow area of ​​the main oil tank 3 larger. The larger tank space can reduce the flow resistance of the oil, enhance the oil's throughput, and ensure that the oil flows smoothly to the exhaust outlet 201.

[0033] By limiting the depth of the main oil trough 3 to between 1 mm and 2 mm, the capillary effect of the trough body, the structural strength of the side wall 202 of the end cover 2, and the production cost of the parts are taken into account. This oil return structure has multiple advantages, including stable collection of oil and guidance of its return flow, reduction of the probability of the trough body being blocked by impurities, and improvement of the structural strength of the end cover 2. This comprehensively improves the reliability and service life of the compressor.

[0034] Optionally, in one implementation of this embodiment, such as Figures 1 to 3 , Figure 5 As shown, the main oil tank 3 is constructed as a straight strip-shaped tank; a first preset angle α is formed between two adjacent main oil tanks 3, where α satisfies: 5°≤α≤15°.

[0035] In this embodiment, the main oil groove 3 is constructed as a straight strip-shaped groove structure, which is the simplest and most regular groove shape. Multiple straight strip-shaped main oil grooves 3 are arranged radially around the exhaust chamber outlet 201. Each straight strip-shaped main oil groove 3 extends straight from the exhaust chamber outlet 201 to the outer edge of the end cap 2 side wall 202, without any bends or corners inside the groove. The included angle between two adjacent main oil grooves 3 forms a first preset angle α. This included angle α determines the distribution density of the main oil grooves 3 on the end cap 2 side wall 202. The smaller the included angle α, the more main oil grooves 3 there are per unit area, the denser the groove distribution, and the more comprehensive the oil collection coverage, thus guiding more oil to return. The larger the included angle α, the fewer main oil grooves 3 there are per unit area, and the sparser the groove distribution. When there is less oil in the exhaust chamber 101, a larger included angle α can reduce the processing cost of the oil return structure. The oil return structure sets different included angles α based on the area of ​​the side wall 202 of the end cover 2 of the exhaust chamber 101, the compressor's discharge volume, and the amount of oil entrained in the exhaust chamber 101. This ensures that the distribution density of the main oil groove 3 is precisely matched to the actual oil accumulation in the exhaust chamber. This avoids both excessively dense groove distribution, which increases the processing cost of the end cover 2 and reduces the structural strength of the side wall 202, and excessively sparse groove distribution, which can lead to oil stagnation. During compressor operation, the oil accumulated on the side wall 202 of the end cover 2 is adsorbed and collected by the straight main oil groove 3 under capillary action. It then flows along the straight flow path defined by the groove to the exhaust chamber outlet 201. During flow, the oil does not experience sudden increases in flow resistance due to bends in the groove, nor does it stagnate or accumulate at corners, thus ensuring that the oil returns along the shortest and smoothest path.

[0036] In one embodiment, the first preset angle α between two adjacent main oil grooves 3 is 10°. All main oil grooves 3 are evenly distributed on the side wall 202 of the end cover 2 along the circumference of the exhaust outlet 201 with a 10° included angle as the standard. The small included angle of 10° increases the distribution density of the main oil grooves 3, so that multiple straight main oil grooves 3 can fully cover the oil accumulation area of ​​the side wall 202 of the end cover 2. The dense straight main oil grooves 3 can quickly collect the stagnant oil in the entire area of ​​the side wall 202 of the end cover 2, ensuring the oil return efficiency, which is suitable for high speed and large displacement compressors.

[0037] In another embodiment, the first preset angle α between two adjacent main oil grooves 3 is 15°. All main oil grooves 3 are evenly distributed on the side wall 202 of the end cover 2 along the circumference of the exhaust outlet 201 with a 15° included angle as the standard. The larger included angle of 30° reduces the distribution density of the main oil grooves 3. Fewer grooves can enable the side wall 202 of the end cover 2 to maintain higher structural strength and reduce the risk of structural damage caused by vibration. It is suitable for compressors with low speed and small exhaust volume.

