Double-loop differential pressure oil pumping compressor

Abstract

The utility model provides a double-loop differential pressure pump oil compressor. The double-loop differential pressure pump oil compressor comprises a shell, a first partition plate, an oil separator and a compression assembly. A sealing cavity is formed in the shell; the first partition plate divides the sealing cavity into a low-pressure cavity and a high-pressure cavity, and an exhaust noise reduction cavity is formed in the high-pressure cavity. The compression assembly comprises a motor, a crankshaft and at least one stage of compression unit; the compression unit comprises a cylinder body and a rotary piston, an air suction cavity and a compression cavity are arranged between the cylinder body and the corresponding rotary piston, a first oil suction channel is arranged between the air suction cavity and the low-pressure cavity, the compression cavity is communicated with the oil separator, and an oil return channel is arranged between the exhaust silencing cavity and the high-pressure cavity; oil passing channels are arranged on the crankshaft at intervals, a center hole is formed in the crankshaft, and a second oil suction channel is arranged between the high-pressure cavity and the oil passing channels. The rotary compressor overcomes the defects that an existing rotary compressor depends on high-speed rotation of a crankshaft to drive an oil pump, oil supply is insufficient under the conditions of low rotating speed, low oil level and gravity change, and the lubricating effect and the operation efficiency are affected.

Description

Technical Field

[0001] This utility model relates to the field of compressor technology, and in particular to a dual-circuit differential pressure pump oil compressor. Background Technology

[0002] In existing rotary compressors, a helical pump blade is typically installed in the inner bore of one end of the crankshaft. The rotation of the crankshaft drives the pump blade to rotate, thereby achieving the flow of refrigerant oil. Alternatively, a helical pump body is installed in the inner bore of the crankshaft, and the cooperation between the pump body and the inner bore of the crankshaft forms a lubricating oil pump to supply lubrication and sealing clearances of various friction pairs in the compressor. However, the oil pump driving force of existing rotary compressors mainly relies on the high-speed rotation of the crankshaft, resulting in a small pressure differential of the oil pump, poor self-priming ability, and a tendency to cause insufficient oil supply at low speeds and low oil levels.

[0003] Especially in special scenarios, such as when the installation posture of a horizontal rotary compressor is variable or when it is used in a microgravity environment (e.g., automobiles, airplanes, high-speed trains, tanks, ships, flying cars, spacecraft, satellites, space stations, and extraterrestrial bases), the oil level in the compressor changes or the acceleration due to gravity. Traditional oil pumps that rely on gravity, centrifugal force, or capillary force cannot effectively guarantee reliable lubrication between moving parts and efficient oil sealing of the fit clearance, thus affecting the compressor's service life and operating efficiency. Utility Model Content

[0004] This invention provides a dual-circuit differential pressure pump oil compressor to solve the defects of existing rotary compressors that rely on high-speed crankshaft rotation to drive the oil pump, resulting in insufficient oil supply under conditions of low speed, low oil level, and gravity changes, which affects lubrication effect and operating efficiency.

[0005] This utility model provides a dual-loop differential pressure pump oil compressor, including: a housing, a first partition, an oil separator, and a compression assembly.

[0006] A sealed cavity is formed inside the housing; the first partition is located inside the sealed cavity and divides the sealed cavity into a low-pressure cavity and a high-pressure cavity, and an exhaust silencing chamber is provided inside the high-pressure cavity; the oil separator is located inside the exhaust silencing chamber; the compression assembly includes a motor, a crankshaft and at least one compression unit, both ends of the crankshaft are rotatably engaged with the housing, and the motor is drively connected to the crankshaft.

[0007] The compression unit includes a cylinder and a rotary piston. The rotary piston is located on the crankshaft. An intake chamber and a compression chamber are provided between the cylinder and the corresponding rotary piston. The intake chamber is connected to the corresponding compression chamber. A first oil suction channel is provided between the intake chamber and the low-pressure chamber. The compression chamber is connected to the oil separator. An oil return channel is provided between the exhaust muffler chamber and the high-pressure chamber.

[0008] The crankshaft is provided with oil passages that correspond one-to-one with the compression unit. The crankshaft is provided with a central hole. The oil passages are connected to the first end of the central hole. The second end of the central hole is connected to the rotational engagement of the crankshaft and the housing and the low-pressure cavity in sequence. A second oil suction channel is provided between the high-pressure cavity and the oil passages.

[0009] According to the dual-circuit differential pressure pump oil compressor provided by this utility model, the compression assembly includes multiple stages of compression units connected in series. The compression chamber of the first stage compression unit is connected to the suction chamber of the subsequent stage compression unit, and the compression chamber of the last stage is connected to the exhaust silencer chamber. A first oil suction channel is provided between the suction chamber of at least one stage compression unit and the low-pressure chamber. Alternatively, the compression assembly includes multiple stages of compression units connected in parallel. The compression chamber of each stage compression unit is connected to the exhaust silencer chamber, and a first oil suction channel is provided between the suction chamber of at least one stage compression unit and the low-pressure chamber.

