Electric motor rotor compressor, air conditioning system and vehicle

Abstract

The application discloses an electric rotor compressor, an air conditioning system and a vehicle, and relates to the technical field of compressors. The electric rotor compressor comprises a first shell with an oil separation cavity, a first communication channel and a second communication channel are formed in the shell wall of the first shell, and an oil separation outlet of the oil separation cavity is communicated with a refrigerant discharge outlet through the first communication channel; a compression component comprises a cylinder assembly, a piston, a crankshaft, a first bearing and a second bearing, a first discharge cavity is defined between the first bearing and the first shell, the compression component is provided with a first discharge port and is communicated with the first discharge cavity, and an oil separation inlet of the oil separation cavity is communicated with the first discharge cavity through the second communication channel. The electric rotor compressor forms the first discharge cavity between the first bearing and the first shell, reduces the strong correlation between the oil separation position, the discharge position and the intermediate position structure of the shell component, and has low difficulty in changing the discharge structure and the oil separation structure. The electric rotor compressor is beneficial to reducing the structural design difficulty and the assembly difficulty and improving the part universality.

Description

Technical Field

[0001] This invention relates to the field of compressor technology, and in particular to an electric rotary compressor, an air conditioning system, and a vehicle. Background Technology

[0002] Electric compressors are core components of vehicle refrigeration equipment. They are high-efficiency, low-noise, and stable-operating positive displacement compressors, widely used in automotive air conditioning systems as third-generation vehicle compressors. In recent years, with the development of new energy vehicles, the requirements for noise, vibration, and durability of automotive air conditioning compressors have further increased. Electric compressors, such as scroll compressors and rotary compressors, require lubricating oil to lubricate the friction pairs inside the compressor during use to reduce the noise generated by the friction pairs during operation.

[0003] In existing technologies, an oil separator is installed within the electric compressor to separate the mixture of refrigerant and lubricating oil discharged from the compressor's compression chamber. Some solutions propose converging all exhaust gas into an exhaust chamber between the main bearing and the support in a rotary compressor, from which exhaust gas is then discharged into the oil separator chamber. However, this approach suffers from several drawbacks. Since the compressor's refrigerant outlet and oil separator outlet are strongly correlated with the exhaust chamber, and the exhaust chamber is located between the main bearing and the support, a relatively long exhaust pipe is required between the exhaust chamber and the oil separator chamber. Furthermore, any changes to the exhaust or oil separator structure necessitate modifications to the support structure, making structural design alterations difficult. Summary of the Invention

[0004] The present invention aims to at least solve one of the technical problems existing in the prior art. To this end, the present invention proposes an electric rotary compressor that, while setting an oil separator chamber, adjusts the position of the exhaust chamber leading to the oil separator chamber to shorten the exhaust path between the exhaust chamber and the oil separator chamber, and facilitates structural modifications to the exhaust structure and the oil separator structure.

[0005] The present invention further proposes an air conditioning system having the above-mentioned electric rotary compressor.

[0006] The present invention also proposes a vehicle having the above-mentioned air conditioning system.

[0007] An electric rotary compressor according to an embodiment of the present invention includes: a housing component, the housing component including a first housing, the first housing having a refrigerant outlet, the first housing having an oil separator chamber, a first communicating channel and a second communicating channel formed in the housing wall of the first housing, the oil separator outlet of the oil separator chamber communicating with the refrigerant outlet through the first communicating channel; and a compression component, at least a portion of the compression component being housed within the first housing, the compression component including a cylinder assembly, a piston, a crankshaft, a first bearing and a second bearing, the piston being disposed within the cylinder assembly, the first bearing and the second bearing cooperating at both axial ends of the cylinder assembly, the crankshaft being connected to the piston to drive the piston to rotate, a first exhaust chamber being defined between the first bearing and the first housing, the compression component having a first exhaust port communicating with the first exhaust chamber, and the oil separator inlet of the oil separator chamber communicating with the first exhaust chamber through the second communicating channel.

[0008] According to an embodiment of the electric rotary compressor of the present invention, a first exhaust chamber is formed between the first bearing and the first housing. The compression component discharges the compressed high-pressure fluid into the first exhaust chamber, and then into the oil separator chamber for gas-liquid separation. The oil separator chamber does not directly intake air at the middle position of the housing component (including the second bearing), reducing the strong correlation between the oil separator position, the exhaust position and the middle position of the housing component. This makes modifications to the exhaust structure and oil separator structure easier, thus improving the applicability of this electric rotary compressor. This also helps reduce the difficulty of structural design and assembly, and improves the versatility of the electric rotary compressor parts. In this application, the intake and exhaust of the oil separator chamber are completed by forming a first connecting channel and a second connecting channel on the shell wall of the first housing. This reduces the number of pipes and utilizes the strength and rigidity of the first housing to mitigate the impact of the airflow and reduce the vibration of the electric rotary compressor.

[0009] In some embodiments, the housing component includes a bracket, the compression component is located between the bracket and the first housing, and one end of the crankshaft passes through the bracket;

[0010] The second bearing is connected to the bracket, and a second exhaust chamber is defined between the second bearing and the bracket. The compression component has a second exhaust port and communicates with the second exhaust chamber. The second exhaust chamber communicates with the first exhaust chamber.

[0011] Specifically, the compression component is provided with an exhaust channel, and the second exhaust chamber is connected to the first exhaust chamber through the exhaust channel.

[0012] Furthermore, the compression component is fixed to the bracket by the second bearing, the end face of the first bearing is clearance-fitted with the first housing, and a first seal is provided between the first bearing and the first housing to seal the first exhaust chamber.

[0013] Optionally, the clearance between the end face of the first bearing and the first housing is between 0.05 mm and 1 mm.

[0014] Optionally, the first seal is a rubber component or an elastic gasket.

[0015] In some specific embodiments, a first receiving cavity is formed between the bracket and the first housing, and a balancing channel is formed on the first housing. One end of the balancing channel is connected to the upper part of the first receiving cavity, and the other end is connected to the first connecting channel.

[0016] Optionally, the electric rotary compressor also includes a first muffler disposed within the first exhaust chamber.

