Oil separator and compressor

Abstract

The invention relates to the technical field of compressors, in particular to an oil separator and a compressor. The oil separator comprises a spiral separation pipe, a spiral oil separation channel is arranged in the spiral separation pipe, and an oil discharge structure communicated with the oil separation channel is arranged on the outer side of the outer wall of the spiral separation pipe. When the oil separator works, compressed gas carrying tiny lubricating oil liquid drops enters the oil separation channel and then moves in the spiral oil separation channel, the lubricating oil liquid drops can be attached to the inner wall of the spiral separation pipe under the action of centrifugal force, and when the lubricating oil liquid drops are accumulated to a certain degree, the tiny lubricating oil liquid drops can form large lubricating oil liquid drops; according to the oil-gas separation device, oil-gas separation is carried out through the centrifugal force of the spiral separation pipe, the oil-gas separation requirement under the conditions of constant gravity and small gravity can be met, and the oil-gas separation effect is good. The defect that an existing oil separator is poor in oil separation effect under the conditions of constant gravity and small gravity is overcome.

Description

Technical Field

[0001] The present invention relates to the technical field of compressors, and particularly to an oil separator and a compressor. Background Art

[0002] In existing rotary compressors, the oil supply is driven by the rotation of a crankshaft to drive an oil pumping vane or a spiral pump body, mainly relying on the high-speed rotation of the crankshaft to drive the flow of lubricating oil. However, the oil pump pressure difference in this way is small, and the self-priming ability of the oil pump is poor. Especially at low speeds or low oil levels, it is easy to cause insufficient oil supply. A linear compressor drives the oil pump through the vibration of the body, but also faces problems such as difficult startup and poor self-priming ability.

[0003] For compressors in variable installation postures and micro-gravity environments (such as automobiles, airplanes, high-speed rails, aircraft, etc.), traditional oil pump methods (relying on gravity, centrifugal force, capillary force, etc.) cannot effectively ensure the lubrication of moving pairs and efficient oil sealing, thereby affecting the service life and operating efficiency of the compressor. In these scenarios, changes in the installation posture of the compressor or changes in gravitational acceleration will cause unstable lubricating oil supply and affect its normal operation.

[0004] In addition, a compressor needs to be provided with an oil separator to prevent lubricating oil from entering the system. However, in normal gravity and micro-gravity scenarios, existing oil separators cannot fully separate the lubricating oil, so that some lubricating oil will enter the system along with the compressed gas. The lubricating oil entering the refrigeration system is difficult to quickly return to the compressor interior through the refrigerant carrying, seriously affecting the lubrication and operating efficiency of the compressor moving pairs. Summary of the Invention

[0005] The present invention provides an oil separator and a compressor to solve the defect that the existing oil separator has poor oil separation effect in a micro-gravity scenario.

[0006] On the one hand, the present invention provides an oil separator, including: a spiral separation tube, a spiral oil separation channel is formed inside the spiral separation tube, an air inlet and an air outlet are respectively provided at both ends of the spiral separation tube, both the air inlet and the air outlet are communicated with the oil separation channel, an oil drainage structure is provided outside the outer wall of the spiral separation tube, the oil drainage structure is communicated with the oil separation channel, and the oil drainage structure is used to drain the lubricating oil in the oil separation channel.

[0007] According to the oil separator provided by the present invention, the spiral separation tube includes a plurality of spiral tube units connected in sequence, all the spiral tube units have the same structure and form a cylindrical spiral separation tube; or, the diameters of the plurality of spiral tube units gradually decrease along the axial direction of the spiral separation tube to form a conical spiral separation tube.

[0008] According to the oil separator provided by the present invention, an oil drainage structure is provided at the outer bottom of the outer wall of each spiral tube unit, a lipophilic structure is provided on the outer side of the inner wall of the oil separation channel, and an oilophobic structure is provided on the inner side of the inner wall of the oil separation channel.

[0009] According to the oil separator provided by the present invention, a porous oil filter screen is provided at the air inlet and / or the air outlet.

[0010] On the other hand, the present invention provides a compressor, comprising: a housing, a partition plate, and the oil separator according to any one of the above; a sealed cavity is formed in the housing; the partition plate is located in the sealed cavity and divides the sealed cavity into a high-pressure cavity and a low-pressure cavity, and an exhaust muffler cavity is provided in the high-pressure cavity; the oil separator is provided in the exhaust muffler cavity.

[0011] According to the compressor provided by the present invention, it further comprises: a differential pressure ejector pump oil structure, the differential pressure ejector pump oil structure is located in the sealed cavity, the differential pressure ejector pump oil structure comprises a body, a pump oil channel is formed in the body, the pump oil channel comprises a high-pressure ejecting oil inlet, a low-pressure ejected oil inlet, a nozzle, a contraction channel, a mixing channel and an expansion channel, the high-pressure ejecting oil inlet and the low-pressure ejected oil inlet are both communicated with the nozzle, and the nozzle, the contraction channel, the mixing channel and the expansion channel are communicated in sequence; the high-pressure ejecting oil inlet is communicated with the high-pressure cavity, the low-pressure ejected oil inlet is communicated with the low-pressure cavity, and the expansion channel is communicated with the moving pair of the compressor.

[0012] According to the compressor provided by the present invention, the compressor is a linear compressor; it further comprises a linear motor, a piston and a cylinder, the cylinder is located in the sealed cavity, the linear motor is in transmission connection with the piston, the piston and the cylinder are in axial sliding fit, and the expansion channel is communicated with the fitting gap between the piston and the cylinder.

[0013] According to the compressor provided by the present invention, the compressor is a rotary compressor; it further comprises a first rotary motor, a first crankshaft, a first crankshaft support and a second crankshaft support, the first crankshaft support and the second crankshaft support are coaxially and spaced in the sealed cavity, one end of the first crankshaft is in rotational fit with the housing, the other end of the first crankshaft is in rotational fit with the first crankshaft support and the second crankshaft support, the first rotary motor is in transmission connection with the first crankshaft, and the expansion channel is communicated with the fitting gap between the first crankshaft and the first crankshaft support and the second crankshaft support.

