Compressor

Abstract

The utility model relates to a compressor which comprises a shell, a partition plate and a differential pressure jet oil pumping structure. A sealed cavity is formed in the shell; the partition plate divides the sealing cavity into a low-pressure cavity and a high-pressure cavity; the differential pressure injection oil pumping structure comprises a body, an oil pumping channel is formed in the body and 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 communicated with the nozzle, and the nozzle, the contraction channel, the mixing channel and the expansion channel are sequentially communicated; the high-pressure injection oil inlet is communicated with the high-pressure cavity, the low-pressure injected oil inlet is communicated with the low-pressure cavity, and the expansion channel is communicated with a kinematic pair of the compressor. The compressor solves the problems that lubricating oil supply of an existing compressor cannot be effectively guaranteed under the conditions of low rotating speed, low oil level, vibration and jolting, mounting posture change and changeable gravity, and consequently the compressor is insufficient in lubrication, low in efficiency and unstable in system.

Description

Technical Field

[0001] This utility model relates to the field of compressor technology, and in particular to a compressor. Background Technology

[0002] Existing rotary compressors supply oil by rotating a crankshaft to drive oil pump blades or a spiral pump body, primarily relying on the high-speed rotation of the crankshaft to drive the flow of lubricating oil. However, this method results in a small oil pump pressure differential and poor self-priming capability, especially at low speeds or low oil levels, which can easily lead to insufficient oil supply. Linear compressors, on the other hand, drive the oil pump through machine vibration, but they also face the problems of difficult starting and poor self-priming capability.

[0003] Furthermore, for compressors operating in environments with variable installation postures and microgravity (such as automobiles, airplanes, high-speed trains, and aircraft), traditional oil pump methods (relying on gravity, centrifugal force, capillary force, etc.) cannot effectively guarantee the lubrication of moving parts and efficient oil sealing, thus affecting the compressor's service life and operating efficiency. In these scenarios, compressor vibration, changes in installation posture, or alterations in gravitational acceleration can lead to unstable lubricant supply, affecting its normal operation. Utility Model Content

[0004] This invention provides a compressor to solve the defects of existing compressors that cannot effectively guarantee the supply of lubricating oil under low speed, low oil level and variable gravity scenarios, resulting in insufficient lubrication, low efficiency and system instability.

[0005] This utility model provides a compressor, including: a housing, a partition plate, and a differential pressure ejector pump oil structure.

[0006] A sealed cavity is formed within the housing; a partition plate is located within the sealed cavity and divides the sealed cavity into a low-pressure cavity and a high-pressure cavity; a differential pressure ejector pump structure is located within the sealed cavity, the differential pressure ejector pump structure includes a body, and an oil pumping channel is formed within the body. The oil pumping channel includes a high-pressure ejector oil inlet, a low-pressure ejected oil inlet, a nozzle, a contraction channel, a mixing channel, and an expansion channel. The high-pressure ejector oil inlet and the low-pressure ejected oil inlet are both connected to the nozzle, and the nozzle, the contraction channel, the mixing channel, and the expansion channel are connected sequentially; the high-pressure ejector oil inlet is connected to the high-pressure cavity, the low-pressure ejected oil inlet is connected to the low-pressure cavity, and the expansion channel is connected to the moving part of the compressor.

[0007] The compressor provided by this utility model further includes a first oil inlet pipe, one end of which is connected to the low-pressure chamber, and the other end of which is connected to the low-pressure ejected oil inlet; and / or, it further includes a second oil inlet pipe, one end of which is connected to the high-pressure chamber, and the other end of which is connected to the high-pressure ejected oil inlet.

[0008] According to the compressor provided by this utility model, both the first oil inlet pipe and the second oil inlet pipe are flexible oil inlet pipes.

[0009] According to the compressor provided by this utility model, 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 drivenly connected to the piston, the piston and the cylinder are axially slidingly engaged, and the expansion channel is connected to the engagement gap between the piston and the cylinder.