[0010] According to the dual-circuit differential pressure pump oil compressor provided by this utility model, the compression assembly further includes 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 crankshaft is rotatably engaged with the housing, and the other end of the crankshaft is rotatably engaged with the first crankshaft support and the second crankshaft support. The multiple compression units are all located between the first crankshaft support and the second crankshaft support. A second partition is provided between adjacent compression units, and the crankshaft passes through the second partition. A first oil suction hole is provided on the first partition, and a second oil suction hole is provided on the first crankshaft support. The first oil suction hole and the second oil suction hole communicate to form the first oil suction channel.

[0011] According to the dual-circuit differential pressure pump oil compressor provided by this utility model, at least one of the first crankshaft support, the second crankshaft support and the second partition is provided with the second oil suction channel.

[0012] According to the dual-circuit differential pressure pump oil compressor provided by this utility model, the first crankshaft support is provided with a second oil suction channel, and the first crankshaft support is provided with a first oil storage tank at the outlet of the second oil suction channel, and the first oil storage tank is connected to the oil passage.

[0013] According to the dual-circuit differential pressure pump oil compressor provided by this utility model, a second oil storage tank is provided between the crankshaft and the second partition plate, and the second oil storage tank is connected to the oil passage.

[0014] According to the dual-circuit differential pressure pump oil compressor provided by this utility model, the first partition plate and the first crankshaft support are integrally formed.

[0015] According to the dual-circuit differential pressure pump oil compressor provided by this utility model, the oil separator includes a spiral separation tube, a spiral oil separation channel is formed inside the spiral separation tube, an air inlet and an exhaust outlet are respectively provided at both ends of the spiral separation tube, and the air inlet and the exhaust outlet are both connected to the oil separation channel; the air inlet is connected to the compression chamber located in the last stage, the exhaust outlet is configured to be connected to the exhaust pipe, and an oil discharge structure is provided on the outer side of the outer wall of the spiral separation tube, the oil discharge structure is connected to the oil separation channel, and the oil discharge structure is connected to the exhaust silencer chamber.

[0016] According to the dual-circuit differential pressure pump oil compressor provided by this utility model, the spiral separator tube includes multiple spiral tube units connected in sequence. All the spiral tube units have the same structure to form a cylindrical spiral separator tube, or the diameter of multiple spiral tube units gradually decreases along the axial direction of the spiral separator tube to form a conical spiral separator tube.

[0017] According to the dual-loop differential pressure pump oil compressor provided by this utility model, the bottom of the outer side of the outer wall of each spiral tube unit is provided with the oil discharge structure, the outer side of the inner wall of the oil separation channel is provided with an oil-loving structure, and the inner side of the inner wall of the oil separation channel is provided with an oil-repellent structure.

[0018] The dual-circuit differential pressure pump oil compressor provided by this utility model can realize dual-circuit differential pressure pump oil, ensuring that the lubricating oil entering the low-pressure chamber from the high-pressure chamber can quickly return to the high-pressure chamber, ensuring long-term reliable lubrication of the friction pair, and can achieve stable oil supply under low speed, low oil level and gravity changes, ensuring the lubrication effect and operating efficiency of the compressor. During the intake of the compression unit, the lubricating oil in the low-pressure chamber is drawn into the intake chamber through the first oil suction channel using the intake pressure difference. After entering the intake chamber, most of the lubricating oil flows back to the low-pressure chamber through the intake channel, while a small portion adheres to the surface of the rotating piston and is carried into the corresponding compression chamber to lubricate the contact surface between the rotating piston and the corresponding cylinder. Then, it follows the compressed gas into the oil separator, where the separated lubricating oil finally flows back to the high-pressure chamber through the return oil channel. During the exhaust of the compression unit, under the action of the intake and exhaust pressure difference between the low-pressure and high-pressure chambers, the lubricating oil in the high-pressure chamber enters the crankshaft's mating clearance through the second oil suction channel for lubrication. Then, it enters the crankshaft's central hole through the oil channel, and finally reaches the rotating mating between the crankshaft and the housing for lubrication. Finally, it flows back to the low-pressure chamber, realizing the circulation of lubricating oil between the low-pressure and high-pressure chambers and providing long-term reliable lubrication for the corresponding friction pairs.

[0019] Additional aspects and advantages of this invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

[0020] To more clearly illustrate the technical solutions in this utility model or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of this utility model. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0021] Figure 1 This is one of the cross-sectional views of the dual-loop differential pressure pump oil compressor provided in this embodiment of the utility model.

[0022] Figure 2 This is a second cross-sectional view of the dual-loop differential pressure pump oil compressor provided in this embodiment of the utility model.

[0023] Figure 3 This is the third cross-sectional view of the dual-loop differential pressure pump oil compressor provided in this embodiment of the utility model.

[0024] Figure 4 This is the fourth cross-sectional view of the dual-loop differential pressure pump oil compressor provided in this embodiment of the utility model.

[0025] Figure 5 This is one of the schematic diagrams of the crankshaft in the dual-loop differential pressure pump oil compressor provided in this embodiment of the utility model.

[0026] Figure 6 This is the second schematic diagram of the crankshaft in the dual-circuit differential pressure pump oil compressor provided in this embodiment of the utility model.