[0017] Optionally, the electric rotary compressor also includes a second muffler disposed within the second exhaust chamber.

[0018] In some embodiments, the first bearing includes: a first flange and a first journal, the first journal having a first center hole, the first flange extending radially outward from the outer peripheral wall of the first journal; one side of the first flange is connected to the cylinder assembly, and the other side is provided with a first external seal between the first flange and the first housing;

[0019] One end of the crankshaft passes through the first central hole, and a first inner seal is provided between the outer peripheral surface of the first journal and the first housing.

[0020] The first exhaust chamber is located radially outside the first journal and between the first flange and the first housing.

[0021] In some embodiments, the electric rotary compressor further includes an inner oil separator tube disposed within the oil separator chamber, the inner cavity of the inner oil separator tube being formed as an outlet chamber communicating with the oil separator outlet;

[0022] The oil separator inlet is located outside the inner oil separator tube and between the two ends of the inner oil separator tube along its length.

[0023] Specifically, the flow area of ​​the air outlet chamber is S1, there is at least one second connecting channel, the sum of the flow areas of all the second connecting channels is S2, and S2 accounts for 25% to 60% of S1.

[0024] Furthermore, an oil storage chamber is defined within the housing component, and an oil return hole communicating with the oil storage chamber is provided at the lower end of the oil distribution chamber.

[0025] Furthermore, the flow area of ​​the air outlet chamber is S1, the oil return hole is at least one, the sum of the flow areas of all the oil return holes is S3, and S3 accounts for 60% to 120% of S1.

[0026] In some embodiments, the electric rotary compressor further includes a filter device disposed within the oil separator chamber, the filter device including a first filter element located between the oil separator outlet and the oil separator inlet.

[0027] In some embodiments, the oil inlet extends tangentially along the oil separator cavity.

[0028] Specifically, the oil separation chamber is formed within the shell wall of the first housing.

[0029] Furthermore, the oil separator chamber is located on the side of the first exhaust chamber away from the second bearing.

[0030] The present invention also proposes an air conditioning system.

[0031] An air conditioning system according to an embodiment of the present invention includes an electric rotary compressor as described in any of the above embodiments.

[0032] The present invention also proposes a vehicle.

[0033] A vehicle according to an embodiment of the present invention includes: a vehicle body and an air conditioning system mounted on the vehicle body, wherein the air conditioning system is the air conditioning system described in the above embodiment.

[0034] The vehicle and the air conditioning system have the same advantages over the prior art as the electric rotary compressor described above, and will not be repeated here.

[0035] Additional aspects and advantages of the 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

[0036] The above and / or additional aspects and advantages of the present invention will become apparent and readily understood from the description of the embodiments taken in conjunction with the following drawings, in which:

[0037] Figure 1 This is a cross-sectional schematic diagram of an electric rotary compressor (omitting parts such as the motor) according to an embodiment of the present invention;

[0038] Figure 2 This is a cross-sectional schematic diagram of an electric rotary compressor (omitting parts such as the motor) according to another embodiment of the present invention;

[0039] Figure 3 This is a cross-sectional schematic diagram of the first housing according to yet another embodiment of the present invention;

[0040] Figure 4 This is a schematic diagram of a vehicle according to an embodiment of the present invention.

[0041] Figure label:

[0042] Vehicle 1000, Air Conditioning System 1001;

[0043] 100-type electric rotary compressor;

[0044] Compression component 101, cylinder assembly 12, cylinder 121, partition plate 122, crankshaft 14;

[0045] First bearing 15, first flange 151, first journal 152, second bearing 16, second flange 161, second journal 162, first muffler 17, second muffler 18;

[0046] Housing component 102;

[0047] First housing 21, refrigerant outlet 213, mating wall 22, first convex ring 221, second convex ring 222, second housing 23;

[0048] Oil separation chamber 30, oil separation inlet 31, first connecting channel 32, oil separation outlet 33, second connecting channel 34, oil return hole 39;

[0049] First exhaust chamber 41, second exhaust chamber 42, exhaust channel 43, balance channel 44;

[0050] Oil separator inner pipe 52, air outlet chamber 521, cyclone chamber 522, first pipe section 523, second pipe section 524, third pipe section 525;

[0051] First seal 61, first outer seal 611, first inner seal 612, second outer seal 621, second inner seal 622;

[0052] Bracket 70;

[0053] First receiving cavity 81, oil storage cavity 812, and second receiving cavity 82. Detailed Implementation

[0054] Embodiments of the present invention are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention, and should not be construed as limiting the present invention.

[0055] In the description of this invention, it should be understood that the terms "center," "longitudinal," "lateral," "length," "width," "upper," "lower," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "axial," "radial," and "circumferential," etc., indicating orientation or positional relationships, are based on the orientation or positional relationships shown in the accompanying drawings and are only for the convenience of describing the invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of the invention. Furthermore, features defined with "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this invention, unless otherwise stated, "a plurality of" means two or more.

[0056] In the description of this invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "linking" 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; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this invention based on the specific circumstances.

[0057] An electric rotary compressor 100 according to an embodiment of the present invention will now be described with reference to the accompanying drawings.

[0058] According to an embodiment of the electric rotary compressor 100 of the present invention, refer to Figure 1 and Figure 2 It includes: housing component 102 and compression component 101.

[0059] The housing component 102 includes a first housing 21 on which a refrigerant outlet 213 is formed, and at least a portion of the compression component 101 is housed within the first housing 21.

[0060] Specifically, the housing component 102 further includes a second housing 23, with an inner cavity formed between the second housing 23 and the first housing 21, and the compression component 101 located within the inner cavity. In some embodiments, the housing component 102 also includes a bracket 70, which is connected to at least one of the second housing 23 and the first housing 21, and the bracket 70 is at least partially located within the inner cavity. In some examples, such as... Figure 1As shown, the second housing 23, the first housing 21, and the bracket 70 are all independently machined parts, with the second housing 23 and the first housing 21 connected to opposite sides of the bracket 70. In other examples, the bracket 70 is an independently machined part and is integrally placed within the inner cavity, connected to the second housing 23 or the first housing 21. In still other examples, the bracket 70 is integrally formed on the second housing 23. When the housing component 102 includes the bracket 70, a first receiving cavity 81 is formed between the bracket 70 and the first housing 21, and a second receiving cavity 82 is formed between the bracket 70 and the second housing 23. The first receiving cavity 81 and the second receiving cavity 82 can be connected or spaced apart from each other.