[0010] According to the compressor provided by this utility model, the compressor is a rotary compressor; it also includes 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 coaxial and spaced apart in the sealed cavity. One end of the first crankshaft is rotatably engaged with the housing, and the other end of the first crankshaft is rotatably engaged with the first crankshaft support and the second crankshaft support. The first rotary motor is drively connected to the first crankshaft, and the expansion channel communicates with the first crankshaft and the mating gap of the first crankshaft support and the second crankshaft support.

[0011] According to the compressor provided by this utility model, a first shaft segment and a second shaft segment are provided at intervals on the first crankshaft. A first oil passage is provided on the outer wall of the first shaft segment along the length direction, and a second oil passage is provided on the outer wall of the second shaft segment along the length direction. Both the first oil passage and the second oil passage are connected to the expansion channel. The first oil passage and the second oil passage are located opposite to each other on the first crankshaft.

[0012] According to the compressor provided by this utility model, the main body and the partition plate are integrally arranged; or, the main body and the first crankshaft support are integrally arranged; or, the main body and the second crankshaft support are integrally arranged.

[0013] According to the compressor provided by this utility model, the compressor is a scroll compressor; it also includes a second rotary 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 disposed in the sealed cavity. One end of the second crankshaft is rotatably engaged with the housing, and the other end of the second crankshaft is rotatably engaged with the third crankshaft support and connected to the scroll moving disk. The expansion channel is connected to the fit clearance between the second crankshaft and the third crankshaft support, as well as the fit clearance between the scroll moving disk and the scroll stationary disk.

[0014] According to the compressor provided by this utility model, the partition plate is integrally formed with the scroll stationary disk, and the body is integrally formed with the scroll stationary disk.

[0015] According to the compressor provided by this utility model, the compressor is a screw compressor or a centrifugal compressor.

[0016] The compressor provided by this utility model, by setting a partition plate and an ejector oil pump structure inside the housing, can divide the sealed cavity formed inside the housing into a low-pressure cavity and a high-pressure cavity. The high-pressure ejector oil inlet of the ejector oil pump structure is connected to the high-pressure cavity, and the low-pressure ejected oil inlet is connected to the low-pressure cavity. When the compressor is working, the lubricating oil (ejector flow) in the high-pressure cavity enters the nozzle of the pump oil channel through the high-pressure ejector oil inlet. Under the action of the nozzle, the lubricating oil flow rate increases, and a low-pressure zone is formed at the low-pressure ejected oil inlet. The lubricating oil (ejected flow) in the low-pressure cavity is drawn into the pump oil channel. The lubricating oil mixture formed by mixing gradually expands and fills the entire mixing channel. After a period of mixing, the lubricating oil mixture becomes a uniform flow at the outlet of the mixing channel. Then, under the action of the expansion channel, the uniform flow velocity decreases and the static pressure increases, which can enter the moving parts of the compressor for lubrication. It has a large pump oil pressure difference and strong self-priming ability, which effectively solves the problem of insufficient oil supply in existing compressors at low speed, low vibration or low oil level. In addition, since the high-pressure chamber and the low-pressure chamber are located on both sides of the partition plate, when the compressor attitude changes, the lubricating oil in either the high-pressure chamber or the low-pressure chamber can smoothly enter the ejector pump oil structure. 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.

[0017] 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

[0018] 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.

[0019] Figure 1 This is a schematic diagram of the differential pressure ejector pump oil structure in the compressor provided in this embodiment of the utility model.

[0020] Figure 2 This is a schematic diagram of a compressor provided in one embodiment of the present utility model.

[0021] Figure 3 This is a schematic diagram of the compressor provided in the second embodiment of this utility model.

[0022] Figure 4 yes Figure 3 A magnified view of part A in the diagram.

[0023] Figure 5 This is one of the schematic diagrams of the first crankshaft in the compressor provided in the second embodiment of this utility model.

[0024] Figure 6 This is the second schematic diagram of the first crankshaft in the compressor provided in the second embodiment of this utility model.