[0027] Figure 7 This is one of the schematic diagrams of the oil separator in the dual-loop differential pressure pump oil compressor provided in this utility model embodiment.

[0028] Figure 8 This is the second schematic diagram of the oil separator in the dual-loop differential pressure pump oil compressor provided in this embodiment of the utility model.

[0029] Figure label:

[0030] 100. Housing; 110. Sealed cavity; 111. Low-pressure cavity; 112. High-pressure cavity; 113. Exhaust silencer cavity; 200. First partition plate; 300. Oil separator; 310. Oil separation channel; 320. Air inlet; 330. Exhaust port; 340. Oil discharge structure; 350. Oleophilic structure; 360. Oleophobic structure; 400. Compression assembly; 410. Motor; 420. Crankshaft; 421. Oil passage Channel; 422, Center hole; 430, Compression unit; 431, Cylinder block; 432, Rotary piston; 433, Intake chamber; 434, Compression chamber; 435, Exhaust chamber; 440, First crankshaft support; 441, First oil reservoir; 450, Second crankshaft support; 460, Second partition; 461, Second oil reservoir; 500, First oil suction channel; 600, Oil return channel; 700, Second oil suction channel. Detailed Implementation

[0031] To make the objectives, technical solutions, and advantages of this utility model clearer, the technical solutions of this utility model will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this utility model, not all embodiments. Based on the embodiments of this utility model, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this utility model.

[0032] In the description of the embodiments of this utility model, it should be noted that the terms "center," "longitudinal," "lateral," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," and "outer," etc., indicating the orientation or positional relationship, are based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing the embodiments of this utility model 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 limitations on the embodiments of this utility model. In addition, the terms "first," "second," and "third" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0033] In the description of the embodiments of this utility model, it should be noted that, unless otherwise explicitly specified and limited, the terms "connected" and "linked" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium. Those skilled in the art can understand the specific meaning of the above terms in the embodiments of this utility model according to the specific circumstances.

[0034] In this embodiment of the utility model, unless otherwise explicitly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature is in indirect contact with the second feature through an intermediate medium. Furthermore, "above," "on top of," and "over" the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

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

[0036] The following is combined Figures 1 to 8 This invention describes a dual-loop differential pressure pump oil compressor.

[0037] See Figures 1 to 6 As shown, the dual-loop differential pressure pump oil compressor provided in this embodiment of the present invention includes: a housing 100, a first partition 200, an oil separator 300, and a compression assembly 400.

[0038] A sealed cavity 110 is formed inside the housing 100; a first partition 200 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. An exhaust silencing cavity 113 is provided inside the high-pressure cavity 112; an oil separator 300 is located inside the exhaust silencing cavity 113; the compression assembly 400 includes a motor 410, a crankshaft 420 and at least one compression unit 430. Both ends of the crankshaft 420 are rotatably engaged with the housing 100, and the motor 410 is drive-connected to the crankshaft 420.

[0039] The compression unit 430 includes a cylinder 431 and a rotary piston 432. The rotary piston 432 is located on the crankshaft 420. An intake chamber 433 and a compression chamber 434 are provided between the cylinder 431 and the corresponding rotary piston 432. The intake chamber 433 is connected to the corresponding compression chamber 434. A first oil suction channel 500 is provided between the intake chamber 433 and the low-pressure chamber 111. The compression chamber 434 is connected to the oil separator 300. An oil return channel 600 is provided between the exhaust silencer chamber 113 and the high-pressure chamber 112.

[0040] The crankshaft 420 is provided with oil passages 421 that correspond one-to-one with the compression unit 430. The crankshaft 420 is provided with a central hole 422. The oil passages 421 are connected to the first end of the central hole 422. The second end of the central hole 422 is connected to the rotational engagement of the crankshaft 420 and the housing 100 and the low-pressure chamber 111 in sequence. A second oil suction passage 700 is provided between the high-pressure chamber 112 and the oil passages 421.

[0041] The dual-circuit differential pressure pump oil compressor provided by this utility model can realize dual-circuit differential pressure pump oil, ensuring that the lubricating oil entering the low-pressure chamber 111 from the high-pressure chamber 112 can quickly return to the high-pressure chamber 112, ensuring long-term reliable lubrication of the friction pair, and can achieve stable oil supply under low speed, low oil level and gravity changes, ensuring the lubrication effect and operating efficiency of the compressor.

[0042] The dual-loop differential pressure pump oil compressor provided by this utility model can realize differential pressure pumping through two oil supply passages.

[0043] Oiling pathway one: Oiling is carried out by utilizing the pressure difference between the suction chamber 433 and the suction pressure, which is also known as suction oiling.

[0044] See Figure 1 and Figure 2 As shown, when the compression unit 430 draws in air, the lubricating oil in the low-pressure chamber 111 is drawn into the suction chamber 433 along the first oil suction channel 500 using the suction pressure difference. After entering the suction chamber 433, most of the lubricating oil flows back to the low-pressure chamber 111 through the suction channel, while a small portion adheres to the surface of the rotating piston 432 and is carried into the corresponding compression chamber 434 to lubricate the contact surface between the rotating piston 432 and the corresponding cylinder 431. Then, it follows the compressed gas into the oil separator 300, and the separated lubricating oil finally flows back to the high-pressure chamber 112 through the return oil channel 600. The return oil channel 600 is a capillary channel.