[0014] According to the compressor provided by the present invention, a first shaft section and a second shaft section are arranged at intervals on the first crankshaft. A first oil passage is arranged along the length direction on the outer wall of the first shaft section, and a second oil passage is arranged along the length direction on the outer wall of the second shaft section. Both the first oil passage and the second oil passage communicate with the expansion passage, and the first oil passage and the second oil passage are arranged on the first crankshaft back to back.

[0015] According to the compressor provided by the present invention, the compressor is a scroll compressor; it further includes a second rotating motor, a second crankshaft, a third crankshaft support, a scroll moving disk and a scroll static disk. The third crankshaft support, the scroll moving disk and the scroll static disk are all arranged in the sealed cavity. One end of the second crankshaft is rotationally matched with the housing, and the other end of the second crankshaft is rotationally matched with the third crankshaft support and connected to the scroll moving disk. The expansion passage communicates with the fitting clearance between the second crankshaft and the third crankshaft support and the fitting clearance between the scroll moving disk and the scroll static disk.

[0016] The oil separator provided by the present invention is set as a spiral separation tube type. During operation, the compressed gas carrying tiny lubricating oil droplets enters the oil separation channel through the air inlet and then moves in the spiral oil separation channel. Under the action of centrifugal force, the lubricating oil droplets can adhere to the inner wall of the spiral separation tube. When accumulated to a certain extent, the tiny lubricating oil droplets can form larger lubricating oil droplets and are discharged through the oil discharge structure arranged outside the outer wall of the spiral separation tube. It can prevent the tiny lubricating oil droplets from following the compressed gas into the system, and has good oil separation effect. Moreover, the oil separator provided by the present invention separates oil and gas through the centrifugal force of the spiral separation tube, can meet the oil and gas separation requirements in the scenarios of normal gravity and micro gravity, and solves the defect that the existing oil separator has poor oil separation effect in the scenarios of normal gravity and micro gravity.

[0017] The compressor provided by the present invention has a good oil separation effect due to the adoption of the above oil separator, can prevent tiny lubricating oil droplets from following the compressed gas into the system, and can meet the oil and gas separation requirements in the scenarios of normal gravity and micro gravity.

[0018] The additional aspects and advantages of the present invention will be partially given in the following description, partially become obvious from the following description, or be understood through the practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] In order to more clearly illustrate the technical solutions in the present invention or the prior art, the following will briefly introduce the drawings required for the description of the embodiments or the prior art. Obviously, the drawings in the following description are some embodiments of the present invention. For those of ordinary skill in the art, other drawings can be obtained based on these drawings without creative efforts.

[0020] Figure 1 It is one of the schematic diagrams of the oil separator provided by the embodiments of the present invention.

[0021] Figure 2 It is another schematic diagram of the oil separator provided by the embodiments of the present invention.

[0022] Figure 3 It is the schematic diagram of the differential pressure ejector pump oil structure in the compressor provided by the embodiments of the present invention.

[0023] Figure 4 It is the schematic diagram of the compressor provided by one of the embodiments of the present invention.

[0024] Figure 5 It is the schematic diagram of the compressor provided by another embodiment of the present invention.

[0025] Figure 6 It is Figure 5 The partial enlarged schematic diagram of A in

[0026] Figure 7 It is one of the schematic diagrams of the first crankshaft in the compressor provided by another embodiment of the present invention.

[0027] Figure 8 It is another schematic diagram of the first crankshaft in the compressor provided by another embodiment of the present invention.

[0028] Figure 9 It is the schematic diagram of the compressor provided by the third embodiment of the present invention.

[0029] Figure 10 It is Figure 9 The partial enlarged schematic diagram of B in

[0030] Reference numerals: 10. Housing; 110. Sealed cavity; 111. Low-pressure cavity; 112. High-pressure cavity; 113. Exhaust silencing cavity; 120. Oil separator; 121. Oil separation channel; 122. Air inlet; 123. Exhaust port; 124. Oil drainage structure; 125. Oil-loving structure; 126. Oil-repellent structure; 20. Partition plate; 30. Differential pressure jet pump oil structure; 310. Body; 320. Oil pumping channel; 321. High-pressure jet oil inlet; 322. Low-pressure oil to be jet inlet; 323. Nozzle; 324. Converging channel; 325. Mixing channel; 326. Diverging channel; 40. Linear compressor; 410. Linear motor; 420. Piston; 430. Cylinder; 440. First oil storage tank; 50. Rotary compressor; 510. First rotating motor; 520. First crankshaft; 521. First shaft section; 5211. First oil passage; 522. Second shaft section; 5221. Second oil passage; 530. First crankshaft support; 540. Second crankshaft support; 550. First bearing; 560. Second oil storage tank; 60. Second oil storage tank; 60. Scroll compressor; 610. Second rotating motor; 620. Second crankshaft; 630. Third crankshaft support; 640. Scroll moving disk; 650. Scroll stationary disk; 660. Third oil storage tank; 670. Second bearing. Detailed implementation manners

[0031] To make the objectives, technical solutions and advantages of the present invention clearer, the technical solutions in the present invention will be clearly and completely described below with reference to the accompanying drawings in the present invention. Apparently, the described embodiments are some but not all of the embodiments of the present invention. All other embodiments obtained by those of ordinary skill in the art based on the embodiments in the present invention without making creative efforts shall fall within the protection scope of the present invention.

[0032] In the description of the embodiments of the present invention, it should be noted that the orientation or positional relationships indicated by the terms "center", "longitudinal", "transverse", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc. are based on the orientation or positional relationships shown in the drawings, and are only for the convenience of describing the embodiments of the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus should not be construed as a limitation to the embodiments of the present invention. In addition, the terms "first", "second", and "third" are only used for descriptive purposes and cannot be construed as indicating or implying relative importance.

[0033] In the description of the embodiments of the present invention, it should be noted that, unless otherwise clearly defined and limited, the terms "connected" and "coupled" should be understood in a broad sense. For example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be directly connected or indirectly connected through an intermediate medium. For those of ordinary skill in the art, the specific meanings of the above terms in the embodiments of the present invention can be understood according to specific circumstances.