[0038] The main oil trough 3 is set as a straight strip, and the adjacent main oil troughs 3 are arranged at a first preset angle α. This simplifies the flow path of the oil, reduces flow resistance, and avoids oil accumulation at corners. It also allows the oil accumulation range and amount of different compressors to be precisely matched with different first preset angles α, thus ensuring efficient oil return under different operating conditions. At the same time, it takes into account the processing cost and structural strength of the end cover 2, further improving the versatility and reliability of the oil return structure.

[0039] Optionally, in one implementation of this embodiment, such as Figure 2 and Figure 3 As shown, the second end of the main oil tank 3 is connected to at least one branch oil tank 301; The branch oil tank 301 and the corresponding main oil tank 3 form a second preset angle β, where β satisfies: 15°≤β≤25°.

[0040] In this embodiment, a corresponding and connected branch oil trough 301 is provided at the end of each main oil trough 3 away from the exhaust port outlet 201. Both the main oil trough 3 and the branch oil trough 301 are straight strip-shaped troughs. The fixed included angle formed between the branch oil trough 301 and the corresponding main oil trough 3 is a second preset angle β. This can expand the range of oil collection and form a tree-shaped oil collection network with a larger coverage area. The straight strip-shaped branch oil trough 301 can have the same width as the main oil trough 3. For example, the width of the branch oil trough 301 and the main oil trough 3 are both 1 mm. This allows the branch oil trough 301 and the main oil trough 3 to have the characteristics of low flow resistance. When the oil is absorbed from the dead corner of the side wall 202 of the end cap 2 by the branch oil trough 301, it will flow along the straight strip-shaped trough and quickly flow into the main oil trough 3. During this process, there will be no oil stagnation in the oil return structure. The range of the second preset angle β between the branch oil trough 301 and the main oil trough 3 defines the extension direction of the branch oil trough 301. Different included angles between 15° and 25° allow the branch oil trough 301 to extend divergently towards different oil accumulation areas on the side wall 202 of the end cap 2, collecting the stagnant oil in various corners of the side wall 202 of the end cap 2. The main oil trough 3 serves as the main flow channel for the oil, and the branch oil trough 301 serves as the terminal oil collection channel. The combination of the two forms a multi-stage oil return channel from extensive collection to directional transportation, increasing the oil collection area of ​​the oil return structure and improving the oil transportation efficiency of the oil return structure.

[0041] In one embodiment, the second preset angle β between the branch oil groove 301 and the main oil groove 3 is 20°. Two branch oil grooves 301 are symmetrically arranged at the end of each main oil groove 3. The two branch oil grooves 301 extend to both sides of the main oil groove 3 at 20°. This symmetrical layout can make the oil collection range more balanced. It is suitable for the side wall 202 of the end cap 2 with a conventional shape and has strong versatility.

[0042] A straight branch oil tank 301 is connected to the outer end of the main oil tank 3, and a second preset angle β is set to limit the extension direction of the branch oil tank 301. This can form a multi-stage oil return channel, increase the oil collection area of ​​the oil return structure, improve the oil delivery efficiency of the oil return structure, and ensure that the oil in all positions in the exhaust chamber 101 can be smoothly guided to the exhaust chamber outlet 201, so that the performance of the oil return structure is further optimized.

[0043] Optionally, in one implementation of this embodiment, such as Figure 2 and Figure 3 As shown, the width of the main oil tank 3 ranges from 0.8 mm to 1.0 mm, and the width of the branch oil tank 301 ranges from 0.5 mm to 1.0 mm.

[0044] In this embodiment, the widths of both the main oil tank 3 and the branch oil tank 301 are within the range of 1 mm to 2 mm. The width significantly affects the capillary action, oil flow rate, and structural strength of the tank. Therefore, the widths of the main oil tank 3 and the branch oil tank 301 should be limited based on the viscosity, surface tension, oil flow rate of the refrigeration oil in the compressor, and the structural dimensions of the side wall 202 of the end cover 2. The branch oil tank 301, as the terminal collection channel of the oil return structure, is mainly responsible for adsorbing thin oil films and scattered oil droplets. The main oil tank 3, as the main oil transport channel of the oil return structure, needs to simultaneously receive oil collected from multiple branch oil tanks 301. By limiting the width of both the main oil tank 3 and the branch oil tank 301 to the range of 1 mm to 2 mm, it is possible to avoid oil flow blockage or sudden changes in flow rate caused by excessive difference in width between the two. This ensures that the oil in the branch oil tank 301 can smoothly flow into the main oil tank 3 and be transported to the exhaust chamber outlet 201, thereby achieving a balance between the main oil tank 3 and the branch oil tank 301 in terms of capillary adsorption capacity, oil flow capacity, anti-clogging performance and structural strength.

