Multi-cylinder rotary compressor

Abstract

The application discloses a multi-cylinder rotary compressor and relates to the technical field of compressors.The multi-cylinder rotary compressor comprises a shell, a crankshaft, at least two cylinders and at least one partition plate.The shell comprises a cavity.The crankshaft is arranged in the shell.The at least two cylinders are arranged in the shell along the axial direction of the crankshaft, and a part of the crankshaft is located in the cylinders.The at least one partition plate is arranged between two adjacent cylinders, and the partition plate is provided with a communication port through which the crankshaft passes.The diameter of the communication port is larger than the diameter of the crankshaft.The partition plate, the crankshaft and the at least two cylinders surround an inner chamber, and the shell, the partition plate, the crankshaft and the at least two cylinders surround an outer chamber.The at least one through hole is arranged on the partition plate along the radial direction of the crankshaft and communicates the outer chamber with the inner chamber.The slide groove is arranged on the end face of the cylinder facing the partition plate, and a first included angle is formed between the symmetrical center plane of the slide groove along the axial direction and the symmetrical center plane of the through hole along the axial direction.The flow of lubricating oil is used to realize pressure balance, reduce impact load and improve the service life and operation stability of the compressor.

Description

Technical Field

[0001] This application relates to the field of compressor technology, specifically to a multi-cylinder rotary compressor. Background Technology

[0002] Multi-cylinder compressors operate by connecting multiple cylinders in series or parallel to achieve higher efficiency or a larger pressure ratio. Dividers in multi-cylinder compressors are used to separate adjacent cylinder chambers, but these dividers are typically solid structures or only have simple axial channels, limiting their function to mechanical isolation and lacking effective support for lubrication and pressure balance.

[0003] Therefore, how to solve the oil pressure balance in the compressor has become a technical problem that urgently needs to be solved in this field. Utility Model Content

[0004] The present invention aims to at least solve the problem of oil pressure balance in compressors in related technologies.

[0005] Therefore, the first aspect of this utility model provides a multi-cylinder rotary compressor, comprising: a housing including a cavity; a crankshaft disposed within the housing; at least two cylinders disposed within the housing along the axial direction of the crankshaft, a portion of the crankshaft being located within the cylinders; at least one partition disposed between two adjacent cylinders, the partition having a connecting port through which the crankshaft passes, the diameter of the connecting port being larger than the diameter of the crankshaft, the partition, the crankshaft, and the at least two cylinders enclosing an inner cavity, and the housing, the partition, the crankshaft, and the at least two cylinders enclosing an outer cavity; at least one through hole disposed on the partition along the radial direction of the crankshaft and connecting the outer cavity and the inner cavity; and a vane groove disposed on the end face of the cylinder facing the partition, the vane groove forming a first included angle with the axial center plane of the vane groove and the axial center plane of the through hole.

[0006] This utility model provides a multi-cylinder rotary compressor, comprising a housing, a crankshaft, at least two cylinders, at least one partition, at least one through hole, and a vane groove. The housing has a cavity for accommodating the internal components of the compressor and providing structural support. The crankshaft, as the core component for power transmission, is located within the cavity of the housing. At least two cylinders are arranged axially along the crankshaft within the housing, each cylinder forming a compression chamber capable of containing working gas, with a portion of the crankshaft passing through the cylinder. Each cylinder includes rollers, which are connected to the crankshaft, driving the rollers in reciprocating motion. This, in conjunction with an eccentric portion and a piston, achieves changes in cylinder volume. At least one partition is located between two adjacent cylinders, allowing each cylinder to operate independently, ensuring that each cylinder can operate independently according to its designed intake, compression, and exhaust processes without interference. For example, during compression, if the pressure in one cylinder increases, the partition can prevent high-pressure gas from entering the adjacent low-pressure cylinder, ensuring the compressor's operational stability. The partition has a connecting port through which the crankshaft passes, with the diameter of the connecting port larger than the crankshaft diameter to ensure smooth crankshaft rotation and avoid interference, while also providing a channel for fluid flow between the chambers. The inner chamber is enclosed by the partition, crankshaft, and at least two cylinders, while the outer chamber is enclosed by the housing, partition, crankshaft, and at least one cylinder. At least one through-hole is formed on the partition along the radial direction of the crankshaft, directly connecting the outer and inner chambers, allowing fluid to flow between the two chambers. Specifically, the through-hole is used to deliver lubricating oil between the outer and inner chambers; the lubricating oil in the inner chamber lubricates the contact area between the partition and the crankshaft, as well as the contact area between the cylinder end face and the partition, reducing friction and wear between components. Secondly, when the crankshaft rotates at high speed, the lubricating oil in the inner and outer chambers will experience pressure differences due to agitation, resulting in higher pressure in the inner chamber than in the outer chamber. The through-hole allows the lubricating oil in the inner chamber to flow to the outer chamber, thereby eliminating the pressure difference and further preventing excessive pressure in the inner chamber from causing an increase in the clearance between the baffle and cylinder. It also reduces the amount of lubricating oil in the chamber, lowering the resistance to crankshaft rotation. Therefore, the through-hole balances the pressure in the inner and outer chambers; it is essentially a pressure relief channel. Lowering the pressure in the inner chamber also reduces the impact load of the lubricating oil on the inner chamber. In other words, the through-hole in this application is a channel specifically designed for lubricating oil, independent of the cylinder's compression chamber and refrigerant circuit, connecting only the outer and inner chambers. Pressure balance is achieved through the flow of lubricating oil, reducing impact loads and improving the compressor's service life and operational stability.