[0034] In the embodiments of the present invention, unless otherwise clearly defined and limited, the first feature being "on" or "under" the second feature can be that the first and second features are in direct contact, or the first and second features are indirectly in contact through an intermediate medium. Moreover, the first feature being "above", "over" and "on top of" the second feature can be that the first feature is directly above or obliquely above the second feature, or merely indicates that the first feature has a higher horizontal height than the second feature. The first feature being "under", "beneath" and "underneath" the second feature can be that the first feature is directly below or obliquely below the second feature, or merely indicates that the first feature has a lower horizontal height than the second feature.

[0035] In the description of this specification, the descriptions with reference to terms such as "one embodiment", "some embodiments", "example", "specific example", or "some examples" mean that the specific features, structures, materials, or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the embodiments of the present invention. In this specification, the schematic descriptions of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials, or characteristics described can be combined in a suitable manner in any one or more embodiments or examples. In addition, without contradiction, those skilled in the art can combine and combine the different embodiments or examples described in this specification and the features of different embodiments or examples.

[0036] The following Figures 1 to 10 describes the oil separator and compressor provided by the present invention.

[0037] Refer to Figure 1 and Figure 2 As shown, the oil separator 120 provided by the embodiments of the present invention includes: a spiral separation tube. A spiral oil separation channel 121 is formed inside the spiral separation tube. An air inlet 122 and an air outlet 123 are respectively provided at both ends of the spiral separation tube. Both the air inlet 122 and the air outlet 123 are communicated with the oil separation channel 121. An oil drainage structure 124 is provided on the outer side of the outer wall of the spiral separation tube. The oil drainage structure 124 is communicated with the oil separation channel 121. The oil drainage structure 124 is used to drain the lubricating oil in the oil separation channel 121.

[0038] It should be noted that the above "outer side of the outer wall of the spiral separation tube" can be referred to Figure 2as indicated by the arrow direction

[0039] The oil separator 120 provided by the present invention is set as a spiral separation tube. During operation, the compressed gas carrying tiny lubricating oil droplets enters the oil separation channel 121 through the air inlet 122. Under the action of the centrifugal force in the spiral oil separation channel 121, the lubricating oil droplets can adhere to the outer side of the inner wall of the spiral separation tube. When accumulated to a certain extent, the tiny lubricating oil droplets can form larger lubricating oil droplets and are discharged through the oil drainage structure 124 arranged on the outer side of the outer wall of the spiral separation tube, which can prevent the tiny lubricating oil droplets from entering the system along with the compressed gas, and has a good oil separation effect. Moreover, the oil separator 120 provided by the present invention separates oil and gas through the centrifugal force of the spiral separation tube, which can meet the oil and gas separation requirements in normal gravity and micro-gravity scenarios, and solves the defect that the existing oil separator 120 has a poor oil separation effect in normal gravity and micro-gravity scenarios.

[0040] Specifically, the spiral separation tube includes a plurality of (greater than or equal to two) spiral tube units connected in sequence, and the inner diameter of the spiral separation tube can be adjusted according to specific application requirements. For example, according to the exhaust volume of the compressor, the inner diameter of the spiral separation tube is adjusted to optimize the gas flow rate and separation effect. If the exhaust volume is large, a larger inner diameter can be designed to avoid too rapid air flow and ensure that the oil droplets have enough time to be separated; if the exhaust volume is small, the inner diameter can be appropriately reduced to increase the rotation speed of the gas, thereby enhancing the centrifugal force and improving the separation effect. The design parameters of the spiral separation tube can also be adjusted according to the exhaust volume, flow rate and oil-gas mixing degree of the compressor. For example, the adjustment of the inner diameter of the spiral separation tube and the number of spiral tube units can ensure efficient oil and gas separation under various working conditions.

[0041] The oil drainage structure 124 can adopt various forms such as oil drainage holes, oil drainage grooves or oil drainage hollows. Among them, the oil drainage holes are formed by setting a plurality of (greater than or equal to one) holes on the outer side of the outer wall of the spiral separation tube, and the separated lubricating oil can flow along the inner wall of the tube and be smoothly discharged through the oil drainage holes. The oil drainage groove is similar to the oil drainage hole, and forms a groove-like structure such as a strip shape or a square shape on the outer side of the outer wall of the spiral tube. The oil drainage hollow forms a channel by hollowing out a partial area on the outer wall of the spiral tube or forming a channel, so that the oil can flow out through the gap, reducing the resistance to the air flow, and is suitable for scenarios with a high oil drainage rate.

[0042] See Figure 1 and Figure 2As shown, by way of example, the oil drainage structure 124 in this embodiment is an oil drainage hole, which has a simple structure and is easy to manufacture. The aperture of the oil drainage hole can be set according to actual requirements. For example, the aperture ratio of the spiral separation tube to the oil drainage hole is set in the range of 2 to 20, and the aperture size is adjusted according to the exhaust volume of the compressor, the degree of oil-gas mixing, and the separation efficiency requirements. For applications with a large exhaust volume, the aperture of the oil drainage hole can be appropriately increased to ensure that the oil can be discharged smoothly and avoid excessive oil accumulation affecting the separation effect. For applications with a small exhaust volume, the aperture of the oil drainage hole can be reduced to ensure that the oil drainage process does not affect the gas flow and achieve an ideal oil-gas separation effect at the same time.

[0043] See Figure 1 and Figure 2 As shown, according to some embodiments of the present invention, the spiral separation tube includes a plurality of spiral tube units connected in sequence. All the spiral tube units have the same structure and form a cylindrical spiral separation tube.

[0044] By connecting a plurality of spiral tube units in series, a longer oil-gas separation path can be achieved, improving the oil-gas separation effect. Each spiral tube unit is designed with a spiral structure, making the oil-gas mixture move spirally in the pipeline and enhancing the separation efficiency of the oil and gas. Since all the spiral tube units have the same structure, the production and manufacturing process can be simplified.