[0045] Oiling pathway 2: Oiling is carried out using the pressure difference between exhaust pressure and intake pressure, also known as exhaust oiling.

[0046] See Figure 3 and Figure 4As shown, when the compression unit 430 exhausts, under the pressure difference between the intake and exhaust of the low-pressure chamber 111 and the high-pressure chamber 112, the lubricating oil in the high-pressure chamber 112 enters the mating clearance of the crankshaft 420 through the second oil suction channel 700 for lubrication. Then, it enters the central hole 422 of the crankshaft 420 through the oil channel 421, and then reaches the rotational mating between the crankshaft 420 and the housing 100 for lubrication. Finally, it flows back to the low-pressure chamber 111, realizing the circulation of lubricating oil between the low-pressure chamber 111 and the high-pressure chamber 112, and providing long-term reliable lubrication for the corresponding friction pairs.

[0047] In addition, since the high-pressure chamber 112 and the low-pressure chamber 111 are located on both sides of the first partition 200, when the compressor attitude changes, the lubricating oil in either the high-pressure chamber 112 or the low-pressure chamber 111 can smoothly enter the first oil suction channel 500. This solves the problem of insufficient oil level and oil supply to the moving parts caused by compressor vibration, changes in installation attitude, or changes in the gravitational acceleration of the usage scenario. It is suitable for scenarios such as automobiles, airplanes, high-speed trains, tanks, ships, flying cars, aerospace vehicles, satellites, space stations, and extraterrestrial space bases.

[0048] Specifically, the compression assembly 400 is used to compress gas and ultimately discharges the compressed gas at a set pressure to a set position through the exhaust silencer 113. The compression assembly 400 includes a motor 410, a crankshaft 420, and at least one compression unit 430. The motor 410 drives the crankshaft 420 to rotate, and the crankshaft 420 drives the compression unit 430 to compress the gas. The compression unit 430 can be single-stage or multi-stage. When it is single-stage, the gas is compressed using a single-stage compression unit 430. When it is multi-stage, the multi-stage compression units 430 can be connected in series or in parallel, without limitation.

[0049] An oil separator 300 is installed inside the exhaust muffler chamber 113. The compressed gas at the set pressure contains some lubricating oil mist. Under the action of the oil separator 300, the oil mist can be re-accumulated to form oil and enter the exhaust muffler chamber 113.

[0050] In some embodiments, the cross-sectional dimensions of the housing 100 can be set according to the size of its internal cavity. For example, the cross-sectional dimension of the housing 100 is larger at the location of the low-pressure cavity 111, and smaller at the location of the high-pressure cavity 112.

[0051] See Figures 1 to 4As shown, according to some embodiments of the present invention, the compression assembly 400 includes multiple compression units 430 connected in series. The compression chamber 434 of the front compression unit 430 is connected to the intake chamber 433 of the rear compression unit 430. The compression chamber 434 of the last stage is connected to the exhaust silencer chamber 113. A first oil suction channel 500 is provided between the intake chamber 433 of at least one compression unit 430 and the low-pressure chamber 111.

[0052] By configuring the compression assembly 400 as a multi-stage compression unit 430 connected in series, the gas can be compressed stage by stage to increase the gas pressure. Furthermore, a first oil suction channel 500 is provided between the intake chamber 433 of at least one compression unit 430 and the low-pressure chamber 111. During intake, the pressure difference allows lubricating oil in the low-pressure chamber 111 to be drawn into the first oil suction channel 500, causing most of the lubricating oil to flow back to the low-pressure chamber through the intake channel. A small portion of the lubricating oil flows sequentially through the intake chamber 433 and compression chamber 434 of each compression unit 430, finally entering the exhaust silencer chamber 113. Under the action of the oil separator 300, the oil in the oil-gas mixture is separated and returned to the high-pressure chamber 112 through the return oil channel 600, ensuring that the lubricating oil in the high-pressure chamber 112 remains within a preset range.

[0053] At this time, a first oil suction channel 500 can be provided between any one stage of the compression unit 430 and the low-pressure chamber 111, or a first oil suction channel 500 can be provided between any number of compression units 430 and the low-pressure chamber 111. When a first oil suction channel 500 is provided only between a single stage compression unit 430 and the low-pressure chamber 111, the lubricating oil in the low-pressure chamber 111 can be drawn into the compression assembly 400 when the compression unit 430 draws air, and some of the lubricating oil is stored in the high-pressure chamber 112 after lubricating the corresponding friction pairs. When a first oil suction channel 500 is provided between multiple stages of the compression unit 430 and the low-pressure chamber 111, the lubricating oil in the low-pressure chamber 111 can be drawn into the compression assembly 400 simultaneously when the multiple stages of the compression unit 430 draw air, and some of the lubricating oil is stored in the high-pressure chamber 112 after lubricating the corresponding friction pairs.