[0061] The compression component 101 includes a cylinder assembly 12, a piston (not shown), a crankshaft 13, a first bearing 15 and a second bearing 16. The piston is located inside the cylinder assembly 12. The first bearing 15 and the second bearing 16 are fitted at both ends of the cylinder assembly 12 in the axial direction. The crankshaft 13 is connected to the piston to drive the piston to rotate.

[0062] Specifically, the cylinder assembly 12 includes at least one cylinder 121. Each cylinder 121 has a cylinder chamber and a vane groove, with a reciprocating vane disposed in the vane groove. A crankshaft 14 passes through the cylinder chamber, with an eccentric portion of the crankshaft 14 located within the cylinder chamber. A piston is fitted onto the eccentric portion to rotate eccentrically within the cylinder chamber. One end of the vane abuts against the outer circumferential surface of the piston, dividing the cavity outside the piston within the cylinder into an intake chamber and a compression chamber. The eccentric portion allows the piston to rotate eccentrically, thereby driving the vane to reciprocate within the vane groove. A stop spring is provided within the vane groove, pressing against one end of the vane, thus keeping the other end of the vane in a stop state against the outer circumferential surface of the piston. Of course, other structures can be used instead of the stop spring in this application.

[0063] Of course, the type of compression component 101 in this application is not limited to this. In some designs, one end of the slide is rotatably connected to the piston, so the slide oscillates back and forth within the cylinder assembly 12. Inside the cylinder chamber and outside the piston, one side of the slide is the intake chamber. The pump inlet of the compression component 101 is connected to the refrigerant inlet of the housing component 102 or the low-pressure chamber within the housing component 102 to draw in low-pressure refrigerant gas, so the pressure in the intake chamber is relatively low. The other side of the slide is the compression chamber. After the gas is compressed by the compression chamber, it is discharged from the pump outlet. The pressure in the compression chamber is higher than the pressure in the intake chamber. The discharged gas is discharged to the oil separator 30 for gas-liquid separation and then discharged from the refrigerant outlet 213 of the housing component 102. The cylinder assembly 12 is provided with a first bearing 15 and a second bearing 16 on both axial sides to seal the compression chamber and the intake chamber.

[0064] In some embodiments, the compression component 101 has a single-cylinder structure, that is, the cylinder assembly 12 includes a cylinder 121, and the first bearing 15 and the second bearing 16 are fitted at both ends of the cylinder 121 along its axial direction. In this case, the compression component 101 may have an exhaust port, referred to as the first exhaust port.

[0065] In other embodiments, such as Figure 1 and Figure 2 As shown, the compression component 101 has a multi-cylinder structure, meaning the cylinder assembly 12 includes at least two cylinders 121, with a partition 122 between adjacent cylinders 121. The first bearing 231 and the second bearing 232 are located on the side of the outermost two cylinders 121 furthest from each other. The multiple cylinder chambers of this compression component 101 can be in series, such as multiple cylinders 121 arranged sequentially in a left-right direction, with the compression component 101 forming a first exhaust port at its right end. In the left-to-right direction, the left cylinder pump intake port draws in air, then compresses the fluid and exhausts it from the pump outlet. The pump outlet of the left cylinder connects to the pump intake port of the right cylinder, and the gas is discharged into the right cylinder chamber for further compression, thereby increasing the gas pressure. The multiple cylinder chambers can also be in parallel, such as... Figure 1 In the example, the pump inlets of multiple cylinders are connected in parallel, respectively connected to the refrigerant inlet of the housing component 102 or the low-pressure chamber within the housing component 102. The pump outlets of multiple cylinders are also connected in parallel, respectively connected to the exhaust chamber. That is, the fluid in each cylinder, after compression, is not compressed further, but is discharged to the exhaust chamber and then enters the oil separator 30 for oil-gas separation. Therefore, in the multi-cylinder structure, the compression component 101 may have only one exhaust port, and the pump outlets of multiple cylinders 121 are all connected to this exhaust port, which is called the first exhaust port. The compression component 101 may also have multiple exhaust ports, with each pump outlet of multiple cylinders 121 selecting a suitable exhaust port. When the compression component 101 has exhaust ports at both axial ends, the exhaust port located on the first bearing 15 is called the first exhaust port, and the exhaust port located on the second bearing 16 is called the second exhaust port.

[0066] Of course, the electric rotary compressor 100 in this application also includes a motor (not shown in the figure). The motor is located inside the housing component 102 and connected to the crankshaft 14, and drives the piston to do work by rotating the crankshaft 14. Here, the inner cavity defined between the first housing 21 and the second housing 22 can be a high-pressure cavity connected to the refrigerant outlet 213 or a low-pressure cavity connected to the refrigerant inlet. Alternatively, the inner cavity can be divided by the bracket 70, with one side being a high-pressure cavity and the other side being a low-pressure cavity. Therefore, the motor and the compression component 101 can both be located in the high-pressure cavity, or both can be located in the low-pressure cavity, or the compression component 101 can be located in the high-pressure cavity and the motor in the low-pressure cavity; no limitation is made here. Since the motor is a known structure in the prior art, its structure and working principle will not be described in detail here.

[0067] It should be noted that the terms "high pressure" and "low pressure" mentioned in this invention do not refer to specific pressure values, but rather to indicate the pressure difference between two chambers. For example, in Figure 1 In the example, with the bracket 70 spaced apart, the second receiving cavity 82 between the bracket 70 and the second housing 23 is connected to the refrigerant inlet, resulting in a lower pressure, and is called the low-pressure cavity. The first receiving cavity 81 formed between the bracket 70 and the first housing 21 is connected to the refrigerant outlet 213, resulting in a cavity pressure higher than that of the second receiving cavity 82, and is therefore called the high-pressure cavity 81.