[0045] According to some embodiments of the present invention, the diameters of the plurality of spiral tube units gradually decrease along the axial direction of the spiral separation tube, forming a conical spiral separation tube.

[0046] By setting the diameters of the plurality of spiral tube units to gradually decrease, the oil-gas separation process can be optimized, gradually accelerating the rotational movement of the gas flow, thereby improving the oil-gas separation efficiency.

[0047] Specifically, as the diameter of the spiral tube unit decreases, the speed of the gas flow will gradually increase, and the separation effect of the oil in the gas flow will also be enhanced. Especially at a higher speed, the separation of the oil and gas is more thorough.

[0048] It should be noted that the number of spiral tube units can be set according to actual requirements. Without affecting the exhaust, by increasing or decreasing the number of spiral tube units, the separation effect and processing capacity of the separator can be flexibly adjusted. If the exhaust volume is large, the number of spiral tube units can be increased to provide a longer separation path and improve the oil-gas separation effect. On the contrary, if the exhaust volume is small, the number of spiral tube units can be reduced to ensure smooth gas flow and a stable separation effect.

[0049] See Figure 1 and Figure 2As shown, according to some embodiments of the present invention, an oil drainage structure 124 is provided at the outer bottom of the outer wall of each spiral tube unit.

[0050] By providing an oil drainage structure 124 at the outer bottom of the outer wall of each spiral tube unit, the accumulated oil in each spiral tube unit can be effectively drained in a timely manner, avoiding the accumulation of oil in the separation tube and thus affecting the oil-gas separation effect. Setting the oil drainage structure 124 at the bottom is conducive to the oil flowing naturally towards the oil drainage structure 124 by its own gravity, thereby realizing the automatic discharge of the oil.

[0051] It should be noted that the above-mentioned "outer bottom of the outer wall of the spiral tube unit" specifically refers to the lowest position of the outer wall of the spiral tube unit after the oil separator 120 is installed on the compressor.

[0052] According to some embodiments of the present invention, a lipophilic structure 125 is provided on the outer side of the inner wall of the oil separation channel 121, and an oil-repellent structure 126 is provided on the inner side of the inner wall of the oil separation channel 121.

[0053] By providing a lipophilic structure 125 on the outer side of the inner wall of the oil separation channel 121 and an oil-repellent structure 126 on the inner side of the inner wall of the oil separation channel 121, the oil can be effectively guided to the outside of the channel, while reducing the adhesion of the oil on the inner side of the inner wall, and the wall surface affects the exhaust effect.

[0054] Specifically, the function of the lipophilic structure 125 on the outside is to attract and hold the oil, making it move towards the exhaust structure, while the oil-repellent structure 126 can effectively reduce the adhesion of the oil on the inner side of the inner wall, enabling the air flow to pass through the oil separation channel 121 more smoothly and preventing the secondary adhesion and accumulation of the oil.

[0055] The lipophilic structure 350 can be a lipophilic layer or a lipophilic micro-nano protrusion structure, etc. The oil-repellent structure 360 can be an oil-repellent layer or an oil-repellent micro-nano protrusion structure, etc.

[0056] As an example, in this embodiment, the lipophilic structure 125 is a lipophilic layer, and the oil-repellent structure 126 is an oil-repellent layer. Among them, the lipophilic structure 125 and the oil-repellent structure 126 can be prepared by electroplating, electroless plating, etc. For example, when processing the lipophilic structure 125, the part of the spiral separation tube corresponding to the oil-repellent structure 126 can be physically blocked. After the lipophilic structure 125 is processed, the part of the spiral separation tube corresponding to the lipophilic structure 125 can be physically blocked to process the oil-repellent structure 126. After the lipophilic structure 125 and the oil-repellent structure 126 are processed, the tube body can be bent into a spiral shape.

[0057] According to some embodiments of the present invention, a porous oil filter screen (not shown in the figure) is provided at the air inlet and the air outlet.

[0058] By providing a porous oil filter screen at the air inlet and the air outlet, the oil separation effect of the oil separator 120 can be further enhanced.

[0059] The compressor provided by the present invention will be described below. The compressor described below can be correspondingly referred to the oil separator 120 described above.

[0060] See Figures 3 to 10 As shown, the compressor provided by the embodiment of the present invention includes: a housing 10, a partition plate 20, and the oil separator 120 as described in any one of the above; a sealed cavity 110 is formed inside the housing 10; the partition plate 20 is located inside the sealed cavity 110 and divides the sealed cavity 110 into a low-pressure cavity 111 and a high-pressure cavity 112, and an exhaust muffler cavity 113 is provided inside the high-pressure cavity 112; the oil separator 120 is provided inside the exhaust muffler cavity 113.

[0061] The compressor provided by the present invention has a good oil separation effect due to the adoption of the above oil separator 120, can prevent tiny lubricating oil droplets from entering the system along with the compressed gas, and can meet the oil-gas separation requirements in normal gravity and micro-gravity scenarios.

[0062] Specifically, when the compressor works, the compressed gas carrying tiny lubricating oil droplets enters the exhaust muffler cavity 113, and after entering the oil separation channel through the air inlet, under the action of the centrifugal force of the spiral oil separation channel, the lubricating oil droplets can adhere to the outer side of the inner wall of the spiral separation tube. When accumulated to a certain extent, the tiny lubricating oil droplets can form larger lubricating oil droplets, and are discharged through the oil drainage structure provided on the outer side of the outer wall of the spiral separation tube, and then return to the high-pressure cavity 112. The air outlet 123 of the oil separator 120 is communicated with the exhaust pipe of the compressor, and is used to lead the separated compressed gas to a set position.

[0063] In some embodiments, the cross-sectional size of the housing 10 can be correspondingly set according to the size of the internal cavity. For example, the cross-sectional size of the housing 10 at the position corresponding to the low-pressure cavity 111 is larger, and the cross-sectional size of the housing 10 at the position corresponding to the high-pressure cavity 112 is smaller.