[0007] In addition, the multi-cylinder rotary compressor also includes a vane groove, which is located on the cylinder end face facing the partition. The vane groove forms a first angle with the center plane of symmetry along the crankshaft axial direction and the center plane of symmetry of the through-hole along the crankshaft axial direction. That is, the vane groove and the through-hole do not coincide in the crankshaft axial direction. The cylinder end face where the vane groove is located directly faces the compression chamber. During the intake phase, the compression chamber is at low pressure, and during the compression phase, the pressure rapidly rises to high pressure, with a relatively large pressure amplitude and rapid changes. The separate arrangement of the through-hole and the vane groove facilitates lubricating oil flow and avoids the influence of pressure changes, thereby ensuring the reliability of stable oil pressure in the through-hole.

[0008] Optionally, the crankshaft is provided with an oil suction hole and an oil outlet hole. The crankshaft includes a cavity, with the oil suction hole connecting the crankshaft cavity and the outer chamber, and the oil outlet hole connecting the crankshaft cavity and the inner chamber. The lower part of the crankshaft is immersed in lubricating oil. When the crankshaft rotates at high speed, lubricating oil is drawn into the crankshaft cavity through the oil suction hole and discharged into the inner chamber through the oil outlet hole. The lubricating oil in the inner chamber flows to the outer chamber through a through hole, and the lubricating oil in the outer chamber is drawn into the crankshaft's oil suction hole, thus completing the flow and circulation of lubricating oil.

[0009] In some embodiments, the cross-sectional shape of the through hole along the axial direction may optionally be any one of a circle, an ellipse, a polygon, or an oblong shape.

[0010] In this embodiment, a through-hole is radially disposed on the baffle plate along the crankshaft and connects the outer chamber and the inner chamber. The cross-sectional shape of the through-hole along the axial direction can be any one of circular, elliptical, polygonal, or oblong. The cross-sectional shape of the baffle plate determines the profile of the through-hole under axial projection. Different shapes affect the oil flow path, velocity distribution, and fit with the baffle plate and crankshaft structure. Circular cross-sections are easy to machine, have smooth inner walls, low oil flow resistance, and equal flow area throughout, facilitating stable and uniform oil flow, making them suitable for applications with low requirements for flow disturbance. Elliptical cross-sections provide a larger channel width along the major axis, which is beneficial for guiding oil flow in a specific direction. Polygonal cross-sections, including triangular, quadrilateral, and hexagonal cross-sections, can utilize straight segments and sharp corners to form relatively regular oil channels, facilitating docking and positioning with surrounding structures. Oblong cross-sections are similar to ellipses, but with straight edges at both ends, maintaining a large flow area while reducing burr interference after machining, and making it easier to control directionality during axial installation. By selecting through holes with different cross-sectional shapes, the flow characteristics of lubricating oil between the inner and outer chambers can be optimized, improving lubrication reliability and pressure equalization capability, reducing flow resistance and energy loss, enabling the compressor to maintain stable oil lubrication performance under various operating conditions and have a longer service life.

[0011] In some embodiments, the ratio of the equivalent diameter of the through hole to the thickness of the partition is optionally greater than or equal to 0.1 and less than or equal to 0.8.

[0012] In this embodiment, the ratio of the equivalent diameter of the through-hole to the thickness of the partition is limited to a range greater than or equal to 0.1 and less than or equal to 0.8. The equivalent diameter is the equivalent circular diameter calculated based on the flow cross-sectional area of ​​the through-hole, used to uniformly measure the flow capacity of through-holes with different cross-sectional shapes. A ratio of the equivalent diameter of the through-hole to the thickness of the partition greater than or equal to 0.1 ensures that the through-hole has sufficient flow area to reduce flow resistance, while a ratio less than or equal to 0.8 ensures that the partition has a certain strength and rigidity.

[0013] In some embodiments, the ratio of the equivalent diameter of the through hole to the thickness of the partition is optionally greater than or equal to 0.2 and less than or equal to 0.6.

[0014] In this embodiment, by controlling the ratio of the equivalent diameter of the through hole to the thickness of the partition plate to be between 0.2 and 0.6, it can be further ensured that the flow resistance of the lubricating oil between the inner and outer chambers is moderate and that there is sufficient flow efficiency, while maintaining the strength and rigidity of the partition plate, preventing deformation and leakage, and improving the lubrication reliability and structural durability of the compressor operation.

[0015] In some embodiments, the first included angle is optionally greater than or equal to 180° and less than 360°.

[0016] In this embodiment, a vane groove is disposed on the cylinder end face facing the partition plate. A first included angle is formed between the axial center plane of the vane groove and the axial center plane of the through hole, the first included angle being greater than or equal to 180° and less than 360°. The vane groove is used to accommodate vanes, which move with the piston or rollers to slide within the groove, thereby sealing the refrigerant gas in the cylinder compression chamber and controlling the volume change of the cylinder compression chamber. The cylinder includes an intake side and a compression side. The vane groove is disposed on the end face of the intake side, i.e., the side facing the cylinder inlet, to achieve good intake sealing. The first included angle is the circumferential angle difference between the vane groove and the through hole projected axially onto the crankshaft. By limiting the first included angle to be greater than or equal to 180° and less than 360°, a phase difference between the vane groove and the through hole can be formed in the circumferential layout, so that the timing of lubricating oil delivery and vane movement is matched, ensuring that the vane groove receives sufficient oil when needed, avoiding mutual interference, thereby improving lubrication reliability, reducing noise and mechanical load, and enhancing the smoothness and durability of multi-cylinder rotary compressor operation.