[0025] Figure 7 This is a schematic diagram of the compressor provided in the third embodiment of this utility model.

[0026] Figure 8 yes Figure 7 A magnified view of part B in the diagram.

[0027] Figure label:

[0028] 10. Housing; 110. Sealed cavity; 111. Low-pressure cavity; 112. High-pressure cavity; 113. Exhaust silencer cavity; 120. Oil separator; 20. Divider plate; 30. Differential pressure ejector pump oil structure; 310. Body; 320. Pump oil passage; 321. High-pressure ejector oil inlet; 322. Low-pressure ejected oil inlet; 323. Nozzle; 324. Contraction channel; 325. Mixing channel; 326. Expansion channel; 40. Linear compressor; 410. Linear motor; 420. Piston; 430. Cylinder; 440. First oil storage tank; 50. Rotation. Sub-compressor; 510, First rotary 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 reservoir; 60, Second oil reservoir; 60, Scroll compressor; 610, Second rotary motor; 620, Second crankshaft; 630, Third crankshaft support; 640, Scroll moving plate; 650, Scroll stationary plate; 660, Third oil reservoir; 670, Second bearing. Detailed Implementation

[0029] 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.

[0030] 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.

[0031] 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.

[0032] 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.

[0033] 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.

[0034] The following is combined Figures 1 to 8 This invention describes the compressor provided by this utility model.

[0035] See Figures 1 to 8 As shown, the compressor provided in this embodiment of the present invention includes: a housing 10, a partition plate 20, and a differential pressure ejector pump oil structure 30.

[0036] A sealed cavity 110 is formed within the housing 10; a partition plate 20 is located within the sealed cavity 110 and divides the sealed cavity 110 into a low-pressure cavity 111 and a high-pressure cavity 112; a differential pressure ejector pump oil structure 30 is located within the sealed cavity 110, and the differential pressure ejector pump oil structure 30 includes a body 310, within which a pump oil passage 320 is formed, and the pump oil passage 320 includes a high-pressure ejector oil inlet 321, a low-pressure ejected oil inlet 322, and a nozzle 32. 3. The contraction channel 324, the mixing channel 325, and the expansion channel 326, the high-pressure ejector oil inlet 321, and the low-pressure ejected oil inlet 322 are all connected to the nozzle 323. The nozzle 323, the contraction channel 324, the mixing channel 325, and the expansion channel 326 are connected in sequence. The high-pressure ejector oil inlet 321 is connected to the high-pressure chamber 112, the low-pressure ejected oil inlet 322 is connected to the low-pressure chamber 111, and the expansion channel 326 is connected to the moving part of the compressor.

[0037] The compressor provided by this utility model, by setting a partition plate 20 and an ejector oil pump structure inside the housing 10, allows the partition plate 20 to divide the sealed cavity 110 formed inside the housing 10 into a low-pressure cavity 111 and a high-pressure cavity 112. The high-pressure ejector oil inlet 321 of the ejector oil pump structure is connected to the high-pressure cavity 112, and the low-pressure ejector oil inlet 322 is connected to the low-pressure cavity 111. When the compressor is working, the lubricating oil (ejector flow) in the high-pressure cavity 112 enters the nozzle 323 of the oil pump channel 320 through the high-pressure ejector oil inlet 321. Under the action of the nozzle 323, the lubricating oil flow rate increases, and... A low-pressure zone is formed at the low-pressure ejected oil inlet 322, drawing the lubricating oil (ejected flow) in the low-pressure chamber 111 into the pump oil passage 320. The lubricating oil mixture formed by mixing gradually expands and fills the entire mixing passage 325. After a period of mixing, the lubricating oil mixture becomes a uniform flow at the outlet of the mixing passage 325. Then, under the action of the expansion passage 326, the uniform flow velocity decreases and the static pressure increases, enabling it to enter the moving parts of the compressor for lubrication. It has a large pump oil pressure difference and strong self-priming ability, effectively solving the problem of insufficient oil supply in existing compressors at low speed, low vibration, or low oil level.