[0064] See Figures 3 to 10As shown, according to some embodiments of the present invention, the compressor further includes: a differential pressure ejector oil pumping structure 30, which is located in the sealed cavity 110. The differential pressure ejector oil pumping structure 30 includes a body 310, and a pump oil passage 320 is formed in the body 310. The pump oil passage 320 includes a high-pressure ejector oil inlet 321, a low-pressure ejected oil inlet 322, a nozzle 323, a contraction passage 324, a mixing passage 325, and an expansion passage 326. The high-pressure ejector oil inlet 321 and the low-pressure ejected oil inlet 322 are both communicated with the nozzle 323, and the nozzle 323, the contraction passage 324, the mixing passage 325, and the expansion passage 326 are communicated in sequence; the high-pressure ejector oil inlet 321 is communicated with the high-pressure cavity 112, the low-pressure ejected oil inlet 322 is communicated with the low-pressure cavity 111, and the expansion passage 326 is communicated with the moving pair of the compressor.

[0065] By providing the differential pressure ejector oil pumping structure, when the compressor works, the lubricating oil (ejecting flow) in the high-pressure cavity 112 enters the nozzle 323 of the pump oil passage 320 through the high-pressure ejector oil inlet 321. Under the action of the nozzle 323, the flow rate of the lubricating oil becomes faster, and a low-pressure area is formed at the position of the low-pressure ejected oil inlet 322, sucking the lubricating oil (ejected flow) in the low-pressure cavity 111 into the pump oil passage 320. The formed lubricating oil mixture gradually expands and fills the entire mixing passage 325. After a period of mixing process, at the outlet of the mixing passage 325, the lubricating oil mixture becomes a uniform flow. Then, under the action of the expansion passage 326, the flow rate of the uniform flow decreases and the static pressure increases, and it can enter the moving pair of the compressor for lubrication. Its pump oil pressure difference is large and the self-priming ability is strong, effectively solving the problem of insufficient oil supply of the existing compressor at low speed, low vibration or low oil level.

[0066] In addition, since the low-pressure cavity 111 and the high-pressure cavity 112 are located on both sides of the partition plate 20, when the attitude of the compressor changes, the lubricating oil in any one of the low-pressure cavity 111 and the high-pressure cavity 112 can smoothly enter the ejector oil pumping structure, solving the problem of insufficient oil supply at the oil level height and the position of the moving pair in the compressor caused by the vibration and bump of the compressor, the change of the installation attitude, or the change of the gravitational acceleration in the use scenario, and is applicable to scenarios such as automobiles, airplanes, high-speed rails, tanks, ships, flying cars, aerospace vehicles, satellites, space stations, and extraterrestrial space bases. Figure 4 As an example, when the compressor tilts in the front-rear direction, the lubricating oil in any one of the low-pressure cavity 111 and the high-pressure cavity 112 can smoothly enter the ejector oil pumping structure.

[0067] According to some embodiments of the present invention, the compressor further includes a first oil inlet pipe (not shown in the figure) and a second oil inlet pipe (not shown in the figure), one end of the first oil inlet pipe is connected to the low-pressure cavity 111, and the other end of the first oil inlet pipe is connected to the low-pressure injected oil inlet 322, one end of the second oil inlet pipe is connected to the high-pressure cavity 112, and the other end of the second oil inlet pipe is connected to the high-pressure injected oil inlet 321.

[0068] By setting up the first oil inlet pipe and the second oil inlet pipe, the low-pressure injected oil inlet 322 and the high-pressure injected oil inlet 321 can be connected to the gathering positions of the lubricating oil in the low-pressure cavity 111 and the high-pressure cavity 112 (such as the bottom of the cavity) respectively through the oil inlet pipes, thereby optimizing the oil pumping effect of the injected pump oil structure and being able to meet the requirement of sufficient lubricating oil supply when the compressor undergoes large posture changes.

[0069] Of course, in some embodiments, the first oil inlet pipe or the second oil inlet pipe may be separately provided to meet the spatial layout in the sealing cavity 110 or other practical requirements.

[0070] According to some embodiments of the present invention, both the first oil inlet pipe and the second oil inlet pipe are flexible oil inlet pipes.

[0071] By setting both the first oil inlet pipe and the second oil inlet pipe as flexible oil inlet pipes, during operation, the first oil inlet pipe and the second oil inlet pipe can follow the movement of the lubricating oil in the low-pressure chamber 111 and the high-pressure chamber 112 under the action of gravity, thereby further improving the lubricating oil supply effect of the compressor during large-scale posture changes.

[0072] Specifically, the first oil inlet pipe and the second oil inlet pipe can be made of rubber materials with strong weather resistance, such as fluororubber (FKM) or ethylene propylene diene monomer (EPDM), etc. These materials have excellent high temperature resistance, chemical corrosion resistance and weather resistance, can maintain long-term stable performance in harsh working environments, and effectively improve the reliability and service life of the equipment.

[0073] Three specific implementations of the compressor provided by the present invention are described below, namely a linear compressor 40 , a rotor compressor 50 , and a scroll compressor 60 .

[0074] See also Figure 4 As shown, according to some embodiments of the present invention, the compressor is a linear compressor 40; it also includes a linear motor 410, a piston 420 and a cylinder 430, the cylinder 430 is located in the sealed cavity 110, the linear motor 410 is transmission-connected to the piston 420, the piston 420 and the cylinder 430 are axially slidably matched, and the expansion channel 326 is connected to the matching gap between the piston 420 and the cylinder 430.

[0075] When the linear compressor 40 is operating, the linear motor 410 drives the piston 420 to slide axially in the cylinder 430 to complete the processes of gas suction, compression, and discharge. The compressed gas is discharged through the exhaust passage. During this process, the lubricating oil in the high-pressure cavity 112 enters the differential ejector pump oil structure 30 through the high-pressure ejector oil inlet 321. At the same time, the lubricating oil in the low-pressure cavity 111 enters the differential ejector pump oil structure 30 through the low-pressure ejector oil inlet 322 under the action of negative pressure, and is driven by the high-pressure lubricating oil to form a mixed lubricating oil fluid with sufficient pressure through the contraction channel 324, the mixing channel 325, and the expansion channel 326 in sequence, and enters the kinematic pair (the mating clearance between the piston 420 and the cylinder 430) of the linear compressor 40, thereby realizing the lubrication function.