[0054] In addition, when the compression assembly 400 includes multiple compression units 430 connected in series, an exhaust chamber 435 can be provided downstream of the compression chamber 434 of at least one compression unit 430 to buffer and temporarily store the compressed gas.

[0055] See Figures 1 to 4As shown, as an example, in this embodiment, the compression assembly 400 includes two compression units 430 connected in series. In the two compression units 430, the first compression unit 430 located upstream is provided with a first oil suction channel 500 between it and the low-pressure chamber 111, the compression chamber 434 of the second compression unit 430 located downstream is connected to the exhaust silencer chamber 113, and an exhaust chamber 435 is provided downstream of the compression chamber 434 of the first compression unit 430.

[0056] According to some embodiments of the present invention, the compression assembly 400 includes multiple compression units 430 connected in parallel. The compression chamber 434 of each compression unit 430 is connected to the exhaust silencer chamber 113. A first oil suction channel 500 is provided between the intake chamber 433 of at least one compression unit 430 and the low-pressure chamber 111.

[0057] By configuring the compression assembly 400 as a multi-stage compression unit 430 connected in parallel, the gas can be compressed simultaneously using the multi-stage compression unit 430, thereby improving the gas compression efficiency of the compressor. Similarly, a first oil suction channel 500 is provided between the suction chamber 433 of at least one stage compression unit 430 and the low-pressure chamber 111. During suction, the pressure difference can be used to draw the lubricating oil in the low-pressure chamber 111 into the first oil suction channel 500, so that most of the lubricating oil flows back to the low-pressure chamber through the suction channel, and a small portion of the lubricating oil flows sequentially through the suction chamber 433 and compression chamber 434 of each stage compression unit 430, and finally enters the exhaust silencer chamber 113. Under the action of the oil separator 300, the oil in the oil-gas mixture is separated and flows back to the high-pressure chamber 112 through the oil return channel 600, ensuring that the lubricating oil in the high-pressure chamber 112 is within a preset range.

[0058] At this time, a first oil suction channel 500 can be provided between any level of compression unit 430 and the low-pressure chamber 111, or a first oil suction channel 500 can be provided between any number of compression units 430 and the low-pressure chamber 111. Similarly, when a first oil suction channel 500 is provided only between a single-stage compression unit 430 and the low-pressure chamber 111, the lubricating oil in the low-pressure chamber 111 can be drawn into the compression assembly 400 when the compression unit 430 draws air, and some of the lubricating oil is stored in the high-pressure chamber 112 after lubricating the corresponding friction pairs. When a first oil suction channel 500 is provided between multiple stages of compression units 430 and the low-pressure chamber 111, the lubricating oil in the low-pressure chamber 111 can be drawn into the compression assembly 400 simultaneously when the multiple stages of compression units 430 draw air, and some of the lubricating oil is stored in the high-pressure chamber 112 after lubricating the corresponding friction pairs.

[0059] Similarly, when the compression assembly 400 includes multiple compression units 430 connected in parallel, an exhaust chamber 435 can be provided downstream of the compression chamber 434 of at least one compression unit 430 to buffer and temporarily store the compressed gas.

[0060] See Figures 1 to 4 As shown, according to some embodiments of the present invention, the compression assembly 400 further includes a first crankshaft support 440 and a second crankshaft support 450. The first crankshaft support 440 and the second crankshaft support 450 are coaxial and spaced apart within the sealed cavity 110. One end of the crankshaft 420 is rotatably engaged with the housing 100, and the other end of the crankshaft 420 is rotatably engaged with the first crankshaft support 440 and the second crankshaft support 450. The multi-stage compression units 430 are all located between the first crankshaft support 440 and the second crankshaft support 450. A second partition 460 is provided between adjacent compression units 430, and the crankshaft 420 passes through the second partition 460. A first oil suction hole 510 is provided on the first partition 200, and a second oil suction hole 520 is provided on the first crankshaft support 440. The first oil suction hole 510 and the second oil suction hole 520 are connected to form a first oil suction channel 500.

[0061] By setting the first crankshaft support 440 and the second crankshaft support 450, the crankshaft 420 can be supported and fixed, ensuring its stable rotation under the drive of the motor 410. Each stage of the compression unit 430 is located between the first crankshaft support 440 and the second crankshaft support 450, which can improve the compactness of the compressor. The second partition 460 can effectively separate the compression units 430 and limit the cylinder of each stage of the compression unit 430. The first partition 200 is provided with a first oil suction hole 510, and the first crankshaft support 440 is provided with a second oil suction hole 520. During processing, the first oil suction hole 510 and the second oil suction hole 520 can be drilled in the first partition 200 and the first crankshaft support 440 respectively. During assembly, the outlet of the first oil suction hole 510 and the inlet of the second oil suction hole 520 are aligned and sealed, which facilitates the processing of the first oil suction channel 500.

[0062] Specifically, in this embodiment, the first crankshaft support 440 is located on the side where the first partition 200 is located, and the two are arranged adjacent to each other and fastened together by bolts. The inlet end of the first oil suction hole 510 is located at the bottom of the first partition 200 to meet the oil suction function when the lubricating oil level in the low-pressure chamber 111 is low.