[0017] In some embodiments, optionally, the number of cylinders is two, the number of partitions is one, the cylinder includes a first cylinder body and a second cylinder body, the crankshaft, the first cylinder body, the second cylinder body and the partitions enclose a first inner chamber, the crankshaft, the housing, the first cylinder body, the second cylinder body and the partitions enclose an outer chamber; wherein, the first inner chamber and the outer chamber are connected by a through hole.

[0018] In this embodiment, a baffle is disposed between adjacent first and second cylinder blocks, separating the compression chambers of the two cylinders and guiding the circulation of lubricating oil. A first inner chamber is formed by the crankshaft, first cylinder block, second cylinder block, and baffle, while an outer chamber is formed by the crankshaft, housing, first cylinder block, second cylinder block, and baffle. A through-hole is radially formed on the baffle along the crankshaft, connecting only the first inner chamber and the outer chamber; the through-hole is essentially a dedicated flow channel for lubricating oil. By using a baffle and two cylinder blocks to form the first inner and outer chambers, and connecting them via the through-hole, pressure balance between the first inner and outer chambers is ensured. This also guarantees stable lubrication of the baffle, crankshaft, and sliding vanes, reducing mechanical wear and operating noise, helping to extend service life and maintain high energy efficiency.

[0019] Optionally, in the twin-cylinder compressor, the ratio of the equivalent diameter of the through hole to the thickness of the partition is 0.3.

[0020] In some embodiments, optionally, the number of cylinders is three, the number of partitions is two, the cylinders include a first cylinder body, a second cylinder body and a third cylinder body, the crankshaft, the first cylinder body, the second cylinder body and the partitions enclose a first inner chamber, the crankshaft, the second cylinder body, the third cylinder body and the partitions enclose a second inner chamber, and the crankshaft, the housing, the first cylinder body, the second cylinder body, the third cylinder body and the partitions enclose an outer chamber; wherein, the first inner chamber and the outer chamber are connected through a through hole in one of the partitions, and the second inner chamber and the outer chamber are connected through a through hole in the other partition.

[0021] In this embodiment, a first inner chamber is formed by the crankshaft, the first cylinder block, the second cylinder block, and the first partition plate; a second inner chamber is formed by the crankshaft, the second cylinder block, the third cylinder block, and the second partition plate; and an outer chamber is formed by the crankshaft, the housing, the first cylinder block, the second cylinder block, the third cylinder block, and the two partition plates. The first inner chamber and the outer chamber are connected by a through hole in one of the partition plates, and the second inner chamber and the outer chamber are connected by a through hole in the other partition plate, thus forming two independent oil passages, allowing lubricating oil to flow between the outer chamber and the first inner chamber, and between the outer chamber and the second inner chamber. Compared to a two-cylinder single-partition structure, a three-cylinder double-partition layout can increase displacement and power density within the same space. By setting three cylinder blocks and two partition plates to form the first inner chamber, the second inner chamber, and the outer chamber, and connecting the outer chamber to the partition plates through through holes, stable and targeted lubrication is ensured for each partition plate, crankshaft, and vane, reducing mechanical wear and operating noise.

[0022] Optionally, in the twin-cylinder compressor, the ratio of the equivalent diameter of the through hole to the thickness of the partition is 0.4.

[0023] In some embodiments, the upper bearing, cylinder, partition, and lower bearing may be detachably connected by bolts.

[0024] In this embodiment, the upper bearing, cylinder, partition, and lower bearing are arranged in sequence. Each of these components has threaded through holes for bolts to pass through, providing a detachable rigid connection between the components. The bolts passing through the threaded through holes of adjacent components create a highly coaxial and uniformly stressed rigid frame for the entire assembly. This detachable assembly method allows for the inspection or replacement of the upper bearing, cylinder, partition, and lower bearing without damaging the main structure, significantly reducing downtime and maintenance costs.

[0025] In some embodiments, optionally, at least two cylinders and at least one partition form a cylinder assembly, and the multi-cylinder rotary compressor further includes: an upper bearing disposed on one side of the cylinder assembly along the axial direction of the crankshaft; a lower bearing disposed on the other side of the cylinder assembly along the axial direction of the crankshaft; and a muffler disposed on the side of the lower bearing opposite to the cylinder assembly.

[0026] In this embodiment, the multi-cylinder rotary compressor further includes an upper bearing, a lower bearing, and a muffler. At least two cylinders and at least one partition plate constitute a cylinder assembly. The upper bearing is located on one side of the cylinder assembly along the axial direction of the crankshaft, and the lower bearing is located on the other side of the cylinder assembly along the axial direction of the crankshaft. The muffler is located on the side of the lower bearing facing away from the cylinder assembly. The upper and lower bearings stably support the crankshaft, ensuring synchronous compression strokes of each cylinder, while the muffler suppresses airflow noise and pulsation. The cylinder assembly, together with the upper and lower bearings, forms a stable support and sealing system. The muffler, located outside the lower bearing, reduces airflow noise and pulsation, thereby improving the compressor's operating accuracy and smoothness, reducing mechanical wear and vibrations caused by gas pulsation, and lowering operating noise.

[0027] In some embodiments, the multi-cylinder rotary compressor may optionally include: a solid-liquid separator; an intake port connecting the cylinder and the solid-liquid separator; and an exhaust port disposed on the housing and communicating with the solid-liquid separator.