[0038] Furthermore, since the low-pressure chamber 111 and the high-pressure chamber 112 are located on both sides of the partition plate 20, when the compressor's attitude changes, the lubricating oil in either the low-pressure chamber 111 or the high-pressure chamber 112 can smoothly enter the ejector pump oil structure. This solves the problem of insufficient oil level and oil supply to moving parts caused by compressor vibration, changes in installation attitude, or changes in the gravitational acceleration of the usage scenario. It is suitable for applications such as automobiles, airplanes, high-speed trains, tanks, ships, flying cars, spacecraft, satellites, space stations, and extraterrestrial bases. Figure 2As an example, when the compressor is tilted in the front-to-back direction, the lubricating oil in either the low-pressure chamber 111 or the high-pressure chamber 112 can smoothly enter the ejector pump oil structure.

[0039] In some embodiments, the cross-sectional dimensions of the housing 10 can be set according to the size of its internal cavity. For example, the cross-sectional dimension of the housing 10 is larger at the location of the low-pressure cavity 111, and smaller at the location of the high-pressure cavity 112.

[0040] 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 chamber 111, and the other end of the first oil inlet pipe is connected to the low-pressure ejected oil inlet 322. One end of the second oil inlet pipe is connected to the high-pressure chamber 112, and the other end of the second oil inlet pipe is connected to the high-pressure ejected oil inlet 321.

[0041] By setting up a first oil inlet pipe and a second oil inlet pipe, the low-pressure ejected oil inlet 322 and the high-pressure ejected oil inlet 321 can be connected to the lubricating oil accumulation positions (such as the bottom of the cavity) in the low-pressure cavity 111 and the high-pressure cavity 112 respectively, thereby optimizing the oil pumping effect of the ejector pump structure and ensuring sufficient lubricating oil supply for the compressor during large-scale attitude changes.

[0042] Of course, in some embodiments, a first oil inlet pipe or a second oil inlet pipe may be provided separately to meet the spatial layout or other practical needs within the sealed cavity 110.

[0043] 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.

[0044] By setting both the first and second oil inlet pipes as flexible oil inlet pipes, during operation, the first and second oil inlet pipes 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 when the attitude changes significantly.

[0045] Specifically, the first and second oil inlet pipes can be made of weather-resistant rubber materials, such as fluororubber (FKM) or ethylene propylene diene monomer (EPDM). These materials have excellent high-temperature resistance, chemical corrosion resistance, and weather resistance, and can maintain stable performance in harsh working environments, effectively improving the reliability and service life of the equipment.

[0046] The following describes three specific embodiments of the compressor provided by this utility model: a linear compressor 40, a rotary compressor 50, and a scroll compressor 60.

[0047] See Figure 2 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 connected to the piston 420 in a driving connection, the piston 420 and the cylinder 430 are slidably fitted along the axial direction, and the expansion channel 326 is connected to the fitting gap between the piston 420 and the cylinder 430.

[0048] When the linear compressor 40 is working, the linear motor 410 drives the piston 420 to slide axially within the cylinder 430, completing the process of gas intake, compression, and discharge. The compressed gas is discharged through the exhaust channel. During this process, the lubricating oil in the high-pressure chamber 112 enters the differential pressure ejector pump oil structure 30 through the high-pressure ejector oil inlet 321. At the same time, the lubricating oil in the low-pressure chamber 111 enters the differential pressure ejector pump oil structure 30 through the low-pressure ejector oil inlet 322 under the action of negative pressure. Driven by the high-pressure lubricating oil, it sequentially passes through the contraction channel 324, the mixing channel 325, and the expansion channel 326 to form a mixed lubricating oil fluid with sufficient pressure. This fluid then enters the moving pair (the mating clearance between the piston 420 and the cylinder 430) of the linear compressor 40, thereby achieving lubrication.