[0063] In some embodiments, the first partition 200 and the first crankshaft support 440 may also be integrally formed to further improve the compactness of the compressor.

[0064] According to some embodiments of the present invention, at least one of the first crankshaft support 440, the second crankshaft support 450, and the second partition 460 is provided with a second oil suction channel 700.

[0065] By providing a second oil suction channel 700 in at least one of the first crankshaft support 440, the second crankshaft support 450, and the second partition 460, the lubricating oil in the high-pressure chamber 112 can be smoothly driven into the mating gap between the crankshaft 420 and the corresponding component by utilizing the intake and exhaust pressure difference, thereby satisfying the lubrication function when the crankshaft 420 rotates.

[0066] Specifically, the second oil suction channel 700 can be provided in any one of the first crankshaft support 440, the second crankshaft support 450, and the second partition 460, or the second oil suction channel 700 can be provided in at least two of the first crankshaft support 440, the second crankshaft support 450, and the second partition 460.

[0067] As an example, in this embodiment, the compression assembly 400 includes two-stage compression units 430 arranged in series. Both the first-stage compression unit 430 and the crankshaft 420 corresponding to the second-stage compression unit 430 are provided with oil passages 421. The first crankshaft support 440 is provided with a second oil suction passage 700. Under the action of suction and exhaust pressure, the lubricating oil in the high-pressure chamber 112 enters the mating gap between the crankshaft 420 and the first crankshaft support 440 through the second oil suction passage 700, then reaches the central hole 422 of the crankshaft 420 through the two oil passages 421, and finally returns to the low-pressure chamber 111 through the rotational connection between the crankshaft 420 and the housing 100.

[0068] According to some embodiments of the present invention, a second oil suction channel 700 is provided inside the first crankshaft support 440, and a first oil storage groove 441 is provided at the outlet of the second oil suction channel 700. The first oil storage groove 441 is connected to the oil passage 421. A second oil storage groove 461 is provided between the crankshaft 420 and the second partition 460, and the second oil storage groove 461 is connected to the oil passage 421.

[0069] By providing the first oil reservoir 441, lubricating oil can accumulate in the first oil reservoir 441 when it is discharged from the outlet end of the second oil suction channel 700, thus ensuring sufficient oil supply to the mating clearance between the crankshaft 420 and the corresponding components. By providing the second oil reservoir 461, the connecting channel volume of adjacent oil passages 421 can be increased, thereby increasing the flow speed of lubricating oil between the oil passages 421 and improving the lubrication effect of the crankshaft 420.

[0070] See Figures 7 to 8As shown, according to some embodiments of the present invention, the oil separator 300 includes a spiral separation tube, in which a spiral oil separation channel 310 is formed. The two ends of the spiral separation tube are respectively provided with an air inlet 320 and an exhaust outlet 330, both of which are connected to the oil separation channel 310. The air inlet 320 is connected to the compression chamber 434 located in the final stage, and the exhaust outlet 330 is configured to be connected to the exhaust pipe. An oil discharge structure 340 is provided on the outer side of the outer wall of the spiral separation tube, which is connected to the oil separation channel 310 and the exhaust silencer chamber 113.

[0071] It should be noted that the "outer side of the spiral separator wall" mentioned above can be found in [reference needed]. Figure 8 The direction indicated by the middle arrow.

[0072] By configuring the oil separator 300 as a spiral separation tube, during operation, compressed gas carrying tiny lubricating oil droplets enters the oil separation channel 310 through the air inlet 320. Under the centrifugal force of the spiral oil separation channel 310, the lubricating oil droplets can adhere to the inner and outer walls of the spiral separation tube. When they accumulate to a certain extent, the tiny lubricating oil droplets can form larger lubricating oil droplets, which are then discharged through the oil discharge structure 340 set on the outer wall of the spiral separation tube. This prevents the tiny lubricating oil droplets from entering the system with the compressed gas, resulting in good oil separation. Furthermore, the oil separator 300 separates oil and gas through the centrifugal force of the spiral separation tube, which can meet the oil and gas separation requirements under normal gravity and microgravity scenarios, thus solving the defect of poor oil separation effect of the existing oil separator 300 under normal gravity and microgravity scenarios.

[0073] Specifically, the spiral separator comprises multiple (two or more) spiral tube units connected in sequence. The inner diameter of the spiral separator can be adjusted according to specific application requirements. For example, the inner diameter of the spiral separator can be adjusted based on the compressor's discharge volume to optimize gas flow rate and separation effect. If the discharge volume is large, a larger inner diameter can be designed to avoid excessively rapid airflow and ensure sufficient time for oil droplets to be separated; if the discharge volume is small, the inner diameter can be appropriately reduced to increase the gas rotation speed, thereby enhancing centrifugal force and improving separation effect. The design parameters of the spiral separator can also be adjusted according to the compressor's discharge volume, flow rate, and oil-gas mixing degree. For example, adjusting the inner diameter of the spiral separator and the number of spiral tube units can ensure efficient oil-gas separation under various operating conditions.