[0045] In one embodiment, the width of both the main oil trough 3 and the branch oil trough 301 is set to 1 mm. The capillary adsorption capacity of the trough is strongest at this width, and the small trough opening can also block large particles of impurities from entering the flow channel. This is suitable for compressors operating at low temperatures or compressors with high viscosity and weak fluidity of refrigeration oil.

[0046] In another embodiment, the width of both the main oil tank 3 and the branch oil tank 301 is set to 1 mm. This provides a larger flow space inside the tank, increasing the oil throughput and enabling it to handle larger flow rates. The 1 mm wide tank opening is also larger, preventing blockage even if small impurities enter the flow channel. The wider tank also accelerates oil flow, improving the overall oil return efficiency of the compressor. This design is suitable for compressors operating at high temperatures or those with high oil flow rates and large oil droplet sizes.

[0047] By limiting the width of the main oil tank 3 and the branch oil tank 301, the tank body has a stable capillary adsorption capacity and oil flow capacity. At the same time, it avoids negative situations such as blockage due to the tank body being too narrow, and reduction of the structural strength of the end cap 2 and failure of capillary action due to the tank body being too wide. This ensures that the cooperation between the main oil tank 3 and the branch oil tank 301 is balanced, and that the oil return structure can operate stably and efficiently.

[0048] Optionally, in one implementation of this embodiment, such as Figure 2 and Figure 3 As shown, the oil return structure further includes: an oil collection groove 4; the oil collection groove 4 is disposed through the exhaust chamber outlet 201, and the oil collection groove 4 is connected to the exhaust chamber outlet 201. In the plurality of main oil tanks 3, one of the main oil tanks 3 is connected to the exhaust chamber outlet 201; A portion of the remaining main oil tanks 3 are connected to the converging oil tank 4 and are located on one side of the exhaust outlet 201, while another portion of the remaining main oil tanks 3 are connected to the converging oil tank 4 and are located on the other side of the exhaust outlet 201.

[0049] In this embodiment, the oil return structure is also provided with a collecting oil groove 4, which passes through the exhaust chamber outlet 201 and is connected to the exhaust chamber outlet 201. All main oil grooves 3 are divided into two parts. One part of the main oil groove 3 is directly connected to the exhaust chamber outlet 201, and the other part of the main oil groove 3 is directly connected to the collecting oil groove 4 and thus indirectly connected to the exhaust chamber outlet 201, so as to disperse the pressure of the oil before it enters the exhaust chamber outlet 201.

[0050] The oil converging tank 4 is an oil flow channel connecting part of the main oil tank 3 and the exhaust chamber outlet 201. The oil converging tank 4 passes through and is connected to the exhaust chamber outlet 201, so that a part of the oil in the main oil tank 3 can first flow into the oil converging tank 4, and after accumulating in the oil converging tank 4, it can flow smoothly to the exhaust chamber outlet 201 to complete the diversion, thereby realizing the dispersion of the oil converging pressure. The oil collection tank 4 can expand the oil collection area in the central area near the air inlet of the exhaust chamber 101, and disperse the pressure of the simultaneous convergence of multiple main oil tanks 3. By secondary collection of a portion of the oil output from the main oil tanks 3, the impact force generated by the instantaneous convergence of large flow of oil is reduced, and oil splashing and rebound are avoided. In this process, the oil in the multiple main oil tanks 3 is also divided into two paths for flow. One path of oil flows directly into the exhaust chamber outlet 201, and the other path of oil first flows into the oil collection tank 4 for buffering, and then flows from the oil collection tank 4 into the exhaust chamber outlet 201, forming a multi-convergence mode that combines direct delivery and intermediate buffering. This ensures that all the oil in the exhaust chamber 101 can enter the exhaust chamber outlet 201 smoothly and orderly without turbulence and impact splashing, and greatly improves the oil guiding capacity of the return oil structure at the exhaust chamber outlet 201.