[0028] In this embodiment, the solid-liquid separator is a device connected in the refrigerant circuit to separate liquid refrigerant or lubricating oil particles entrained in the refrigerant gas, preventing excessive liquid from entering the cylinder and causing impact. The intake port connects the cylinder and the solid-liquid separator, allowing the separated low-pressure gaseous refrigerant to enter the cylinder, ensuring clean intake to the compression chamber. The exhaust port is located on the housing and communicates with the solid-liquid separator, forming a refrigerant circulation loop. The refrigerant first enters the solid-liquid separator to remove liquid and oil, and then enters the cylinder for compression through the intake port. Compared to a structure without a solid-liquid separator, this design intercepts liquid and impurities, reduces impact on the cylinder, and improves compression efficiency and operational safety. Attached Figure Description

[0029] The above and / or additional aspects and advantages of this utility model will become apparent and readily understood from the description of the embodiments taken in conjunction with the following drawings, in which:

[0030] Figure 1 One of the structural schematic diagrams of a multi-cylinder rotary compressor according to an embodiment of this application is shown;

[0031] Figure 2 A second schematic diagram of the structure of a multi-cylinder rotary compressor according to an embodiment of this application is shown;

[0032] Figure 3 A schematic diagram of the structure of a twin-cylinder rotary compressor according to an embodiment of this application is shown;

[0033] Figure 4 A schematic diagram of the structure of a three-cylinder rotary compressor according to an embodiment of this application is shown;

[0034] Figure 5 One of the structural schematic diagrams of a partition according to an embodiment of this application is shown;

[0035] Figure 6 A second schematic diagram of the structure of a partition according to an embodiment of this application is shown;

[0036] Figure 7 The third schematic diagram shows the structure of a partition according to an embodiment of this application;

[0037] Figure 8 The fourth schematic diagram shows the structure of a partition according to an embodiment of this application;

[0038] Figure 9 It shows Figure 8 A schematic diagram of the cross-section along the AA direction.

[0039] The components include: 1. Housing; 11. Cavity; 12. Intake port; 13. Exhaust port; 2. Crankshaft; 3. Cylinder; 31. Sliding vane groove; 32. First cylinder body; 33. Second cylinder body; 34. Third cylinder body; 4. Partition; 41. Connecting port; 43. First partition; 44. Second partition; 5. Inner chamber; 51. First inner chamber; 52. Second inner chamber; 6. Outer chamber; 7. Through hole; 81. Upper bearing; 82. Lower bearing; 83. Silencer; 9. Solid-liquid separator; 20. Cylinder assembly; and 100+ cylinder rotary compressor. Detailed Implementation

[0040] To better understand the above-mentioned objectives, features, and advantages of this application, the application will be further described in detail below with reference to the accompanying drawings and specific embodiments. It should be noted that, unless otherwise specified, the embodiments and features described in these embodiments can be combined with each other.

[0041] Many specific details are set forth in the following description in order to provide a full understanding of this application. However, this application may also be implemented in other ways different from those described herein. Therefore, the scope of protection of this application is not limited to the specific embodiments disclosed below.

[0042] like Figure 1 , Figure 2 , Figure 3 and Figure 4 As shown, the first aspect of this utility model provides a multi-cylinder rotary compressor 100, comprising: a housing 1, including a cavity 11; a crankshaft 2, disposed within the housing 1; at least two cylinders 3, disposed within the housing 1 along the axial direction of the crankshaft 2, with a portion of the crankshaft 2 located within the cylinders 3; at least one partition 4, disposed between two adjacent cylinders 3, the partition 4 having a connecting port 41 through which the crankshaft 2 passes, the diameter of the connecting port 41 being larger than the diameter of the crankshaft 2; the partition 4, the crankshaft 2, and the at least two cylinders 3 enclosing an inner chamber 5; the housing 1, the partition 4, the crankshaft 2, and the at least two cylinders 3 enclosing an outer chamber 6; at least one through hole 7, disposed on the partition 4 along the radial direction of the crankshaft 2, and connecting the outer chamber 6 and the inner chamber 5; and a vane groove 31, disposed on the end face of the cylinder 3 facing the partition 4, the vane groove 31 forming a first included angle with the axial center plane of the symmetrical plane of the symmetrical plane of the symmetrical plane of the through hole 7.