[0068] Reference Figure 1 and Figure 2 The first housing 21 is provided with an oil separator 30. A first connecting channel 32 and a second connecting channel 34 are formed within the housing wall of the first housing 21. The oil outlet 33 of the oil separator 30 is connected to the refrigerant outlet 213 through the first connecting channel 32. It should be noted that the phrase "the first housing 21 is provided with an oil separator 30" should be interpreted broadly. For example, it could include: the oil separator 30 being defined by a pipe body assembled on the first housing 21, i.e., the first housing 21 and the pipe body are separate designs, thus facilitating the free design of the axis and cross-sectional area of ​​the oil separator 30 defined by the pipe body to meet different design requirements. Alternatively, it could also include: Figure 1 and Figure 2 As shown, the oil separator 30 can be integrally formed on the first housing 21, so that the oil separator 30 does not need to be assembled separately, which helps to simplify the production steps.

[0069] Specifically, such as Figure 1 and Figure 2 As shown, a first exhaust chamber 41 is defined between the first bearing 15 and the first housing 21. The compression component 101 has a first exhaust port and is connected to the first exhaust chamber 41. The oil inlet 31 of the oil separator 30 is connected to the first exhaust chamber 41 through the second connecting channel 34.

[0070] Understandably, the compression component 101 requires lubricating oil to operate, and the refrigerant discharged will be mixed with lubricating oil. The oil separator 30 is designed to separate the lubricating oil mixed in the refrigerant, preventing the electric rotary compressor 100 from discharging too much lubricating oil. This ensures that there is sufficient lubricating oil inside the electric rotary compressor 100 and also prevents excessive lubricating oil from accumulating in other pipelines and structures outside the electric rotary compressor 100, thus avoiding obstruction of flow channels. The lubricating oil separated by the oil separator 30 facilitates oil return from the electric rotary compressor 100, thereby improving the performance of the electric rotary compressor 100.

[0071] During the actual operation of the electric rotary compressor 100, the mixture of gaseous refrigerant and lubricating oil discharged from the compression chamber can be discharged through the first exhaust port. This mixture then enters the oil separator chamber 30 via the second connecting channel 34 and the oil separator inlet 31. In the oil separator chamber 30, the mixture undergoes gas-liquid separation, meaning the gaseous refrigerant and lubricating oil are separated. Next, the gaseous refrigerant enters the first connecting channel 32 via the oil separator outlet 33 and is discharged through the refrigerant outlet 213, thus achieving the exhaust of the electric rotary compressor 100. The lubricating oil returns to the compression component 101 to lubricate and protect the moving parts, ensuring the efficient and reliable operation of the electric rotary compressor 100.

[0072] Optionally, such as Figure 2 As shown, the housing component 102 defines an oil storage chamber 812. The lubricating oil separated by the oil separator 30 returns to the oil storage chamber 812 through the oil return hole 39, and can then be supplied to the compression component 101 via the oil storage chamber 812. Alternatively, the oil separator 30 can also supply the separated lubricating oil directly to the compression component 101 via other oil discharge paths.

[0073] In this application, a first exhaust chamber 41 is defined between the first bearing 15 and the first housing 21. The compression component 101 discharges high-pressure fluid into the first exhaust chamber 41, and then into the oil separator 30 for gas-liquid separation. This design avoids a strong correlation between the structural and positional parameters of the oil separator 30 and the second bearing 16, as the oil separator 30 does not directly receive air from the exhaust chamber at the second bearing 16. Furthermore, since the second bearing 16 is located in the middle of the housing component 102, modifications to the exhaust and oil separator structures have minimal impact on the structure located in the middle of the housing component 102. For example, in... Figure 1 and Figure 2 In the example, when the volume of the first exhaust chamber 41 and the oil separator chamber 30 needs to be increased or decreased, the second housing 23, the bracket 70, and the structure between them of the electric rotary compressor 100 can remain unchanged, and the structure and parameters of the compression component 101 can also remain unchanged. Only the structural parameters of the first housing 21 and the oil separator chamber 30 need to be changed to adjust the volume of the first exhaust chamber 41 and the oil separator chamber 30. Therefore, this structural solution of the present application can reduce the difficulty of structural modification and also help to reduce the assembly difficulty. The parts of this electric rotary compressor 100 are highly versatile and have a wide range of applications.

[0074] It is understandable that in this application, by utilizing the shell wall of the first housing 21 to form the first connecting channel 32, the gaseous refrigerant separated by the oil separator 30 is directly discharged to the refrigerant outlet 213 via the first connecting channel 32, instead of the oil separator outlet 33 of the oil separator 30 venting to the refrigerant outlet 213 through the first receiving cavity 81. This reduces the external impact of high-pressure airflow on the compression component 101, thus reducing vibration. On the other hand, since the first receiving cavity 81 surrounds the compression component 101, lubricating oil inevitably flows out at the joints of the components. Reducing the flow of high-pressure airflow through the first receiving cavity 81 can reduce the amount of lubricating oil carried away by the airflow. In some solutions, part of the first receiving cavity 81 is the oil storage cavity 812. If the exhaust carries away the lubricating oil stored in the first receiving cavity 81, it will reduce the oil separation efficiency of the initial gas-liquid separation using the oil separator 30. Therefore, this application directly uses the first connecting channel 32 to exhaust the refrigerant outlet 213 from the oil separator 30, which is beneficial to maintaining a higher oil-gas separation rate.

[0075] Another understandable reason is that, due to the limitations of the pump body structure in existing rotary compressors, the compression component is located in the center of the first receiving chamber, making it difficult to align the oil separator chamber coaxially with the refrigerant outlet. This limitation often leads to problems with the oil separator chamber of rotary compressors, such as difficulty in machining, insufficient diameter, and installation challenges.