[0074] The oil discharge structure 340 can take various forms, such as oil discharge holes, oil discharge grooves, or oil discharge perforations. Oil discharge holes consist of several (or more than one) holes on the outer side of the spiral separator tube, allowing the separated lubricating oil to flow along the inner wall of the tube and be smoothly discharged through the holes. Oil discharge grooves are similar to oil discharge holes, forming strip-shaped, square, or other groove-like structures on the outer side of the spiral tube. Oil discharge perforations, by hollowing out a portion of the outer wall of the spiral tube or forming a channel, allow oil to flow out through the gaps, reducing resistance to airflow and making them suitable for high oil discharge rates.

[0075] See Figure 7 and Figure 8 As shown in the illustration, the oil discharge structure 340 in this embodiment is an oil discharge hole, which has a simple structure and is easy to manufacture. The diameter of the oil discharge hole can be set according to actual needs. For example, the ratio of the diameter of the spiral separator tube to the diameter of the oil discharge hole can be set in the range of 2 to 20. The size of the hole diameter can be adjusted according to the compressor's discharge volume, the degree of oil-gas mixing, and the separation efficiency requirements. For applications with larger discharge volumes, the diameter of the oil discharge hole can be appropriately increased to ensure that the oil can be discharged smoothly and to avoid excessive oil accumulation that would affect the separation effect. For applications with smaller discharge volumes, the diameter of the oil discharge hole can be reduced to ensure that the oil discharge process does not affect the gas flow and to achieve the ideal oil-gas separation effect.

[0076] See Figure 7 and Figure 8 As shown, according to some embodiments of the present invention, the spiral separation tube includes multiple spiral tube units connected in sequence, all of which have the same structure to form a cylindrical spiral separation tube.

[0077] By connecting multiple helical tube units in series, a longer oil-gas separation path can be achieved, improving the oil-gas separation effect. Each helical tube unit, through its helical structural design, causes the oil-gas mixture to move in a spiral motion within the tube, enhancing the separation efficiency of oil and gas. Furthermore, since all helical tube units have the same structure, the manufacturing process can be simplified.

[0078] According to some embodiments of this utility model, the diameter of multiple spiral tube units gradually decreases along the axial direction of the spiral separation tube to form a conical spiral separation tube.

[0079] By setting the diameter of multiple spiral tube units to gradually decrease, the oil-gas separation process can be optimized, and the rotational motion of the airflow can be gradually accelerated, thereby improving the oil-gas separation efficiency.

[0080] Specifically, as the diameter of the spiral tube unit decreases, the airflow speed gradually increases, and the separation effect of oil in the airflow is enhanced. Especially at higher speeds, the separation of oil and gas is more thorough.

[0081] It should be noted that the number of spiral tube units can be set according to actual needs. By increasing or decreasing the number of spiral tube units without affecting the exhaust, 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; conversely, if the exhaust volume is small, the number of spiral tube units can be reduced to ensure smooth airflow and stable separation effect.

[0082] See Figure 7 and Figure 8 As shown, according to some embodiments of the present invention, each spiral tube unit has an oil drain structure 340 at the bottom of the outer side of its outer wall.

[0083] By installing an oil drain structure 340 at the bottom outer side of each spiral tube unit, the accumulated oil in each spiral tube unit can be effectively drained in a timely manner, preventing oil from accumulating in the separation tube and thus affecting the oil-gas separation effect. Placing the oil drain structure 340 at the bottom allows the oil to flow naturally to the oil drain structure 340 by its own gravity, thereby achieving automatic oil discharge.

[0084] It should be noted that the "outer bottom of the spiral tube unit" mentioned above specifically refers to the lowest position of the outer wall of the spiral tube unit after the oil separator 300 is installed in the compressor.

[0085] According to some embodiments of the present invention, the outer side of the inner wall of the oil separation channel 310 is provided with an oleophilic structure 350, and the inner side of the inner wall of the oil separation channel 310 is provided with an oleophobic structure 360.

[0086] By providing an oleophilic structure 350 on the outer side of the inner wall of the oil separation channel 310 and an oleophobic structure 360 ​​on the inner side of the inner wall of the oil separation channel 310, the oil can be effectively guided to the outer side of the channel, while reducing the adhesion of oil on the inner side of the inner wall and reducing the impact of the wall surface on the exhaust effect.

[0087] Specifically, the oleophilic structure 350 on the outside attracts and retains the oil, causing it to move towards the exhaust structure, while the oleophobic structure 360 ​​effectively reduces the adhesion of oil on the inner wall, allowing the airflow to pass more smoothly through the oil separation channel 310 and preventing secondary adhesion and accumulation of oil.

[0088] The oleophilic structure 350 can be an oleophilic layer or an oleophilic micro / nano protrusion structure, etc. The oleophobic structure 360 ​​can be an oleophobic layer or an oleophobic micro / nano protrusion structure, etc.

[0089] As an example, in this embodiment, the oleophilic structure 350 is an oleophilic layer, and the oleophobic structure 360 ​​is an oleophobic layer. The oleophilic structure 350 and the oleophobic structure 360 ​​can be prepared by electroplating, chemical plating, or other methods. For example, when processing the oleophilic structure 350, the portion of the spiral separation tube corresponding to the oleophobic structure 360 ​​can be physically shielded. After the oleophilic structure 350 is processed, the portion of the spiral separation tube corresponding to the oleophilic structure 350 can be physically shielded to process the oleophobic structure 360. After the oleophilic structure 350 and the oleophobic structure 360 ​​are processed, the tube can be bent into a spiral shape.