[0076] See Figure 4 As shown, during the lubrication process, part of the lubricating oil returns to the low-pressure cavity 111 through the mating clearance between the piston 420 and the cylinder 430, and another part of the lubricating oil can pass through the mating clearance between the piston 420 and the cylinder 430, follow the compressed gas into the exhaust silencer cavity 113, and return to the high-pressure cavity 112 under the action of the oil separator 120. Specifically, see Figure 4 the direction of the arrow shown in

[0077] In addition, a first oil storage groove 440 can be provided at the position of the mating clearance between the piston 420 and the cylinder 430 corresponding to the expansion channel 326. When the lubricating oil is discharged through the expansion channel 326, it can accumulate in the first oil storage groove 440 to fully supply oil to the mating clearance between the piston 420 and the cylinder 430.

[0078] When the compressor is the linear compressor 40, the differential ejector pump oil structure 30 can be provided as an independent component in the sealed cavity 110, or the differential ejector pump oil structure 30 (the body 310) can be integrally provided with the partition plate 20 or the cylinder block to reduce its occupancy of the space in the sealed cavity 110 and improve the compactness of the compressor.

[0079] See Figure 4 As shown, as an example, the differential ejector pump oil structure 30 (the body 310) in this embodiment is integrally provided with the cylinder 430.

[0080] See Figures 5 to 8As shown, according to some embodiments of the present invention, the compressor is a rotary compressor 50; it further includes a first rotary motor 510, a first crankshaft 520, a first crankshaft support 530 and a second crankshaft support 540. The first crankshaft support 530 and the second crankshaft support 540 are coaxially arranged and spaced apart in the sealed cavity 110. One end of the first crankshaft 520 is rotatably engaged with the housing 10, and the other end of the first crankshaft 520 is rotatably engaged with the first crankshaft support 530 and the second crankshaft support 540. The first rotary motor 510 is drivingly connected to the first crankshaft 520, and the expansion channel 326 communicates with the mating clearance between the first crankshaft 520 and the first crankshaft support 530 and the second crankshaft support 540.

[0081] When the rotary compressor 50 works, the first rotary motor 510 drives the first crankshaft 520 to rotate, and then drives the rotor to perform compression work in the sealed cavity 110. The first rotary motor 510 drives the first crankshaft 520 to rotate through the driving connection with the first crankshaft 520. One end of the first crankshaft 520 is rotatably engaged with the housing 10, and the other end is rotatably engaged with the first crankshaft support 530 and the second crankshaft support 540, ensuring the smooth rotation of the crankshaft. During this process, the lubricating oil in the high-pressure cavity 112 enters the differential ejector pump oil structure 30 through the high-pressure ejector oil inlet 321. At the same time, the lubricating oil in the low-pressure cavity 111 enters the differential ejector pump oil structure 30 through the low-pressure ejected oil inlet 322 under the action of negative pressure, and is driven by the high-pressure lubricating oil to form a mixed lubricating oil fluid with sufficient pressure and enter the moving pairs of the rotary compressor 50 (the mating clearance between the first crankshaft 520 and the first crankshaft support 530 and the second crankshaft support 540) in sequence through the contraction channel 324, the mixing channel 325 and the expansion channel 326, thereby realizing the lubrication function.

[0082] See Figure 5 and Figure 6 As shown, during the lubrication process, part of the lubricating oil returns to the low-pressure cavity 111 through the mating clearance between the first crankshaft 520 and the first crankshaft support 530, and another part of the lubricating oil enters the exhaust muffler cavity 113 following the compressed gas through the mating clearance between the first crankshaft 520, the first crankshaft support 530 and the second crankshaft support 540, and returns to the high-pressure cavity 112 under the action of the oil separator 120. At the same time, a first oil return channel is provided in the first crankshaft 520, and part of the lubricating oil can return to the rotationally mating position (the first bearing 550) between the first crankshaft 520 and the inner wall of the housing 10 through the first oil return channel, lubricate this place, and then return to the low-pressure cavity 111. Specifically, see Figure 5 and Figure 6 the direction of the arrow shown in

[0083] In addition, a second oil storage groove 560 may be provided at a position where the clearance between the first crankshaft 520 and the first crankshaft support 530 or the second crankshaft support 540 corresponds to the expansion channel 326. When the lubricating oil is discharged through the expansion channel 326, it can accumulate in the second oil storage groove 560 to fully supply oil to the clearance between the first crankshaft 520 and the first crankshaft support 530 or the second crankshaft support 540.

[0084] See Figure 5 and Figure 6 As shown, as an example, a second oil storage groove 560 is provided at a position where the clearance between the first crankshaft 520 and the first crankshaft support 530 in this embodiment corresponds to the expansion channel 326.

[0085] See Figures 5 to 8 As shown, according to some embodiments of the present invention, the first crankshaft 520 is provided with a first shaft section 521 and a second shaft section 522 at intervals. The outer wall of the first shaft section 521 is provided with a first oil passage 5211 along the length direction, and the outer wall of the second shaft section 522 is provided with a second oil passage 5221 along the length direction. Both the first oil passage 5211 and the second oil passage 5221 are communicated with the expansion channel 326.

[0086] By providing the first shaft section 521 and the second shaft section 522 on the crankshaft and respectively opening the first oil passage 5211 and the second oil passage 5221 on the first shaft section 521 and the second shaft section 522, the lubricating oil at the clearance between the first crankshaft 520 and the first crankshaft support 530 and the second crankshaft support 540 can be introduced into the high-pressure cavity 112 and the low-pressure cavity 111 through the first oil passage 5211 and the second oil passage 5221.

[0087] See Figures 5 to 8 As shown, according to some embodiments of the present invention, the first oil passage 5211 and the second oil passage 5221 are arranged on the first crankshaft 520 in opposite directions.