[0076] In the embodiments of the present invention, by providing a first connecting channel 32 within the shell wall (i.e., within the wall thickness space) of the first housing 21, and by connecting the oil separator outlet 33 and the refrigerant outlet 213, the direct connection between the oil separator outlet 33 and the refrigerant outlet 213 can be avoided. This ensures that the size and position of the refrigerant outlet 213 do not affect the oil separator chamber 30. For example, the axis and cross-sectional area of ​​the first connecting channel 32 can be freely designed, and the refrigerant outlet 213 can also be flexibly designed to meet different design requirements. Therefore, the oil separator chamber 30 can achieve optimal oil separation efficiency, ensuring oil return lubrication requirements under high load conditions and other situations, reducing gas leakage or refrigerant leakage, thereby improving the cooling capacity and compression efficiency of the electric rotary compressor 100, and even meeting the reliability requirements of the electric rotary compressor 100.

[0077] In this application, by utilizing the shell wall of the first housing 21 to form a second connecting channel 34, the airflow in the first exhaust chamber 41 is discharged to the oil separator chamber 30 through the second connecting channel 34, which helps to reduce the number of pipes. The connection relationship between the first connecting channel 32, the second connecting channel 34, and the oil separator chamber 30 ensures the controllability of the fluid inflow and outflow direction in the oil separator chamber 30. Furthermore, this arrangement ensures that both the air inlet and outlet positions of the oil separator chamber 30 are connected to the first housing 21, utilizing the strength and rigidity of the first housing 21 to resist the impact of airflow and reduce the vibration of the electric rotary compressor 100.

[0078] Furthermore, instead of exhausting gas from the first exhaust chamber 41 to the first receiving chamber 81 and then supplying gas from the first receiving chamber 81 to the oil separator 30, a second connecting channel 34 is formed using the shell wall of the first housing 21, thus facilitating the maintenance of airflow velocity. In some embodiments of this application, the mixed fluid flows circumferentially within the oil separator 30, and centrifugal force throws the lubricating oil out of the gaseous refrigerant, completing gas-liquid separation. The higher the flow velocity of the mixed liquid, the stronger the centrifugal force, and the better the gas-liquid separation effect. Therefore, supplying gas from the first exhaust chamber 41 to the oil separator 30 through the second connecting channel 34 helps maintain a better gas-liquid separation effect.

[0079] By forming the second connecting channel 34 on the shell wall of the first housing 21, rather than on the first bearing 15, direct connection between the oil separator structure and the compression component 101 can be avoided. Especially when the oil separator structure includes a pipe, reducing the large-scale vibration of the pipe caused by the vibration of the compression component 101 helps to ensure the reliability of the pipe connection and reduces the probability of breakage and leakage at the connection.

[0080] In summary, the electric rotary compressor 100 according to the embodiments of the present invention forms a first exhaust chamber 41 between the first bearing 15 and the first housing 21. The compression component 101 discharges the compressed high-pressure fluid into the first exhaust chamber 41, and then into the oil separator 30 for gas-liquid separation. The oil separator 30 does not directly intake air at the middle position (including the second bearing) of the housing component 102, reducing the strong correlation between the oil separator position, the exhaust position and the middle position structure of the housing component 102. The assembly difficulty of the electric rotary compressor 100 is low, and the difficulty of modifying the exhaust structure and the oil separator structure is low, which helps to improve the applicability of the parts of this electric rotary compressor 100. In this application, the intake and exhaust of the oil separator 30 are completed by forming a first connecting channel 32 and a second connecting channel 34 on the shell wall of the first housing 21. On the one hand, the number of pipes is reduced, and on the other hand, the strength and rigidity of the first housing 21 can be used to reduce the vibration caused by the impact of the exhaust airflow of the compression component 101, thereby helping to reduce the vibration and operating noise of the electric rotary compressor 100.

[0081] In some embodiments, such as Figure 1 and Figure 2 As shown, housing component 102 includes a bracket 70, a compression component 101 located between the bracket 70 and the first housing 21, and one end of the crankshaft 13 passing through the bracket 70 to be connected to the motor. A second bearing 16 is connected to the bracket 70, defining a second exhaust chamber 42 between the second bearing 16 and the bracket 70. The compression component 101 has a second exhaust port and communicates with the second exhaust chamber 42, which communicates with the first exhaust chamber 41.

[0082] In other words, the exhaust position of the compression component 101 is not limited to the first bearing 15; a second exhaust port can also be provided on the second bearing 16. This compression component 101 can be a multi-cylinder structure, allowing each cylinder 121 to select an exhaust position nearby, reducing the design complexity of the cylinder 121's exhaust path. Of course, the structure of this application is not limited to this. In some single-cylinder compression components 101, due to large exhaust volume or high exhaust frequency, exhaust positions on both axial sides of the compression component 101 can facilitate rapid exhaust and reduce exhaust resistance.

[0083] Here, although a second exhaust chamber 42 is provided between the second bearing 16 and the bracket 70, the fluid in the second exhaust chamber 42 is first discharged to the first exhaust chamber 41, and then the mixed fluid enters the oil separator 30 through the second connecting channel 341 for gas-liquid separation. The fluid in the second exhaust chamber 42 is not directly discharged to the first receiving chamber 81, which reduces the external impact of high-pressure gas on the compression component 101 and also reduces the amount of lubricating oil carried away.

[0084] Furthermore, in some embodiments of this application, the mixed fluid achieves gas-liquid separation by generating different centrifugal forces through circumferential flow within the oil separator 30. Therefore, the second exhaust chamber 42 supplies gas to the oil separator 30 via the first exhaust chamber 41, which helps maintain the flow velocity of the mixed fluid and ensures the gas-liquid separation effect.

[0085] Specifically, such as Figure 2 As shown, the compression component 101 is provided with an exhaust channel 43, and the second exhaust chamber 42 is connected to the first exhaust chamber 41 through the exhaust channel 43. Of course, the structure of the present application is not limited to this. The exhaust channel 43 can also be formed in the shell wall of the first housing 21, or a pipe can be provided in the first receiving cavity 81, with one end of the pipe connected to the first exhaust chamber 41 and the other end connected to the second exhaust chamber 42.

[0086] Compared to the other two options, directly setting the exhaust channel 43 inside the compression component 101 can shorten the exhaust path, reduce the difficulty of assembly sealing, and reduce the number of parts.