[0043] The multi-cylinder rotary compressor 100 provided by this utility model includes a housing 1, a crankshaft 2, at least two cylinders 3, at least one partition 4, at least one through hole 7, and a vane groove 31. The housing 1 has a cavity 11 for accommodating the internal components of the compressor and providing structural support. The crankshaft 2, as the core component for power transmission, is disposed within the cavity 11 of the housing 1. At least two cylinders 3 are arranged in the housing 1 along the axial direction of the crankshaft 2, and each cylinder 3 forms a compression chamber for accommodating working gas, with a portion of the crankshaft 2 passing through the cylinder 3. The cylinder 3 includes rollers, and the crankshaft 2 is connected to the rollers and drives the rollers to reciprocate, cooperating with the eccentric part and piston to realize the volume change of the cylinder 3. At least one partition 4 is disposed between two adjacent cylinders 3, and the partition 4 makes each cylinder 3 independent of each other, ensuring that each cylinder 3 can work independently according to the designed intake, compression, and exhaust processes without interference. For example, during compression, when the pressure inside a cylinder 3 increases, the baffle 4 can prevent high-pressure gas from entering the adjacent low-pressure cylinder 3, ensuring the operational stability of the compressor. The baffle 4 has a connecting port 41 through which the crankshaft 2 passes, and the diameter of the connecting port 41 is larger than the diameter of the crankshaft 2, ensuring smooth rotation of the crankshaft 2 and avoiding interference, while also providing a channel for fluid flow between the chambers. The inner chamber 5 is enclosed by the baffle 4, the crankshaft 2, and at least two cylinders 3, while the outer chamber 6 is enclosed by the housing 1, the baffle 4, the crankshaft 2, and at least one cylinder 3. At least one through hole 7 is formed on the baffle 4 along the radial direction of the crankshaft 2, directly connecting the outer chamber 6 and the inner chamber 5, allowing fluid to flow between the two chambers. That is, the through hole 7 is used to deliver lubricating oil between the outer chamber 6 and the inner chamber 5. The lubricating oil in the inner chamber 5 lubricates the contact area between the baffle 4 and the crankshaft 2, as well as the contact area between the end face of the cylinder 3 and the baffle 4, reducing friction and wear between components. Secondly, when the crankshaft 2 rotates at high speed, the lubricating oil in the inner chamber 5 and the outer chamber 6 will experience a pressure difference due to agitation, resulting in a higher pressure in the inner chamber 5 than in the outer chamber 6. The through-hole 7 allows the lubricating oil in the inner chamber 5 to flow to the outer chamber 6, thereby eliminating the pressure difference and further preventing excessive pressure in the inner chamber 5 from causing an increase in the clearance between the baffle 4 and the cylinder 3. It also reduces the amount of lubricating oil in the chamber 5, lowering the resistance to crankshaft 2 rotation. Therefore, the through-hole 7 can balance the pressure between the inner chamber 5 and the outer chamber 6. The through-hole 7 is essentially a pressure relief channel; the reduced pressure in the inner chamber 5 also reduces the impact load of the lubricating oil on the inner chamber 5. In other words, the through-hole 7 of this application is a channel specifically designed for lubricating oil, independent of the compression chamber and refrigerant circuit of the cylinder 3, connecting only the outer chamber 6 and the inner chamber 5. Pressure balance is achieved through the flow of lubricating oil, reducing impact load and improving the compressor's service life and operational stability.

[0044] In addition, the multi-cylinder rotary compressor 100 also includes a vane groove 31, which is disposed on the end face of the cylinder 3 facing the partition 4. The vane groove 31 forms a first angle with the center plane of symmetry of the through hole 7 along the axial direction of the crankshaft 2. That is, the vane groove 31 and the through hole 7 do not coincide in the axial direction of the crankshaft 2. The end face of the cylinder 3 containing the vane groove 31 directly faces the compression chamber. During the intake phase, the compression chamber is at low pressure, and during the compression phase, the pressure rapidly rises to high pressure, with a relatively large pressure amplitude and rapid changes. The through hole 7 is separated from the vane groove 31, which facilitates the flow of lubricating oil and avoids the influence of pressure changes, thereby ensuring the reliability of the stable oil pressure in the through hole 7.

[0045] Optionally, the crankshaft 2 is provided with an oil suction hole and an oil outlet hole. The crankshaft 2 includes a cavity, the oil suction hole connects the cavity of the crankshaft 2 to the outer chamber 6, and the oil outlet hole connects the cavity of the crankshaft 2 to the inner chamber 5. The lower part of the crankshaft 2 is immersed in lubricating oil. When the crankshaft 2 rotates at high speed, lubricating oil is drawn into the cavity of the crankshaft 2 through the oil suction hole and discharged into the inner chamber 5 through the oil outlet hole. The lubricating oil in the inner chamber 5 flows to the outer chamber 6 through the through hole 7. The lubricating oil in the outer chamber 6 is then drawn into the oil suction hole of the crankshaft 2, thereby completing the flow and circulation of the lubricating oil.

[0046] In some embodiments, optionally, such as Figure 1 , Figure 5 , Figure 6 and Figure 7 As shown, the cross-sectional shape of the through hole 7 along the axial direction is any one of a circle, an ellipse, a polygon, or an oblong.

[0047] In this embodiment, the through-hole 7 is radially disposed on the partition 4 along the crankshaft 2 and connects the outer chamber 6 and the inner chamber 5. The cross-sectional shape of the through-hole 7 along the axial direction can be any one of a circle, ellipse, polygon, or oblong. The cross-sectional shape of the partition 4 determines the profile of the through-hole 7 under axial projection. Different shapes will affect the oil flow path, velocity distribution, and the fit between the through-hole 7 and the partition 4 and the crankshaft structure. For example... Figure 1 As shown, the circular cross-section through hole 7 is easy to machine, has a smooth inner wall, low oil flow resistance, and equal flow area throughout, which is conducive to forming a stable and uniform oil flow, making it suitable for applications with low requirements for flow disturbance. Figure 5 As shown, an elliptical cross-section provides a larger channel width along its major axis, which is beneficial for guiding oil flow in a specific direction. For example... Figure 6 As shown, polygonal cross-sections include triangular, quadrilateral, and hexagonal cross-sections, etc. They can utilize straight segments and sharp corners to form relatively regular oil channels, facilitating docking and positioning with surrounding structures. For example... Figure 7As shown, the oblong cross-section resembles an ellipse, but with straight edges at both ends. This reduces burr interference after machining while maintaining a large flow area, and makes directional control easier during axial installation. By selecting through holes 7 with different cross-sectional shapes, the flow characteristics of lubricating oil between the inner and outer chambers 6 can be optimized, improving lubrication reliability and pressure equalization, reducing flow resistance and energy loss. This allows the compressor to maintain stable oil lubrication performance under various operating conditions and has a longer service life.