[0051] In one embodiment, the oil collecting trough 4 is a straight-line channel that extends horizontally through the exhaust outlet 201. Approximately half of the main oil channels 3 are directly connected to the exhaust outlet 201, while the remaining main oil channels 3 are symmetrically distributed on the left and right sides of the oil collecting trough 4 and are directly connected to it. The straight-line oil collecting trough 4 has a simple structure, is easy to manufacture, and has no internal bends. The flow resistance of the oil within the straight-line oil collecting trough 4 is extremely low, allowing the oil flowing from the main oil channels 3 on both sides to flow quickly along the straight channel to the exhaust outlet 201. The symmetrically distributed main oil channels 3 ensure that the oil from both sides of the exhaust outlet 201 is evenly collected into the oil collecting trough 4 for buffering, resulting in balanced flow pressure without uneven load. The straight-line oil collecting trough 4 combines structural simplicity with flow stability, making it suitable for compressors with low or moderate oil flow rates.

[0052] In another embodiment, the oil collecting groove 4 is a cross-shaped through groove, the center of which coincides with the center of the exhaust outlet 201. The cross-shaped oil collecting groove 4 extends into four equal-width grooves in four directions. Only a small portion of the main oil groove 3 is directly connected to the exhaust outlet 201, while the majority of the main oil groove 3 is connected to the four grooves extending from the cross-shaped oil collecting groove 4. This increases the oil collecting area and enhances the oil flow guidance capacity. It can be applied to the working conditions of ultra-large flow oil collection and is suitable for large compressors with large total oil volume and strong oil flow impact.

[0053] By making the oil collection tank 4 pass through the exhaust chamber outlet 201, the flow path of the oil in the multiple main oil tanks 3 is divided into two types: direct flow into the exhaust chamber outlet 201 and indirect flow into the exhaust chamber outlet 201. The secondary transfer and collection of the oil in the oil collection tank 4 expands the confluence area at the output end of the oil return structure, disperses the impact force generated by the large amount of oil confluence, and enhances the stability of the oil flow from the main oil tank 3 to the exhaust chamber outlet 201, thus ensuring that the entire oil return process is more efficient.

[0054] More specifically, such as Figure 3 As shown, the oil collection tank 4 is constructed as a straight strip-shaped tank; among the multiple main oil tanks 3, one main oil tank 3 is connected to the exhaust chamber outlet 201; a portion of the remaining main oil tanks 3 is connected to the oil collection tank 4 and is located on one side of the exhaust chamber outlet 201, and another portion of the remaining main oil tanks 3 is connected to the oil collection tank 4 and is located on the other side of the exhaust chamber outlet 201.

[0055] In this embodiment, when the oil collection trough 4 is a straight, linear channel, only one main oil trough 3 is directly connected to the exhaust outlet 201. The remaining main oil troughs 3 are symmetrically distributed on the left and right sides of the oil collection trough 4 with the exhaust outlet 201 as the center and are directly connected to the oil collection trough 4. A single main oil trough 3 is directly connected to the exhaust outlet 201 and is responsible for transporting the oil in the central area. The main oil troughs 3 on the left and right sides of the oil collection trough 4 are responsible for the oil in the left and right sides respectively. In this way, the oil transport in each direction on the side wall 202 of the end cap 2 is clearly divided and the flow direction is clear. The straight oil collection trough 4 can also accurately guide the oil on both sides to converge towards the exhaust outlet 201 in the center. The symmetrical layout keeps the flow rate and velocity of the oil on both sides in a balanced state, and will not cause flow deviation or congestion due to excessive flow on one side, ensuring that the oil can complete the convergence more smoothly and orderly.

[0056] In one embodiment, the straight-lined oil converging groove 4 is arranged horizontally, and the number of main oil grooves 3 connected on the left and right sides is exactly the same. The main oil groove 3 directly connected to the exhaust port outlet 201 is located on the center line of the oil converging groove 4. In this way, the oil flow rate and velocity on the left and right sides of the oil converging groove 4 are completely balanced, the confluence impact can cancel each other out, and the oil flow stability is extremely high. This is suitable for the side wall 202 of the end cap 2 with a conventional symmetrical shape.