[0087] In this application, the arrangement of the oil separator chamber 30 is not limited. For example, in some embodiments, as described above, the oil separator chamber 30 is defined by a tube mounted on the first housing 21. Specifically, an outer oil separator tube (not shown in the figure) is mounted on the first housing 21, and the inner cavity of the outer oil separator tube forms at least a portion of the oil separator chamber 30. That is, the outer oil separator tube and the first housing 21 are separate structures, and the outer oil separator tube is inserted into the first housing 21. Thus, it is not necessary to process the oil separator chamber 30 on the first housing 21, reducing the structural and wall thickness requirements of the first housing 21, and the first housing 21 can be designed flexibly.

[0088] In some specific embodiments, the lower end of the outer pipe has a tapered tube, and the lower port of the tapered tube is connected to the oil return hole 39.

[0089] For example, the axial cross-sectional shape of the wall of a tapered tube can be constructed as a straight line, or the axial cross-sectional shape of the wall of a tapered tube can be constructed as an arc, without limitation.

[0090] For example, the inner diameter of the end of the tapered tube connected to the outer oil separator tube is the same as the inner diameter of the outer oil separator tube, that is, the inner diameter of the end of the tapered tube connected to the outer oil separator tube is the same as the inner diameter of the oil separator cavity 30. This allows lubricating oil to enter the tapered tube along the cavity wall of the oil separator cavity 30. In the direction of lubricating oil flow, the inner diameter of the tapered tube gradually decreases, so that a return oil hole 39 is connected at the end of the tapered tube away from the outer oil separator tube. Optionally, the diameter of the return oil hole 39 is smaller than the inner diameter of the oil separator cavity 30.

[0091] Therefore, by setting up a tapered tube, the inner wall of the tapered tube, whose inner diameter gradually decreases, can guide and converge the lubricating oil as it flows towards the return oil hole 39, thereby improving the reliability of the return oil.

[0092] In other embodiments of this application, such as Figure 3 As shown, an oil separator cavity 30 is formed within the shell wall of the first housing 21. In other words, the oil separator cavity 30 is integrally formed on the first housing 21, or the first housing 21 itself can form a complete oil separator cavity 30. This eliminates the need for assembling the outer oil separator pipe, reduces the number of parts, lowers costs, simplifies production processes, and improves production efficiency.

[0093] Specifically, a portion of the shell wall of the first housing 21 is thicker to form the oil separator chamber 30; this portion is called the mating wall 22, and the oil separator inlet 31 is formed on the mating wall 22. Furthermore, the first connecting channel 32, the oil separator outlet 33, and the second connecting channel 34 are also formed on the mating wall 22. Even further, a refrigerant outlet 213 is formed on the mating wall 22; optionally, the refrigerant outlet 213 is located at the top of the mating wall 22.

[0094] Furthermore, the oil separator 30 is located on the side of the first exhaust chamber 41 furthest from the second bearing 16. For example... Figure 1 and Figure 2 In the first housing 21, the shell wall opposite to the bracket 70 is the mating wall 22. In this way, the exhaust structure and the oil separation structure are concentrated at the same end of the housing component 102. On the one hand, the length of the exhaust path and the oil return path is shortened, and on the other hand, there is less interference with the compression component 101 during assembly, which reduces the design difficulty and facilitates assembly.

[0095] In some specific embodiments, such as Figure 1 and Figure 2As shown, the compression component 101 is fixed to the bracket 70 via the second bearing 16, and the end face of the first bearing 15 is clearance-fitted with the first housing 21. For example, the compression component 101 can be rigidly connected and fixed to the bracket 70 by bolts, while the compression component 101 remains fixed within the housing component 102 when the bracket 70 is fixed to the first housing 21 or the second housing 23. In this case, a gap can be maintained between the end face of the first bearing 15 and the first housing 21 to avoid over-positioning that could cause interference between the end faces of the first housing 21 and the first bearing 15, resulting in a higher defect rate.

[0096] When there is a gap between the end face of the first bearing 15 and the first housing 21, a first sealing element 61 can be provided between the first bearing 15 and the first housing 21 to achieve the separation between the first exhaust chamber 41 and the first receiving chamber 81.

[0097] Optionally, the fit clearance between the end face of the first bearing 15 and the first housing 21 is between 0.05mm and 1mm. This reasonable setting of the clearance width ensures that the two do not interfere with each other and reduces the difficulty of sealing at the gap.

[0098] When setting the first seal 61, it is best to use a seal with strong elasticity, such as a rubber component or an elastic gasket. Utilizing its strong elasticity, the first seal 61 can adapt to any significant fluctuations in the aforementioned fit clearance due to machining errors. Furthermore, it easily ensures that the first seal 61, the first bearing 15, and the first housing 21 are all in a compressed state, improving sealing reliability.

[0099] Using rubber components and elastic gaskets can extend its service life. Of course, the first seal 61 can also use other seals with strong elasticity, such as silicone rings.

[0100] In some specific embodiments, such as Figure 1 and Figure 2As shown, the first bearing 15 includes a first flange 151 and a first journal 152. The first journal 152 has a first central hole, and the first flange 151 extends radially outward from the outer peripheral wall of the first journal 152. A cylinder assembly 12 is connected to one side of the first flange 151, and a first outer seal 611 is provided between the other side and the first housing 21. One end of the crankshaft 13 passes through the first central hole, and a first inner seal 612 is provided between the outer peripheral surface of the first journal 152 and the first housing 21. A first exhaust chamber 41 is located radially outward of the first journal 152 and between the first flange 151 and the first housing 21. This prevents high-pressure gas from leaking out from the first central hole. The first outer seal 611 and the first inner seal 612 facilitate assembly and provide sufficient volume space for the first exhaust chamber 41. Furthermore, the first bearing 15 is supported at the first outer seal 611 and the first inner seal 612.

[0101] Specifically, such as Figures 1-3 As shown, the mating wall 22 is provided with a first protruding ring 221, the first journal 152 is inserted into the first protruding ring 221, and a first inner seal 612 is provided between the first protruding ring 221 and the first journal 152. Of course, the solution of this application is not limited to this. For example, a groove can be formed on the surface of the mating wall 22 facing the first bearing 15, the first journal 152 is inserted into the groove, and a first inner seal 612 is provided between the first journal 152 and the inner circumferential surface of the groove.