[0088] By arranging the first oil passage 5211 and the second oil passage 5221 on the first crankshaft 520 in opposite directions, the lubricating oil flow path can be increased, so that the clearances between the first crankshaft 520 and the first crankshaft support 530 and the second crankshaft support 540 and the clearance between the first crankshaft 520 and the rotary piston are filled with lubricating oil, achieving full lubrication of the friction pairs cooperating with the first crankshaft 520. The accumulated lubricating oil ensures reliable lubrication when the compressor starts and the suction and discharge pressure differences have not been established.

[0089] Specifically, "the first oil passage 5211 and the second oil passage 5221 are arranged on the first crankshaft 520 in opposite directions" means that the included angle between the first oil passage 5211 and the second oil passage 5221 is 180°, and they are respectively located on the opposite sides of the first crankshaft 520.

[0090] SeeFigure 5 and Figure 6 As shown in Figure 6 , according to some embodiments of the present invention, when the compressor is a rotary compressor 50, the differential pressure ejector oil structure 30 can be provided as an independent component in the sealed cavity 110, or the differential pressure ejector oil structure 30 (body 310) can be integrally provided with the partition plate 20, the first crankshaft support 530 or the second crankshaft support 540 to reduce its space occupation of the sealed cavity 110 and improve the compactness of the compressor.

[0091] See Figure 5 and Figure 6 As shown in Figure 6 , as an example, in this embodiment, the differential pressure ejector oil structure 30 (body 310) is integrally provided with the first crankshaft support 530, the partition plate 20 is adjacently provided on the first crankshaft support 530, and an oil passage for communicating the low-pressure cavity 111 and the low-pressure ejector oil inlet 322 is provided on the partition plate 20.

[0092] In some embodiments, the partition plate 20 can also be integrally provided with the first crankshaft support 530 or the second crankshaft support 540 to reduce the space occupation of the partition plate 20 in the sealed cavity 110 and improve the compactness of the compressor.

[0093] See Figure 9 and Figure 10 As shown in Figure 10 , according to some embodiments of the present invention, the compressor is a scroll compressor 60; it further includes a second rotating motor 610, a second crankshaft 620, a third crankshaft support 630, a scroll orbiting disk 640 and a scroll fixed disk 650. The third crankshaft support 630, the scroll orbiting disk 640 and the scroll fixed disk 650 are all provided in the sealed cavity 110. One end of the second crankshaft 620 is rotatably matched with the housing 10, and the other end of the second crankshaft 620 is rotatably matched with the third crankshaft support 630 and connected to the scroll orbiting disk 640. The expansion channel 326 communicates with the fitting clearance between the second crankshaft 620 and the third crankshaft support 630 and the fitting clearance between the scroll orbiting disk 640 and the scroll fixed disk 650.

[0094] When the scroll compressor 60 is operating, the second rotating motor 610 drives the second crankshaft 620 to rotate, thereby driving the scroll moving disk 640 to move relative to the scroll stationary disk 650 within the sealed cavity 110 to complete the gas compression process. One end of the second crankshaft 620 is rotatably fitted with the housing 10, and the other end is rotatably fitted with the third crankshaft support 630 and connected to the scroll moving disk 640. As the second crankshaft 620 rotates, the scroll moving disk 640 rotates in cooperation with the scroll stationary disk 650 to form multiple compression chambers, and the gas is gradually compressed within the chambers. During this process, the lubricating oil in the high-pressure cavity 112 enters the differential injection pump oil structure 30 through the high-pressure injection oil inlet 321. At the same time, the lubricating oil in the low-pressure cavity 111 enters the differential injection pump oil structure 30 through the low-pressure injected oil inlet 322 under the action of negative pressure, and is driven by the high-pressure lubricating oil to successively pass through the contraction channel 324, the mixing channel 325, and the expansion channel 326 to form a mixed lubricating oil fluid with sufficient pressure and enter the moving pairs of the scroll compressor 60 (the fitting clearance between the second crankshaft 620 and the third crankshaft support 630 and the fitting clearance between the scroll moving disk 640 and the scroll stationary disk 650), thereby realizing the lubrication function.

[0095] See Figure 9 and Figure 10 As shown, during the lubrication process, the lubricating oil enters the fitting clearance between the scroll moving disk 640 and the scroll stationary disk 650 through the expansion channel 326. Then, part of the lubricating oil enters the fitting clearance between the second crankshaft 620 and the third crankshaft support 630 and returns to the low-pressure cavity 111, and the other part of the lubricating oil follows the compressed gas into the exhaust muffler cavity 113 and finally returns to the high-pressure cavity 112 under the action of the oil separator 120. Specifically, see Figure 9 and Figure 10 the arrow directions shown in

[0096] In some embodiments, an oil return channel can be provided between the scroll moving disk 640 and the scroll stationary disk 650 to guide the lubricating oil through the oil return channel into the compressed gas cavity, then into the exhaust muffler cavity 113, and finally return to the high-pressure cavity 112 under the action of the oil separator 120.

[0097] In some embodiments, an oil return channel can be provided within the second crankshaft 620 to connect the oil return channel with the fitting clearance between the second crankshaft 620 and the third crankshaft support 630. After the lubricating oil reaches the fitting clearance between the second crankshaft 620 and the third crankshaft support 630, it can enter the oil return channel and reach the rotational fitting position of the second crankshaft 620 and the housing 10 (the second bearing 670) to lubricate this location, and then the lubricating oil can return to the low-pressure cavity 111. Additionally, a third oil storage groove 660 can be provided at the connection position between the oil return channel and the fitting clearance between the second crankshaft 620 and the third crankshaft support 630 for temporarily storing the lubricating oil.

[0098] See Figure 9 and Figure 10 As shown, according to some embodiments of the present invention, the partition plate 20 is integrally provided with the scroll stationary disk 650, and the body 310 is integrally provided with the scroll stationary disk 650.

[0099] By integrally providing the partition plate 20 with the scroll stationary disk 650 and integrally providing the body 310 with the scroll stationary disk 650, the space occupied by the partition plate 20 and the differential pressure ejector pump oil structure 30 in the sealed cavity 110 can be reduced, thereby improving the compactness of the compressor. At this time, oil passageways for communicating the low-pressure cavity 111 and the low-pressure oil suction inlet 322 are provided on both the third crankshaft support 630 and the scroll orbiting disk 640.