[0049] See Figure 2 As shown, during the lubrication process, part of the lubricating oil returns to the low-pressure chamber 111 through the clearance between the piston 420 and the cylinder 430, while another part of the lubricating oil passes through the clearance between the piston 420 and the cylinder 430, follows the compressed gas into the exhaust muffler chamber 113, and returns to the high-pressure chamber 112 under the action of the oil separator 120. For details, please refer to... Figure 2 The direction indicated by the middle arrow.

[0050] In addition, a first oil reservoir 440 can be provided at the position of the expansion channel 326 corresponding to the mating clearance between the piston 420 and the cylinder 430. When the lubricating oil is discharged through the expansion channel 326, it can be stored in the first oil reservoir 440 to achieve sufficient oil supply to the mating clearance between the piston 420 and the cylinder 430.

[0051] When the compressor is a linear compressor 40, the differential pressure ejector pump oil structure 30 can be set as an independent component in the sealed cavity 110, or the differential pressure ejector pump oil structure 30 (body 310) can be integrated with the partition plate 20 or the cylinder to reduce its space occupation in the sealed cavity 110 and improve the compactness of the compressor.

[0052] See Figure 2 As shown, as an example, in this embodiment, the differential pressure ejector pump oil structure 30 (body 310) is integrated with the cylinder 430.

[0053] See Figures 3 to 6As shown, according to some embodiments of the present invention, the compressor is a rotary compressor 50; it also 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 coaxial 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 drive-connected to the first crankshaft 520, and the expansion channel 326 is connected to the mating gap of the first crankshaft 520, the first crankshaft support 530 and the second crankshaft support 540.

[0054] When the rotary compressor 50 is working, the first rotary motor 510 drives the first crankshaft 520 to rotate, which in turn drives the rotor to perform compression work within the sealed cavity 110. The first rotary motor 510 drives the first crankshaft 520 to rotate through a transmission 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 chamber 112 enters the differential pressure ejector pump oil structure 30 through the high-pressure ejector oil inlet 321, while the lubricating oil in the low-pressure chamber 111 enters the differential pressure ejector pump oil structure 30 through the low-pressure ejector oil inlet 322 under the action of negative pressure. Driven by the high-pressure lubricating oil, the lubricating oil flows through the contraction channel 324, the mixing channel 325 and the expansion channel 326 in sequence to form a mixed lubricating oil fluid with sufficient pressure. This fluid then enters the kinematic pair of the rotor compressor 50 (the fit clearance between the first crankshaft 520 and the first crankshaft support 530 and the second crankshaft support 540), thereby achieving lubrication.

[0055] See Figure 3 and Figure 4 As shown, during the lubrication process, part of the lubricating oil returns to the low-pressure chamber 111 through the clearance between the first crankshaft 520 and the first crankshaft support 530, while another part of the lubricating oil follows the compressed gas into the exhaust muffler chamber 113 through the clearance between the first crankshaft 520, the first crankshaft support 530, and the second crankshaft support 540. Under the action of the oil separator 120, it returns to the high-pressure chamber 112. Simultaneously, the first crankshaft 520 has a first oil return channel, through which part of the lubricating oil can return to the rotational fit position between the first crankshaft 520 and the inner wall of the housing 10 (the first bearing 550), where it is lubricated, before returning to the low-pressure chamber 111. For details, please refer to [link to relevant documentation]. Figure 3 and Figure 4 The direction indicated by the middle arrow.

[0056] In addition, a second oil reservoir 560 can be provided at the position of the expansion channel 326 corresponding to the fit clearance between the first crankshaft 520 and the first crankshaft support 530 or the second crankshaft support 540. When the lubricating oil is discharged through the expansion channel 326, it can be stored in the second oil reservoir 560 to achieve sufficient oil supply to the fit clearance between the first crankshaft 520 and the first crankshaft support 530 or the second crankshaft support 540.

[0057] See Figure 3 and Figure 4 As shown in the figure, as an example, in this embodiment, the first crankshaft 520 and the first crankshaft support 530 are provided with a second oil storage groove 560 at the position corresponding to the expansion channel 326.