[0102] Specifically, the mating wall 22 has a second raised ring 222 near its edge, and the end face of the first flange 151 faces the second raised ring 222, such that the diameter of the first flange 151 is larger than the outer diameter of the second raised ring 222. A first external sealing element 611 is provided between the end face of the first flange 151 and the second raised ring 222. With this arrangement, there is less interference between the end face of the first flange 151 and other positions of the mating wall 22, making assembly easier.

[0103] In some specific embodiments, such as Figure 1 and Figure 2 As shown, the second bearing 16 includes a second flange 161 and a second journal 162. The second journal 162 has a second central hole, and the second flange 161 extends radially outward from the outer peripheral wall of the second journal 162. A cylinder assembly 12 is connected to one side of the second flange 161, and a second external seal 621 is provided between the other side and the bracket 70. One end of the crankshaft 13 passes sequentially through the second central hole and into the bracket 70, and a second internal seal 622 is provided between the outer peripheral surface of the second journal 162 and the inner peripheral surface of the bracket 70. The second exhaust chamber 41 is located radially outward of the second journal 162 and between the second flange 162 and the bracket 70. This prevents high-pressure gas from leaking out from the second central hole, thus supporting the second bearing 16.

[0104] In some specific embodiments, such as Figure 2 and Figure 3 As shown, a first receiving cavity 81 is formed between the bracket 70 and the first housing 21. A balance channel 44 is formed on the first housing 21. One end of the balance channel 44 is connected to the first receiving cavity 81, and the other end is connected to the first connecting channel 32. In this way, the high-pressure gaseous refrigerant after gas-liquid separation can be sent to the first receiving cavity 81 through the balance channel 44. The first receiving cavity 81 maintains a high-pressure environment to avoid a small pressure difference between the first receiving cavity 81 and the first exhaust cavity 41, thereby reducing gas leakage in the first exhaust cavity 41.

[0105] Specifically, the bottom of the first receiving cavity 81 forms an oil storage cavity 812, and the balance channel 44 is opened above the oil storage cavity 812. In this way, the oil storage cavity 812 is in a high-pressure state, which facilitates the use of pressure difference to transport the lubricating oil in the oil storage cavity 812 to the compression component 101 for lubrication.

[0106] Optionally, the balance channel 44 is formed on the shell wall of the first housing 21 in a direction parallel to the axis of the compression member 101, thereby facilitating processing.

[0107] Of course, as described above, the oil return method in this application is not limited to the oil storage chamber 812. In some designs, one end of the oil return hole 39 is located inside the first convex ring 221, and lubricating oil is forced into the compression component 101 from the shaft hole of the crankshaft 14 or the outer circumferential surface of the crankshaft 14 using pressure difference. Optionally, a throttling structure (throttle valve) is provided in the oil return hole 39, or the flow area of ​​the oil return hole 39 is set to be small, so that the oil return flow rate can be properly controlled during oil return, which is beneficial to matching the oil return speed with the gas-oil separation speed.

[0108] In some optional embodiments of this application, the electric rotary compressor 100 further includes a first silencer 17 disposed within the first exhaust chamber 41, with a first silencer cavity formed between the first bearing 15 and the first silencer 17, thereby reducing exhaust noise from the airflow in the compression component 101 discharged to the first exhaust chamber 41. Optionally, the first silencer 17 may be provided in one or more layers.

[0109] In some alternative embodiments of this application, the electric rotary compressor 100 further includes a second silencer 18 disposed within the second exhaust chamber 42. A second silencer chamber is formed between the second bearing 16 and the second silencer 18, thereby reducing exhaust noise from the airflow in the compression component 101 discharged to the second exhaust chamber 42. Optionally, the second silencer 18 may be provided in one or more layers.

[0110] In some embodiments, such as Figure 2 As shown, the oil separator inlet 31 extends tangentially along the oil separator chamber 30. This facilitates the circumferential rotation of the fluid within the oil separator chamber 30, achieving the effect of cyclone separation.

[0111] Of course, the present invention is not limited to this. It may not utilize tangential entry to achieve cyclone separation. For example, a filter device (not shown in the figure) may be installed in the oil separator 30 to achieve oil-gas separation through filtration. Alternatively, both cyclone separation and a filter device may be used.

[0112] Optionally, the filtration device includes a first filter element located between the oil separator outlet 33 and the oil separator inlet 31. This allows all unseparated gas-liquid mixture to be blocked below the first filter element, ensuring that all fluid is filtered before discharge. The location of the first filter element facilitates assembly and inspection during maintenance.

[0113] Alternatively, the filter device may employ a filter screen structure to reduce flow resistance.

[0114] In some alternative embodiments, the first filter element is a sheet-like shape, with its edge fixed to the inner wall of the oil separator 30, and the middle portion of the first filter element protruding downwards, which helps the mixed fluid to swirl and flow within the oil separator 30.

[0115] In some embodiments, such as Figures 1-3 As shown, the electric rotary compressor 100 also includes an inner oil separator tube 52 disposed within the oil separator chamber 30. The inner cavity of the inner oil separator tube 52 is formed into an outlet chamber 521 communicating with the oil separator outlet 33. A cyclone chamber 522 is formed between the oil separator chamber 30 and the inner oil separator tube 52. The oil separator inlet 31 is located outside the inner oil separator tube 52 and between its two ends in the longitudinal direction of the inner oil separator tube 52, such that the oil separator inlet 31 is positioned facing the cyclone chamber 522. Thus, the cyclone chamber 522 provides space for the exhaust gas to enter and rotate.

[0116] Here, placing the oil separator inlet 31 between the two ends along the length of the oil separator inner tube 52 helps to drive the entire mixed flow to rotate and flow along the swirl separation space, thereby improving the gas-liquid separation effect.