[0057] In another embodiment, the straight-line oil collection trough 4 can be arranged along an inclined direction according to the asymmetrical distribution of oil accumulation on certain sidewalls 202 of the end cap 2. One side of the oil collection trough 4 is connected to a larger number of main oil troughs 3, which is the side with a larger amount of oil accumulation on the sidewall 202 of the end cap 2. The other side of the oil collection trough 4 has fewer main oil troughs 3, which is the side with a smaller amount of oil accumulation on the sidewall 202 of the end cap 2. The main oil trough 3 directly connected to the exhaust outlet 201 is also biased towards the side with a larger amount of oil accumulation on the sidewall 202 of the end cap 2. This asymmetrical layout of the oil collection trough 4 is suitable for working conditions where the oil accumulation on the sidewall 202 of the end cap 2 is unevenly distributed. By allocating oil flow channels as needed, the oil collection and transportation capacity for specific areas can be improved.

[0058] Optionally, in one implementation of this embodiment, such as Figure 3 As shown, the connection points between the multiple main oil tanks 3, the converging oil tank 4, and the exhaust outlet 201 are all constructed as arc-shaped transition structures.

[0059] In this embodiment, the outer contour edge of the exhaust chamber outlet 201 is arc-shaped. The locations where the main oil groove 3, the converging oil groove 4, and the exhaust chamber outlet 201 connect are all machined into corresponding arc-shaped grooves. The curvature of the arc-shaped grooves matches the arc-shaped edge of the exhaust chamber outlet 201, creating an arc-shaped transition structure at all connecting sections and turning points through which the oil flows. This allows the oil to smoothly change its flow direction when flowing from the main oil groove 3 and the converging oil groove 4 into the exhaust chamber outlet 201, significantly reducing flow resistance and making the oil flow velocity more stable. The continuous arc-shaped wall surface allows the capillary channel to remain continuous throughout, avoiding interruptions in capillary action. This allows the oil to flow continuously due to capillary effects without stagnating at turning points. Simultaneously, the arc-shaped structure does not generate eddies, eliminating the risk of eddies carrying oil back and ensuring that the oil always flows in one direction.

[0060] By using mutually compatible arc-shaped structures for the edge of the exhaust outlet 201 and the connecting positions of the main oil groove 3 and the converging oil groove 4, the obstruction of the sharp corner structure to the capillary action and the adverse effect on the oil flow can be eliminated. This ensures that the capillary channel remains continuous and intact, and the oil flow is smooth and gentle. As a result, the entire flow process of the oil from the side wall 202 of the end cover 2 to the exhaust outlet 201 is more stable, further improving the oil return efficiency of the compressor.

[0061] Optionally, in one implementation of this embodiment, such as Figure 1 , Figure 4 and Figure 6 As shown, an oil return channel 203 is formed inside the end cover 2, and the exhaust chamber outlet 201 is connected to the bottom oil sump inside the compressor through the oil return channel 203; The compressor further includes a gas-liquid separator 5, which is connected to the exhaust outlet 201. The liquid phase outlet 501 of the gas-liquid separator 5 is connected to the bottom oil sump inside the compressor through the oil return channel 203, and the gas phase outlet 502 is connected to the outside of the end cover 2.

[0062] The compressor in this embodiment integrates the oil return structure of Embodiment 1. The stationary plate 1 is sealed to the end cover 2 by the sealing strip 103, thus enclosing the exhaust chamber 101. At the same time, a gas-liquid separator 5 is installed on the oil return channel 203 inside the end cover 2, and the gas-liquid separator 5 is installed at the position of the oil return channel 203 corresponding to the exhaust chamber outlet 201. When the compressor is running, the refrigerant mixed with lubricating oil after being compressed by the pump body will enter the exhaust chamber 101 through the exhaust chamber inlet 102 of the stationary plate 1. Under the action of the radial capillary guide network composed of the main oil groove 3, branch oil groove 301, and converging oil groove 4 on the side wall 202 of the end cover 2, the lubricating oil accumulated in various places in the exhaust chamber 101 is actively collected and directed. The oil flows into the exhaust chamber outlet 201 after passing through the main oil groove 3, branch oil groove 301, and converging oil groove 4 in sequence.