[0048] In some embodiments, optionally, such as Figure 1 , Figure 8 and Figure 9 As shown, the ratio of the equivalent diameter of the through hole 7 to the thickness of the partition plate 4 is greater than or equal to 0.1 and less than or equal to 0.8.

[0049] In this embodiment, the ratio of the equivalent diameter of the through-hole 7 to the thickness of the partition 4 is limited to a range greater than or equal to 0.1 and less than or equal to 0.8. The equivalent diameter is the equivalent circular diameter converted from the flow cross-sectional area of ​​the through-hole 7, used to uniformly measure the flow capacity of through-holes 7 with different cross-sectional shapes. A ratio of the equivalent diameter of the through-hole 7 to the thickness of the partition 4 greater than or equal to 0.1 ensures that the through-hole 7 has sufficient flow area to reduce flow resistance, while a ratio of the equivalent diameter of the through-hole 7 to the thickness of the partition 4 less than or equal to 0.8 ensures that the partition 4 has a certain strength and rigidity.

[0050] In some embodiments, optionally, such as Figure 1 , Figure 8 and Figure 9 As shown, the ratio of the equivalent diameter of the through hole 7 to the thickness of the partition plate 4 is greater than or equal to 0.2 and less than or equal to 0.6.

[0051] In this embodiment, by controlling the ratio of the equivalent diameter of the through hole 7 to the thickness of the partition plate 4 to be between 0.2 and 0.6, it can be further ensured that the flow resistance of the lubricating oil between the inner and outer chambers 6 is moderate and that there is sufficient flow efficiency, while maintaining the strength and rigidity of the partition plate 4, preventing deformation and leakage, and improving the lubrication reliability and structural durability of the compressor operation.

[0052] In some embodiments, optionally, such as Figure 8 As shown, the first included angle θ is greater than or equal to 180° and less than 360°.

[0053] In this embodiment, the vane groove 31 is disposed on the end face of the cylinder 3 facing the partition 4. A first included angle θ is formed between the axial center plane and the axial center plane of the through hole 7. The first included angle θ is greater than or equal to 180° and less than 360°. The vane groove 31 is used to accommodate a vane, which moves with the piston or roller to slide within the groove, thereby sealing the refrigerant gas in the compression chamber of the cylinder 3 and controlling the volume change of the compression chamber of the cylinder 3. The cylinder 3 includes an intake side and a compression side. The vane groove 31 is disposed on the end face of the intake side, that is, the side facing the air inlet of the cylinder 3, to achieve good intake sealing. The first included angle θ is the circumferential angle difference between the vane groove 31 and the through hole 7 projected axially onto the crankshaft 2. By limiting the first included angle θ to be greater than or equal to 180° and less than 360°, a phase difference between the vane groove 31 and the through hole 7 can be formed in the circumferential layout, so that the timing of lubricating oil delivery and vane movement is matched, ensuring that the vane groove 31 receives sufficient oil when needed, avoiding mutual interference, thereby improving lubrication reliability, reducing noise and mechanical load, and enhancing the stability and durability of the multi-cylinder rotary compressor 100.

[0054] In some embodiments, optionally, such as Figure 3 As shown, there are two cylinders 3 and one partition 4. The cylinder 3 includes a first cylinder body 32 and a second cylinder body 33. The crankshaft 2, the first cylinder body 32, the second cylinder body 33 and the partition 4 form a first inner chamber 51. The crankshaft 2, the housing 1, the first cylinder body 32, the second cylinder body 33 and the partition 4 form an outer chamber 6. The first inner chamber 51 and the outer chamber 6 are connected by a through hole 7.

[0055] In this embodiment, a baffle 4 is disposed between adjacent first cylinder block 32 and second cylinder block 33, which can separate the compression chambers of the two cylinder blocks and guide the circulation of lubricating oil. The crankshaft 2, first cylinder block 32, second cylinder block 33 and baffle 4 together form the first inner chamber 51, and the crankshaft 2, housing 1, first cylinder block 32, second cylinder block 33 and baffle 4 together form the outer chamber 6. A through hole 7 is radially opened on the baffle 4 along the crankshaft 2, connecting only the first inner chamber 51 and the outer chamber 6. The through hole 7 is actually a dedicated flow channel for lubricating oil. By setting a baffle 4 and two cylinder blocks to form the first inner chamber 51 and the outer chamber 6, and connecting them with the through hole 7, the pressure balance of the first inner chamber 51 and the outer chamber 6 is ensured. At the same time, it also ensures stable lubrication of the baffle 4, crankshaft 2 and sliding vanes, reducing mechanical wear and operating noise, helping to extend service life and maintain high energy efficiency.

[0056] Optionally, in the twin-cylinder compressor, the ratio of the equivalent diameter of the through hole 7 to the thickness of the partition plate 4 is 0.3.