[0058] See Figures 3 to 6 As shown, according to some embodiments of the present invention, a first crankshaft 520 is provided with a first shaft segment 521 and a second shaft segment 522 at intervals. The outer wall of the first shaft segment 521 is provided with a first oil passage 5211 along the length direction, and the outer wall of the second shaft segment 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 connected to the expansion channel 326.

[0059] By setting a first shaft section 521 and a second shaft section 522 on the crankshaft, and opening a first oil passage 5211 and a second oil passage 5221 on the first shaft section 521 and the second shaft section 522 respectively, the lubricating oil at the mating 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 chamber 112 and the low-pressure chamber 111 through the first oil passage 5211 and the second oil passage 5221.

[0060] See Figures 3 to 6 As shown, according to some embodiments of the present invention, the first oil passage 5211 and the second oil passage 5221 are disposed opposite to each other on the first crankshaft 520.

[0061] By arranging the first oil passage 5211 and the second oil passage 5221 opposite to each other on the first crankshaft 520, the flow path of lubricating oil can be increased, so that the mating clearance between the first crankshaft 520 and the first crankshaft support 530 and the second crankshaft support 540, as well as the mating clearance between the first crankshaft 520 and the rotating piston, is filled with lubricating oil, which fully lubricates the friction pair mating with the first crankshaft 520. The accumulated lubricating oil ensures reliable lubrication when the compressor starts up and the suction and exhaust pressure difference has not yet been established.

[0062] Specifically, "the first oil passage 5211 and the second oil passage 5221 are located opposite to each other on the first crankshaft 520" means that the included angle between the first oil passage 5211 and the second oil passage 5221 is 180°, and the two are located on opposite sides of the first crankshaft 520.

[0063] See Figure 3 and Figure 4 As shown, according to some embodiments of the present invention, when the compressor is a rotary compressor 50, the differential pressure ejector pump oil structure 30 can be set as an independent component in the sealed cavity 110, or the differential pressure ejector pump oil structure 30 (body 310) can be integrated with the partition plate 20, the first crankshaft support 530 or the second crankshaft support 540 to reduce its space occupation in the sealed cavity 110 and improve the compactness of the compressor.

[0064] See Figure 3 and Figure 4 As shown in the figure, as an example, the differential pressure ejector pump oil structure 30 (body 310) in this embodiment is integrally formed with the first crankshaft support 530, and the partition plate 20 is adjacent to the first crankshaft support 530. The partition plate 20 is provided with an oil passage for connecting the low-pressure chamber 111 and the low-pressure ejected oil inlet 322.

[0065] In some embodiments, the partition plate 20 may be integrally disposed with the first crankshaft support 530 or the second crankshaft support 540 to reduce the space occupied by the partition plate 20 on the sealing cavity 110 and improve the compactness of the compressor.

[0066] See Figure 7 and Figure 8 As shown, according to some embodiments of the present invention, the compressor is a scroll compressor 60; it also includes a second rotary motor 610, a second crankshaft 620, a third crankshaft support 630, a scroll moving disk 640, and a scroll stationary disk 650. The third crankshaft support 630, the scroll moving disk 640, and the scroll stationary disk 650 are all disposed in the sealed cavity 110. One end of the second crankshaft 620 is rotatably engaged with the housing 10, and the other end of the second crankshaft 620 is rotatably engaged with the third crankshaft support 630 and connected to the scroll moving disk 640. The expansion channel 326 is connected to the fit clearance between the second crankshaft 620 and the third crankshaft support 630, as well as the fit clearance between the scroll moving disk 640 and the scroll stationary disk 650.