[0063] The oil flowing out of the exhaust outlet 201 is not only lubricating oil, but also contains incompletely separated gaseous refrigerant. After the oil-gas mixture enters the oil return channel 203 inside the end cover 2, it flows directly through the gas-liquid separator 5. The gas-liquid separator 5 uses the difference in density between the gas and liquid phases to perform secondary separation of the oil-gas mixture. The denser liquid lubricating oil will flow out from the liquid phase outlet 501 of the gas-liquid separator 5 and continue to flow downward along the oil return channel 203, eventually flowing smoothly back to the oil sump at the bottom of the compressor to complete the lubricating oil circulation. The less dense gaseous refrigerant will be discharged from the gas phase outlet 502 of the gas-liquid separator 5 until it reaches the outside of the end cover 2, and re-enter the refrigerant circulation pipeline of the air conditioning system.

[0064] The compressor that integrates the oil return structure in Embodiment 1 is equipped with a gas-liquid separator 5 in its oil return channel 203. The oil return structure can be used to achieve efficient collection and guidance of oil in the exhaust chamber 101, and the gas-liquid separator 5 can be used to separate the liquid lubricating oil and let it flow back to the bottom oil sump, ensuring stable circulation and lubrication effect of the compressor lubricating oil, thereby improving the overall operating stability, energy efficiency and service life of the compressor.

[0065] Since the compressor in this embodiment is equipped with the oil return structure in Embodiment 1, the compressor in this embodiment has all the beneficial effects of the oil return structure in Embodiment 1, which will not be described in detail here.

[0066] Optionally, in one implementation of this embodiment, such as Figure 1 , Figure 4 and Figure 6As shown, a limit valve plate 6 is provided inside the exhaust chamber 101 and on the inner wall of the stationary plate 1. The limit valve plate 6 covers the exhaust chamber inlet 102 and is configured to open the exhaust chamber inlet 102 under a preset pressure.

[0067] In this embodiment, a limiting valve plate 6 is installed on the inner wall of the stationary plate 1 inside the exhaust chamber 101. The limiting valve plate 6 can completely cover the exhaust chamber inlet 102 on the stationary plate 1. The limiting valve plate 6 will only open and open the exhaust chamber inlet 102 when the pressure difference between the inside and outside of the exhaust chamber 101 reaches a preset value. After the compressor pump body completes the refrigerant compression, the pressure difference between the inside and outside of the exhaust chamber 101 gradually increases. When the pressure difference reaches the opening threshold of the limiting valve plate 6, the high-pressure refrigerant mixed lubricating oil will push open the limiting valve plate 6 and flow into the exhaust chamber 101 from the exhaust chamber inlet 102. When the pump body completes the exhaust and the pressure difference decreases, the limiting valve plate 6 will automatically fall back and re-close the exhaust chamber inlet 102.

[0068] The limit valve 6 can unidirectionally control the opening and closing of the exhaust chamber inlet 102, preventing the lubricating oil and high-pressure refrigerant mixed together inside the exhaust chamber 101 from flowing back into the compressor pump body and impacting the pump body volute teeth, thus reducing the risk of liquid hammer damage to the pump body volute teeth. In addition, the limit valve 6 can also stabilize the working pressure inside the exhaust chamber 101, keeping the exhaust chamber 101 within a reasonable pressure range, ensuring that the oil return structure on the side wall 202 of the end cover 2 is in a good and stable working condition, and avoiding the influence of capillary action and the oil flow state in the tank on drastic pressure fluctuations. At the same time, the valve's shielding of the exhaust chamber inlet 102 can also prevent a large number of oil droplets from directly impacting the surrounding area of ​​the exhaust chamber inlet 102 at high speed, reducing local oil accumulation.

[0069] Example 2 This embodiment provides an air conditioning system, which includes the compressor described in Embodiment 1. The air conditioning system proposed in this embodiment belongs to the high-efficiency energy-saving industry, and the use of the compressor in Embodiment 1 in the air conditioning system achieves energy-saving effects.