[0090] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of this utility model, and not to limit it. Although this utility model has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some of the technical features. Such modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the spirit and scope of the technical solutions of the embodiments of this utility model.

Claims

1. A dual circuit differential pressure pump oil compressor characterized by, include: A housing having a sealed cavity formed within it; A first partition is located within the sealed cavity and divides the sealed cavity into a low-pressure cavity and a high-pressure cavity. An exhaust silencing chamber is provided within the high-pressure cavity. An oil separator, wherein the oil separator is located within the exhaust muffler chamber; A compression assembly, comprising a motor, a crankshaft, and at least one compression unit, wherein both ends of the crankshaft are rotatably engaged with the housing, and the motor is drively connected to the crankshaft; The compression unit includes a cylinder and a rotary piston. The rotary piston is located on the crankshaft. An intake chamber and a compression chamber are provided between the cylinder and the corresponding rotary piston. The intake chamber is connected to the corresponding compression chamber. A first oil suction channel is provided between the intake chamber and the low-pressure chamber. The compression chamber is connected to the oil separator. An oil return channel is provided between the exhaust muffler chamber and the high-pressure chamber. The crankshaft is provided with oil passages that correspond one-to-one with the compression unit. The crankshaft is provided with a central hole. The oil passages are connected to the first end of the central hole. The second end of the central hole is connected to the rotational engagement of the crankshaft and the housing and the low-pressure cavity in sequence. A second oil suction channel is provided between the high-pressure cavity and the oil passages.

2. The dual circuit differential pressure pump oil compressor of claim 1, wherein, The compression assembly includes multiple compression units connected in series. The compression chamber of the first compression unit is connected to the intake chamber of the next compression unit. The compression chamber of the last compression unit is connected to the exhaust silencer chamber. The first oil suction channel is provided between the intake chamber of at least one compression unit and the low-pressure chamber. Alternatively, the compression assembly may include multiple compression units connected in parallel, with the compression chamber of each compression unit communicating with the exhaust silencer chamber, and the first oil suction channel being provided between the intake chamber of at least one compression unit and the low-pressure chamber.

3. The dual circuit differential pressure pump oil compressor of claim 2, wherein, The compression assembly further includes 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 crankshaft is rotatably engaged with the housing, and the other end of the crankshaft is rotatably engaged with the first crankshaft support and the second crankshaft support. The multiple compression units are all located between the first crankshaft support and the second crankshaft support. A second partition is provided between adjacent compression units, and the crankshaft passes through the second partition. The first partition plate is provided with a first oil suction hole, and the first crankshaft support is provided with a second oil suction hole. The first oil suction hole and the second oil suction hole are connected to form the first oil suction channel.

4. The dual circuit differential pressure pump oil compressor of claim 3, wherein, At least one of the first crankshaft support, the second crankshaft support, and the second partition is provided with the second oil suction channel.

5. The dual circuit differential pressure pump oil compressor of claim 4, wherein, The first crankshaft support is provided with a second oil suction channel, and the first crankshaft support is provided with a first oil storage groove at the outlet of the second oil suction channel, and the first oil storage groove is connected to the oil passage.

6. The dual circuit differential pressure pump oil compressor of claim 3, wherein, A second oil storage groove is provided between the crankshaft and the second partition plate, and the second oil storage groove is connected to the oil passage.

7. The dual circuit differential pressure pump oil compressor of claim 3, wherein, The first partition is integrally arranged with the first crank supporting piece.

8. The dual circuit differential pressure pump oil compressor according to any one of claims 1 to 7, characterized in that, The oil separator comprises a spiral separation tube, a spiral oil separation channel is formed in the spiral separation tube, and an air inlet and an air outlet are respectively arranged at two ends of the spiral separation tube, the air inlet and the air outlet are communicated with the oil separation channel; The air inlet is communicated with the compression chamber at the last stage, the air outlet is configured to be connected with an exhaust pipe, an oil discharge structure is arranged on the outside of the outer wall of the spiral separation tube, the oil discharge structure is communicated with the oil separation channel, and the oil discharge structure is communicated with the exhaust silencing cavity.

9. The dual circuit differential pressure pump oil compressor of claim 8, wherein, The spiral separation tube comprises a plurality of spiral tube units connected in sequence, all the spiral tube units are of the same structure, a cylindrical spiral separation tube is formed, or the diameters of the plurality of spiral tube units gradually decrease along the axial direction of the spiral separation tube, and a conical spiral separation tube is formed.

10. The dual circuit differential pressure pump oil compressor of claim 9, wherein, The oil discharge structure is arranged on the outside of the bottom of the outer wall of each spiral tube unit, an oleophilic structure is arranged on the outside of the inner wall of the oil separation channel, and an oleophobic structure is arranged on the inside of the inner wall of the oil separation channel.

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