[0057] In some embodiments, optionally, such as Figure 4As shown, there are three cylinders 3 and two partitions 4. Each cylinder 3 includes a first cylinder body 32, a second cylinder body 33, and a third cylinder body 34. The crankshaft 2, the first cylinder body 32, the second cylinder body 33, and the partitions 4 form a first inner chamber 51. The crankshaft 2, the second cylinder body 33, the third cylinder body 34, and the partitions 4 form a second inner chamber 52. The crankshaft 2, the housing 1, the first cylinder body 32, the second cylinder body 33, the third cylinder body 34, and the partitions 4 form an outer chamber 6. The first inner chamber 51 and the outer chamber 6 are connected through a through hole 7 on one of the partitions 4, and the second inner chamber 52 and the outer chamber 6 are connected through a through hole 7 on the other partition 4.

[0058] In this embodiment, a first inner chamber 51 is formed by the crankshaft 2, the first cylinder block 32, the second cylinder block 33, and the first partition 4; a second inner chamber 52 is formed by the crankshaft 2, the second cylinder block 33, the third cylinder block 34, and the second partition 4; and an outer chamber 6 is formed by the crankshaft 2, the housing 1, the first cylinder block 32, the second cylinder block 33, the third cylinder block 34, and the two partitions 4. The first inner chamber 51 and the outer chamber 6 are connected by a through hole 7 on one of the partitions 4, and the second inner chamber 52 and the outer chamber 6 are connected by a through hole 7 on the other partition 4, thus forming two independent oil passages, allowing lubricating oil to flow between the outer chamber 6 and the first inner chamber 51, and between the outer chamber 6 and the second inner chamber 52, respectively. Compared to a two-cylinder single-partition structure, the three-cylinder double-partition 4 layout can increase displacement and power density within the same space. By setting up three cylinders and two partitions 4 to form a first inner chamber 51, a second inner chamber 52 and an outer chamber 6, and connecting the outer chamber 6 with through holes 7 on each partition 4, it is ensured that each partition 4, crankshaft 2 and sliding vane and other parts receive stable and targeted lubrication, thereby reducing mechanical wear and operating noise.

[0059] Optionally, in the twin-cylinder compressor, the ratio of the equivalent diameter of the through hole 7 to the thickness of the partition plate 4 is 0.4.

[0060] In some embodiments, optionally, such as Figure 3 and Figure 4 As shown, the upper bearing 81, cylinder 3, partition 4 and lower bearing 82 are detachably connected by bolts.

[0061] In this embodiment, the upper bearing 81, cylinder 3, partition 4, and lower bearing 82 are arranged in sequence. Each of these components has threaded through holes for bolts to pass through, providing a detachable rigid connection. The bolts passing through the threaded through holes of adjacent components create a highly coaxial and uniformly stressed rigid frame for the entire assembly. This detachable assembly method allows for the maintenance or replacement of the upper bearing 81, cylinder 3, partition 4, and lower bearing 82 without damaging the main structure, significantly reducing downtime and maintenance costs.

[0062] In some embodiments, optionally, such as Figure 1 , Figure 3 and Figure 4 As shown, at least two cylinders 3 and at least one partition 4 form a cylinder assembly 20. The multi-cylinder rotary compressor 100 further includes: an upper bearing 81, located on one side of the cylinder assembly 20 along the axial direction of the crankshaft 2; a lower bearing 82, located on the other side of the cylinder assembly 20 along the axial direction of the crankshaft 2; and a muffler 83, located on the side of the lower bearing 82 facing away from the cylinder assembly 20.

[0063] In this embodiment, the multi-cylinder rotary compressor 100 further includes an upper bearing 81, a lower bearing 82, and a muffler 83. At least two cylinders 3 and at least one partition 4 constitute a cylinder assembly 20. The upper bearing 81 is disposed on one side of the cylinder assembly 20 along the axial direction of the crankshaft 2, and the lower bearing 82 is disposed on the other side of the cylinder assembly 20 along the axial direction of the crankshaft 2. The muffler 83 is disposed on the side of the lower bearing 82 facing away from the cylinder assembly 20. The upper bearing 81 and lower bearing 82 stably support the crankshaft 2, ensuring synchronous compression stroke of each cylinder 3, and the muffler 83 suppresses airflow noise and pulsation. The cylinder assembly 20, together with the upper bearing 81 and lower bearing 82, forms a stable support and sealing system. The muffler 83, located outside the lower bearing 82, reduces airflow noise and pulsation, thereby improving the compressor's operating accuracy and smoothness, reducing mechanical wear and vibration caused by gas pulsation, and lowering operating noise.

[0064] In some embodiments, optionally, such as Figure 1 As shown, the multi-cylinder rotary compressor 100 also includes: a solid-liquid separator 9; an intake port 12, connecting the cylinder 3 and the solid-liquid separator 9; and an exhaust port 13, disposed on the housing 1 and communicating with the solid-liquid separator 9.

[0065] In this embodiment, the solid-liquid separator 9 is a device connected in the refrigerant circuit to separate liquid refrigerant or lubricating oil particles entrained in the refrigerant gas, preventing excessive liquid from entering the cylinder 3 and causing impact. The intake port 12 connects the cylinder 3 and the solid-liquid separator 9, allowing the separated low-pressure gaseous refrigerant to enter the cylinder 3, ensuring clean intake into the compression chamber. The exhaust port 13 is located on the housing 1 and communicates with the solid-liquid separator 9, forming a refrigerant circulation loop. The refrigerant first enters the solid-liquid separator 9 to remove liquid and oil, and then enters the cylinder 3 for compression through the intake port 12. Compared to a structure without a solid-liquid separator, this design intercepts liquid and impurities, reduces impact on the cylinder 3, and improves compression efficiency and operational safety.