[0067] When the scroll compressor 60 is working, the second rotary motor 610 drives the second crankshaft 620 to rotate, which in turn drives the scroll moving disk 640 to move relative to the scroll stationary disk 650 within the sealed cavity 110, completing the gas compression process. One end of the second crankshaft 620 is rotatably engaged with the housing 10, and the other end is rotatably engaged 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, forming multiple compression chambers, within which the gas is gradually compressed. During this process, the lubricating oil in the high-pressure chamber 112 enters the differential pressure ejector pump oil structure 30 through the high-pressure ejector oil inlet 321, while the lubricating oil in the low-pressure chamber 111 enters the differential pressure ejector pump oil structure 30 through the low-pressure ejector oil inlet 322 under the action of negative pressure. Driven by the high-pressure lubricating oil, the lubricating oil flows sequentially through the contraction channel 324, the mixing channel 325, and the expansion channel 326 to form a mixed lubricating oil fluid with sufficient pressure. This fluid then enters the kinematic pairs of the scroll compressor 60 (the fit clearance between the second crankshaft 620 and the third crankshaft support 630, and the fit clearance between the scroll moving plate 640 and the scroll stationary plate 650), thereby achieving lubrication.

[0068] See Figure 7 and Figure 8 As shown, during the lubrication process, lubricating oil enters the mating gap between the scroll moving plate 640 and the scroll stationary plate 650 through the expansion channel 326. Then, part of the lubricating oil enters the mating gap between the second crankshaft 620 and the third crankshaft support 630 and returns to the low-pressure chamber 111. Another part of the lubricating oil follows the compressed gas into the exhaust muffler chamber 113, and finally returns to the high-pressure chamber 112 under the action of the oil separator 120. For details, please refer to [link to relevant documentation]. Figure 7 and Figure 8 The arrows in the image indicate the direction.

[0069] In some embodiments, an oil return channel can be provided between the scroll moving plate 640 and the scroll stationary plate 650 to guide the lubricating oil through the oil return channel to the compressed air chamber, and then into the exhaust silencer chamber 113, and finally return to the high pressure chamber 112 under the action of the oil separator 120.

[0070] In some embodiments, an oil return channel can be provided within the second crankshaft 620, communicating with the clearance between the second crankshaft 620 and the third crankshaft support 630. After reaching the clearance between the second crankshaft 620 and the third crankshaft support 630, the lubricating oil can enter the oil return channel and reach the rotational engagement position (second bearing 670) between the second crankshaft 620 and the housing 10 for lubrication. The lubricating oil can then return to the low-pressure chamber 111. Additionally, a third oil storage groove 660 can be provided at the location where the oil return channel communicates with the clearance between the second crankshaft 620 and the third crankshaft support 630 to temporarily store the lubricating oil.

[0071] See Figure 7 and Figure 8 As shown, according to some embodiments of the present invention, the partition plate 20 is integrally formed with the vortex stationary disk 650, and the body 310 is integrally formed with the vortex stationary disk 650.

[0072] By integrating the partition plate 20 with the scroll stationary plate 650 and the main body 310 with the scroll stationary plate 650, the space occupied by the partition plate 20 and the differential pressure ejector pump oil structure 30 within the sealed cavity 110 can be reduced, thereby improving the compactness of the compressor. At this time, both the third crankshaft support 630 and the scroll moving plate 640 are provided with oil passages for connecting the low-pressure cavity 111 and the low-pressure ejected oil inlet 322.

[0073] According to some embodiments of this utility model, the compressor can also be a screw compressor or a centrifugal compressor (with a pump body installed).

[0074] As described above, the compressor provided by this invention can be a linear compressor 40, a rotary compressor 50, a scroll compressor 60, a screw compressor, or a centrifugal compressor. The differential pressure ejector pump oil structure 30, when applied to different types of compressors, can achieve large differential pressure pumping and possesses strong self-priming capability, effectively solving the problem of insufficient oil supply in existing compressors at low speeds, low vibrations, or low oil levels. Furthermore, since the high-pressure chamber 112 and the low-pressure chamber 111 are located on both sides of the partition plate 20, when the compressor's attitude changes, the lubricating oil in either the high-pressure chamber 112 or the low-pressure chamber 111 can smoothly enter the ejector pump oil structure. This solves the problem of insufficient oil level and oil supply at moving parts caused by changes in the compressor's installation attitude or the gravitational acceleration of the usage scenario. It is suitable for scenarios such as automobiles, airplanes, high-speed trains, tanks, ships, flying cars, spacecraft, satellites, space stations, and extraterrestrial bases.