[0070] Since the air conditioning system in this embodiment includes the compressor in Embodiment 1, the air conditioning system in this embodiment has all the beneficial effects of the compressor in Embodiment 1, and will not be described again.

[0071] In summary, the ingenious design of this compressor lies in: First, in this compressor, by designing an oil return structure, multiple main oil grooves with capillary action are arranged radially and interconnected on the side wall of the end cover located inside the exhaust chamber. This can absorb and guide the stagnant oil accumulated in the exhaust chamber, allowing the oil to flow out from the exhaust chamber outlet and return to the bottom oil sump. This reduces the risk of oil stagnation and accumulation in the corners of the cavity under microgravity, which could lead to compressor oil shortage and lubrication failure. At the same time, this oil return structure does not require additional new components, thus reducing the compressor's production cost and failure rate.

[0072] Secondly, by setting the main oil tank to a gradually decreasing depth from near the exhaust chamber outlet to far away from the exhaust chamber outlet, the shallow tank enhances the capillary adsorption capacity at the far end, and the deep tank improves the oil flow and driving capacity at the near end. This effectively solves the problems of speed attenuation, oil stagnation in the tank, and congestion during long-distance oil transportation. It further optimizes the oil transportation effect of the radial main oil tank, allowing the lubricating oil in the exhaust chamber to flow smoothly throughout the process, and continuously ensuring the oil supply and lubrication effect of the compressor.

[0073] Third, by limiting the depth of the main oil tank to between 1 mm and 2 mm, the capillary effect of the tank body, the structural strength of the end cover sidewall, and the production cost of the parts are taken into account. This allows the oil return structure to have multiple advantages, including stable collection of oil and guidance of its return flow, reducing the probability of the tank body being blocked by impurities, and improving the structural strength of the end cover, thereby comprehensively improving the reliability and service life of the compressor.

[0074] Fourth, the main oil trough is set as a straight strip and arranged between adjacent main oil troughs at a first preset angle α. This simplifies the oil flow path, reduces flow resistance, and avoids oil accumulation at corners. It also allows for precise matching of the oil accumulation range and amount of different compressors with different first preset angles α, thus ensuring efficient oil return under different operating conditions. At the same time, it takes into account the processing cost and structural strength of the end cap, further improving the versatility and reliability of the oil return structure.

[0075] Fifth, a straight branch oil tank is connected to the outer end of the main oil tank, and a second preset angle β is set to limit the extension direction of the branch oil tank. This can form a multi-stage oil return channel, increase the oil collection area of ​​the oil return structure, improve the oil delivery efficiency of the oil return structure, and ensure that the oil in all positions in the exhaust chamber can be smoothly guided to the exhaust chamber outlet, thereby further optimizing the performance of the oil return structure.

[0076] Sixth, by making the oil collection tank pass through the exhaust chamber outlet, the flow path of the oil in multiple main oil tanks is divided into two types: direct flow into the exhaust chamber outlet and indirect flow into the exhaust chamber outlet. The secondary transfer and collection of oil in the oil collection tank expands the confluence area at the output end of the oil return structure, disperses the impact force generated by the large amount of oil confluence, and enhances the stability of the oil flow from the main oil tank to the exhaust chamber outlet, thus ensuring that the entire oil return process is more efficient.

[0077] Seventh, by using mutually compatible arc-shaped structures for the edge of the exhaust chamber outlet and the connecting positions of the main oil groove and the converging oil groove, the obstruction of the sharp corner structure to capillary action and the adverse effects on oil flow can be eliminated, so that the capillary channel remains continuous and intact and the oil flow is smooth and gentle. This makes the entire flow process of oil from the end cover side wall to the exhaust chamber outlet more stable, further improving the oil return efficiency of the compressor.

[0078] It can be further understood that in this disclosure, "many" refers to two or more, and other quantifiers are similar. "And / or" describes the relationship between related objects, indicating that three relationships can exist; for example, A and / or B can represent: A alone, A and B simultaneously, and B alone. The character " / " generally indicates that the preceding and following related objects are in an "or" relationship. The singular forms "a," "the," and "the" are also intended to include the plural forms unless the context clearly indicates otherwise.