[0066] In a specific application, such as Figure 1 and Figure 2As shown, the partition 4 has at least one through hole 7, which is configured to fluidly connect the first chamber and the second chamber. The first chamber is the outer chamber 6, and the second chamber is the inner chamber 5. This single through hole structure can simultaneously or selectively achieve multiple functions such as pressure balancing, lubricating oil supply, gas diversion, and pressure unloading, greatly improving the overall performance of the compressor. Figure 9 As shown, the size of the through hole 7 is defined by the ratio of D to T (where D is the diameter of the through hole 7 and T is the thickness of the partition 4 at the through hole 7), eliminating the need for complex dimensional calculations. 0.1≤D / T≤0.8 ensures both the mechanical strength of the partition 4 and the effectiveness of the through hole 7, preventing failure due to processing or blockage.

[0067] like Figure 8 As shown, the cylinder 3 is provided with a sliding vane groove 31. The center surface of the sliding vane groove 31 is the X surface, the center axis surface of the radial oil hole is the Y surface, and the angle between the X surface and the Y surface is θ, which satisfies 180°≤θ≤360°.

[0068] like Figure 3 As shown, in a twin-cylinder rotary compressor, a partition 4 divides the housing 1 into a first chamber and a second chamber. A through hole 7 is opened on the side of the partition 4, which connects the spaces of the first chamber and the second chamber, with D / T=0.3.

[0069] like Figure 4 As shown, the three-cylinder compressor has a first partition 43 and a second partition 44. A through-hole 7 on the first partition 43 connects the first chamber to the second chamber. A through-hole 7 on the second partition 44 connects the first chamber to the third chamber. The D / T ratio is 0.4 for both.

[0070] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "illustrative embodiment," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of this application. 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 any one embodiment or example.

[0071] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "illustrative embodiment," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of this application. 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.

[0072] Although embodiments of this application have been shown and described, those skilled in the art will understand that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of this application, the scope of which is defined by the claims and their equivalents.

Claims

1. A multi-cylinder rotary compressor, characterized in that, include: The housing, including the cavity; The crankshaft is disposed within the housing; At least two cylinders are disposed within the housing along the axial direction of the crankshaft, and a portion of the crankshaft is located within the cylinders; At least one partition is disposed between two adjacent cylinders. The partition has a communication port through which the crankshaft passes. The diameter of the communication port is larger than the diameter of the crankshaft. The partition, the crankshaft, and at least two cylinders enclose an inner cavity. The housing, the partition, the crankshaft, and at least two cylinders enclose an outer cavity. At least one through hole is disposed on the partition plate in the radial direction of the crankshaft and connects the outer chamber and the inner chamber; A sliding vane groove is disposed on the end face of the cylinder facing the partition, and the sliding vane groove forms a first included angle with the center plane of symmetry along the axial direction and the center plane of symmetry along the axial direction of the through hole.

2. The multi-cylinder rotary compressor according to claim 1, characterized in that, The cross-sectional shape of the through hole along the axial direction is any one of a circle, an ellipse, a polygon, or an oblong shape.

3. The multi-cylinder rotary compressor according to claim 1, characterized in that, The ratio of the equivalent diameter of the through hole to the thickness of the partition is greater than or equal to 0.1 and less than or equal to 0.

8.

4. The multi-cylinder rotary compressor according to claim 1, characterized in that, The ratio of the equivalent diameter of the through hole to the thickness of the partition is greater than or equal to 0.2 and less than or equal to 0.

6.

5. The multi-cylinder rotary compressor according to claim 1, characterized in that, The first included angle is greater than or equal to 180° and less than 360°.

6. The multi-cylinder rotary compressor according to claim 1, characterized in that, The cylinder has two parts and one partition. Each cylinder includes a first cylinder body and a second cylinder body. The crankshaft, the first cylinder body, the second cylinder body, and the partition enclose a first inner chamber. The crankshaft, the housing, the first cylinder body, the second cylinder body, and the partition enclose an outer chamber. The first inner chamber is connected to the outer chamber through the through hole.

7. The multi-cylinder rotary compressor according to claim 1, characterized in that, The cylinder has three parts and two partitions. Each cylinder includes a first cylinder body, a second cylinder body, and a third cylinder body. The crankshaft, the first cylinder body, the second cylinder body, and the partitions form a first inner chamber. The crankshaft, the second cylinder body, the third cylinder body, and the partitions form a second inner chamber. The crankshaft, the housing, the first cylinder body, the second cylinder body, the third cylinder body, and the partitions form an outer chamber. The first inner chamber is connected to the outer chamber through a through hole in one of the partitions, and the second inner chamber is connected to the outer chamber through a through hole in the other partition.

8. The multi-cylinder rotary compressor according to claim 1, characterized in that, At least two of the cylinders and at least one of the partitions form a cylinder assembly, and the multi-cylinder rotary compressor further includes: The upper bearing is disposed on one side of the cylinder assembly along the axial direction of the crankshaft; The lower bearing is located on the other side of the cylinder assembly, along the axial direction of the crankshaft; A muffler is located on the side of the lower bearing facing away from the cylinder assembly.

9. The multi-cylinder rotary compressor according to claim 8, characterized in that, The upper bearing, the cylinder, the partition, and the lower bearing are detachably connected by bolts.

10. The multi-cylinder rotary compressor according to claim 1, characterized in that, Also includes: Solid-liquid separator; An air intake is connected to the cylinder and the solid-liquid separator; An exhaust port is provided on the housing and communicates with the solid-liquid separator.

Images