[0075] 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 compressor characterized by, The application relates to a compressor, which comprises a shell, a sealed cavity formed in the shell, a partition plate located in the sealed cavity and separating the sealed cavity into a low-pressure cavity and a high-pressure cavity, a differential pressure ejector pump oil structure located in the sealed cavity, the differential pressure ejector pump oil structure comprising a body, a pump oil channel formed in the body, the pump oil channel comprising a high-pressure ejector oil inlet, a low-pressure ejector oil inlet, a nozzle, a contraction channel, a mixing channel and an expansion channel, the high-pressure ejector oil inlet and the low-pressure ejector oil inlet being communicated with the nozzle, the nozzle, the contraction channel, the mixing channel and the expansion channel being communicated in sequence, the high-pressure ejector oil inlet being communicated with the high-pressure cavity, the low-pressure ejector oil inlet being communicated with the low-pressure cavity, and the expansion channel being communicated with a moving pair of the compressor. The application further comprises a first oil inlet pipe, one end of the first oil inlet pipe being communicated with the low-pressure cavity and the other end of the first oil inlet pipe being communicated with the low-pressure ejector oil inlet. The application further comprises a second oil inlet pipe, one end of the second oil inlet pipe being communicated with the high-pressure cavity and the other end of the second oil inlet pipe being communicated with the high-pressure ejector oil inlet. The first oil inlet pipe and the second oil inlet pipe are flexible oil inlet pipes. The compressor is a linear compressor.

2. The compressor of claim 1, wherein, The application further comprises a linear motor, a piston and a cylinder, the cylinder being located in the sealed cavity, the linear motor being transmissionally connected with the piston, the piston being axially slidably connected with the cylinder, and the expansion channel being communicated with a fitting gap between the piston and the cylinder. The compressor is a rotary compressor.

3. The compressor of claim 2, wherein, The application 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 being coaxially and spacedly arranged in the sealed cavity, one end of the first crankshaft being rotationally connected with the shell, the other end of the first crankshaft being rotationally connected with the first crankshaft support and the second crankshaft support, the first rotary motor being transmissionally connected with the first crankshaft, and the expansion channel being communicated with a fitting gap between the first crankshaft and the first crankshaft support and the second crankshaft support.

4. The compressor of any one of claims 1 to 3, wherein The first crankshaft is provided with a first shaft section and a second shaft section at intervals, an outer wall of the first shaft section is provided with a first oil channel in the length direction, an outer wall of the second shaft section is provided with a second oil channel in the length direction, the first oil channel and the second oil channel are communicated with the expansion channel, and the first oil channel and the second oil channel are arranged at intervals on the first crankshaft. The body is integrally arranged with the partition plate, or the body is integrally arranged with the first crankshaft support, or the body is integrally arranged with the second crankshaft support.

5. The compressor of any one of claims 1 to 3, wherein The compressor is a scroll compressor. ​ 6. The compressor of claim 5, wherein, ​ 7. The compressor of claim 5, wherein, ​ 8. The compressor of any one of claims 1 to 3, wherein ​ The second rotary motor, the second crankshaft, the third crankshaft support, the scroll orbiting disk and the scroll stationary disk are arranged in the sealed cavity, one end of the second crankshaft is rotationally connected with the shell, the other end of the second crankshaft is rotationally connected with the third crankshaft support and connected with the scroll orbiting disk, and the expansion channel is communicated with the gaps between the second crankshaft and the third crankshaft support and between the scroll orbiting disk and the scroll stationary disk.

9. The compressor of claim 8, wherein, The separation plate is integrally arranged with the scroll stationary disk, and the body is integrally arranged with the scroll stationary disk.

10. The compressor of any one of claims 1 to 3, wherein, The compressor is a screw compressor or a centrifugal compressor.

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