[0079] It is further understood that the terms "first," "second," etc., are used to describe various types of information, but this information should not be limited to these terms. These terms are only used to distinguish information of the same type from one another, and do not indicate a specific order or degree of importance. In fact, the expressions "first," "second," etc., are completely interchangeable. For example, without departing from the scope of this disclosure, first information can also be referred to as second information, and similarly, second information can also be referred to as first information.

[0080] It is further understood that although operations are described in a specific order in the accompanying drawings in the embodiments of this disclosure, this should not be construed as requiring these operations to be performed in the specific order or serial order shown, or requiring all of the shown operations to be performed to obtain the desired result. In certain environments, multitasking and parallel processing may be advantageous.

[0081] Other embodiments of this disclosure will readily occur to those skilled in the art upon consideration of the specification and practice of the invention disclosed herein. This application is intended to cover any variations, uses, or adaptations of this disclosure that follow the general principles of this disclosure and include common knowledge or customary techniques in the art not disclosed herein. The specification and examples are to be considered exemplary only, and the true scope and spirit of this disclosure are indicated by the following claims.

[0082] It should be understood that this disclosure is not limited to the precise structures described above and shown in the accompanying drawings, and various modifications and changes can be made without departing from its scope. The scope of this disclosure is limited only by the appended claims.

Claims

1. A compressor comprising a stationary plate (1) and an end cover (2) fastened to the stationary plate (1), wherein an exhaust chamber (101) is formed between the stationary plate (1) and the end cover (2), an exhaust chamber inlet (102) is provided on the stationary plate (1), and an exhaust chamber outlet (201) is provided on the end cover (2), characterized in that: An oil return structure is provided on the side wall (202) of the end cap (2) on one side of the exhaust chamber (101), the oil return structure including: Multiple main oil tanks (3), the first end of each of the multiple main oil tanks (3) is connected to the exhaust chamber outlet (201), and the second end of each of the multiple main oil tanks (3) extends radially along the side wall (202) with the exhaust chamber outlet (201) as the center.

2. The compressor according to claim 1, characterized in that, The depth of the main oil tank (3) gradually decreases from the first end to the second end.

3. The compressor according to claim 2, wherein the depth of the main oil trough (3) is in the range of 1 mm to 2 mm.

4. The compressor according to claim 1, characterized in that, The main oil tank (3) is constructed as a straight strip-shaped tank; A first preset angle α is formed between two adjacent main oil tanks (3), wherein α satisfies: 5°≤α≤15°.

5. The compressor according to claim 1, characterized in that, The second end of the main oil tank (3) is connected to at least one branch oil tank (301); The branch oil tank (301) and the corresponding main oil tank (3) form a second preset angle β, where β satisfies: 15°≤β≤25°.

6. The compressor according to claim 5, characterized in that, The width of the main oil tank (3) ranges from 0.8 mm to 1.0 mm, and the width of the branch oil tank (301) ranges from 0.5 mm to 1.0 mm.

7. The compressor according to any one of claims 1-6, characterized in that, The oil return structure also includes: an oil collection tank (4); The oil collection tank (4) is disposed through the exhaust chamber outlet (201), and the oil collection tank (4) is connected to the exhaust chamber outlet (201). Among the plurality of main oil tanks (3), one of the main oil tanks (3) is connected to the exhaust chamber outlet (201). A portion of the remaining main oil tanks (3) are connected to the converging oil tank (4) and located on one side of the exhaust outlet (201), while another portion of the remaining main oil tanks (3) are connected to the converging oil tank (4) and located on the other side of the exhaust outlet (201).

8. The compressor according to claim 7, characterized in that, The connection points between the multiple main oil tanks (3), the converging oil tank (4), and the exhaust outlet (201) are all constructed as arc-shaped transition structures.

9. The compressor according to claim 1, characterized in that, An oil return channel (203) is formed inside the end cover (2). The compressor also includes a gas-liquid separator (5), which is connected to the exhaust port outlet (201). The liquid phase outlet (501) of the gas-liquid separator (5) is connected to the bottom oil sump inside the compressor through the oil return channel (203), and the gas phase outlet (502) is connected to the outside of the end cover (2).

10. An air conditioning system, characterized in that, include: The compressor as described in any one of claims 1-9.

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