[0100] According to some embodiments of the present invention, the compressor may also be a screw compressor or a centrifugal compressor (equipped with a pump body).

[0101] From the description of the above embodiments, it can be seen that the compressor provided by the present invention may be a linear compressor 40, a rotor compressor 50, a scroll compressor 60, a screw compressor or a centrifugal compressor. When the differential pressure ejector pump oil structure 30 is applied to compressors of different types, it can achieve large differential pressure pump oil and has a strong self-priming ability, effectively solving the problem of insufficient oil supply in existing compressors at low speeds, low vibrations or low oil levels. In addition, since the high-pressure cavity 112 and the low-pressure cavity 111 are located on both sides of the partition plate 20, when the attitude of the compressor changes, the lubricating oil in either the high-pressure cavity 112 or the low-pressure cavity 111 can smoothly enter the ejector pump oil structure, solving the problem of insufficient oil supply at the oil level height and the position of the moving pair in the compressor caused by changes in the installation attitude of the compressor or the change in the gravitational acceleration of the use scenario. It is applicable to scenarios such as automobiles, airplanes, high-speed rails, tanks, ships, flying cars, aerospace vehicles, satellites, space stations, and extraterrestrial space bases.

[0102] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention and are not intended to limit them; although the present invention has been described in detail with reference to the foregoing embodiments, those of ordinary skill in the art should understand that they can still modify the technical solutions described in the foregoing embodiments, or perform equivalent replacements on some of the technical features; and these modifications or replacements do not make the essence of the corresponding technical solutions deviate from the spirit and scope of the technical solutions of the embodiments of the present invention.

Claims

1. An oil separator, characterized in that, include: A spiral separation tube, wherein a spiral oil separation channel is formed in the spiral separation tube, wherein an air inlet and an exhaust port are respectively arranged at both ends of the spiral separation tube, wherein both the air inlet and the exhaust port are communicated with the oil separation channel, and an oil discharge structure is arranged on the outer side of the outer wall of the spiral separation tube, wherein the oil discharge structure is communicated with the oil separation channel, and wherein the oil discharge structure is used to discharge the lubricating oil in the oil separation channel.

2. The oil separator according to claim 1, characterized in that, The spiral separation tube comprises a plurality of spiral tube units connected in sequence, all of which have the same structure to form a cylindrical spiral separation tube; or, the diameters of the plurality of spiral tube units gradually decrease along the axial direction of the spiral separation tube to form a conical spiral separation tube.

3. The oil separator according to claim 2, wherein, The outer bottom of the outer wall of each spiral tube unit is provided with the oil drainage structure, the outer side of the inner wall of the oil separation channel is provided with an oleophilic structure, and the inner side of the inner wall of the oil separation channel is provided with an oleophobic structure.

4. The oil separator according to claim 1, characterized in that, The air inlet and / or the air outlet is provided with a porous oil filter.

5. A compressor, characterized in that, include: A housing having a sealed cavity formed therein; A partition plate, the partition plate is located in the sealed cavity and divides the sealed cavity into a low-pressure cavity and a high-pressure cavity, and an exhaust muffler cavity is provided in the high-pressure cavity; The oil separator according to any one of claims 1 to 4, wherein the oil separator is arranged in the exhaust muffler chamber.

6. The compressor according to claim 5, characterized in that, Also includes: A pressure differential injection pump oil structure, the pressure differential injection pump oil structure is located in the sealed cavity, the pressure differential injection pump oil structure comprises a body, an oil pumping channel is formed in the body, the oil pumping channel comprises a high-pressure injection oil inlet, a low-pressure injected oil inlet, a nozzle, a contraction channel, a mixing channel and an expansion channel, the high-pressure injection oil inlet and the low-pressure injected oil inlet are both connected to the nozzle, and the nozzle, the contraction channel, the mixing channel and the expansion channel are connected in sequence; The high-pressure injection oil inlet is communicated with the high-pressure cavity, the low-pressure injection oil inlet is communicated with the low-pressure cavity, and the expansion channel is communicated with the kinematic pair of the compressor.

7. The compressor according to claim 6, characterized in that, The compressor is a linear compressor; It also includes a linear motor, a piston and a cylinder. The cylinder is located in the sealed cavity. The linear motor is connected to the piston in a transmission manner. The piston and the cylinder are axially slidably matched. The expansion channel is connected to the matching gap between the piston and the cylinder.

8. The compressor according to claim 6, characterized in that, The compressor is a rotary compressor; It also includes a first rotating motor, a first crankshaft, a first crankshaft support and a second crankshaft support. The first crankshaft support and the second crankshaft support are coaxial and spaced apart in the sealed cavity. One end of the first crankshaft is rotatably matched with the housing, and the other end of the first crankshaft is rotatably matched with the first crankshaft support and the second crankshaft support. The first rotating motor is drivingly connected to the first crankshaft, and the expansion channel is connected to the matching clearance between the first crankshaft and the first crankshaft support and the second crankshaft support.

9. The compressor according to claim 8, wherein The first crankshaft is provided with a first shaft section and a second shaft section at intervals. The outer wall of the first shaft section is provided with a first oil passage along the length direction, and the outer wall of the second shaft section is provided with a second oil passage along the length direction. Both the first oil passage and the second oil passage are communicated with the expansion passage, and the first oil passage and the second oil passage are arranged on the first crankshaft in opposite directions.

10. The compressor according to claim 6, characterized in that, The compressor is a scroll compressor; It further includes a second rotating motor, a second crankshaft, a third crankshaft support, a scroll moving disk and a scroll stationary disk. The third crankshaft support, the scroll moving disk and the scroll stationary disk are all arranged in the sealed cavity. One end of the second crankshaft is rotationally matched with the housing, and the other end of the second crankshaft is rotationally matched with the third crankshaft support and connected to the scroll moving disk. The expansion passage is communicated with the fitting clearance between the second crankshaft and the third crankshaft support and the fitting clearance between the scroll moving disk and the scroll stationary disk.

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