[0117] Further extending the oil separator inlet 31 tangentially along the oil separator chamber 30 can further facilitate the circumferential cyclone rotation of the mixed fluid, achieving gas-liquid separation of lubricating oil and gaseous refrigerant. It is understood that the larger the rotation radius of the fluid, the greater the centrifugal force generated. Extending the oil separator inlet 31 tangentially along the oil separator chamber 30 ensures that the fluid entering the oil separator chamber 30 from the inlet 31 is immediately guided to rotate by the inner wall of the chamber. Moreover, the fluid maintains a large rotation radius upon entry, allowing the lubricating oil liquid in the mixed fluid to be ejected from the gas and flow along the oil separator chamber 30, while the gaseous refrigerant, due to its smaller mass, quickly enters the outlet chamber 521 from the bottom and is discharged. Furthermore, extending the oil separator inlet 31 tangentially along the oil separator chamber 30 reduces excessive disturbance between the newly entering fluid and the rotating fluid, allowing more fluid to maintain rotation around the cyclone chamber 522.

[0118] Optionally, the cyclone cavity 522 is annular, so that the outer circumferential surface of the part of the oil separator inner pipe 52 that forms the cyclone cavity 522 is cylindrical, which is easy to process. Moreover, the annular shape of the cyclone cavity 522 can maximize the use of this space and make the flow generate a larger rotation radius.

[0119] In some specific embodiments, such as Figure 2 As shown, the oil separator inner pipe 52 includes a first pipe section 523, a second pipe section 524, and a third pipe section 525 connected sequentially along its length. The first pipe section 523 is adjacent to the first connecting channel 32.

[0120] Specifically, the diameter of the second pipe section 524 gradually decreases from the first pipe section 523 to the third pipe section 525. The first pipe section 523 has a large diameter, facilitating its placement at the oil separator outlet 33. The third pipe section 525 has a relatively small diameter, facilitating the formation of a cyclone chamber 522 between it and the inner wall of the oil separator chamber 30. The gradually decreasing diameter structure of the second pipe section 524 facilitates manufacturing.

[0121] More specifically, during assembly, the inner pipe 52 of the oil separator is inserted from the refrigerant outlet 213, and the first pipe section 523 is interference-fitted at the oil separator outlet 33.

[0122] In some specific embodiments, the section of the oil separator chamber 30 connected to the oil separator outlet 33 is a cylindrical cavity. The inner oil separator pipe 52 includes a first pipe section 523, a second pipe section 524, and a third pipe section 525 connected in sequence. The first pipe section 523 and the third pipe section 525 are circular pipes, and the second pipe section 524 is a tapered pipe whose diameter gradually decreases towards the third pipe section 525. The outer diameter of the third pipe section 525 is smaller than the inner diameter of the cylindrical cavity of the oil separator chamber 30, and the two are coaxially arranged. A ring-shaped cyclone cavity 522 is formed around the third pipe section 525. One end of the second connecting channel 34 forms an oil separator inlet 31 and is arranged tangentially along the cyclone cavity 522. The axis of the second connecting channel 34 is perpendicular to the axis of the inner oil separator pipe 52. Figure 2 In the example shown, the cross-section presented in the attached figure passes through the axis of the inner oil separator pipe 52. Figure 1 and Figure 3 In the example shown, the cross section presented in the attached figure passes through the axis of the second connecting channel 34.

[0123] Furthermore, there is at least one second connecting channel 34. When there are at least two second connecting channels 34, the second connecting channels 34 are distributed sequentially along the axis of the inner oil separator pipe 52. In this way, the fluid discharged from the first exhaust chamber 41 can be divided into at least two streams, which are guided as much as possible. The circulation formed by the two streams is distributed sequentially along the axis of the inner oil separator pipe 52, thus making full use of the space of the cyclone chamber 522.

[0124] Optionally, such as Figure 2 As shown, the distance L between the oil separator inlet 31 and the end of the oil separator inner tube 52 furthest from the oil separator outlet 33 is at least 5 mm, which is conducive to the fluid rotating at least once in the cyclone chamber 522.

[0125] Specifically, the flow area of ​​the exhaust chamber 521 is S1, there is at least one second connecting channel 4, and the sum of the flow areas of all second connecting channels 34 is S2, satisfying that S2 accounts for 25% to 60% of S1. Optionally, the ratio of S2 to S1 can be 25%, 30%, 40%, 45%, 50%, 55%, 58%, 60%, etc. This ensures that the inlet diameter of the oil separator 30 is sufficient and the tangential rotational force is sufficient, thereby improving the efficiency of cyclone separation of refrigerant and lubricating oil, and improving exhaust efficiency and oil return efficiency.

[0126] In some specific embodiments, such as Figure 2 and Figure 3 As shown, the housing component 102 defines an oil storage chamber 812, and the lower end of the oil distribution chamber 30 is provided with an oil return hole 39 that connects to the oil storage chamber 812, thereby reducing the possibility of gaseous refrigerant leaking into the oil storage chamber 812 and causing oil supply interruption.

[0127] Optionally, the oil return hole 39 is disposed on the first housing 21 in a direction parallel to the axis of the compression component 101, and is disposed near the bottom of the oil storage chamber 812.

[0128] Specifically, the flow area of ​​the exhaust chamber 521 is S1, there is at least one oil return hole 39, and the sum of the flow areas of all oil return holes 39 is S3, satisfying that S3 accounts for 60% to 120% of S1. Optionally, the ratio of S3 to S1 can be 60%, 63%, 70%, 75%, 80%, 82%, 88%, 90%, 95%, 100%, 110%, 115%, 120%, etc.

[0129] This ensures that the returned oil can flow back to the oil storage chamber 812 as soon as possible, reducing the oil storage in the oil separator chamber 30, freeing up space for airflow, and reducing the amount of lubricating oil carried away by the refrigerant gas.

[0130] In some embodiments, such as Figures 1-3 As shown, the oil separator 30 is a vertically extending long cavity, which can be a vertical straight line or an inclined extension, and the axis of the oil separator 30 can also be a curve.

[0131] Optionally, the lower end of the oil separator 30 has a tapered cavity, and the lower port of the tapered cavity is connected to the oil return hole 39. By setting the tapered cavity, the inner wall of the tapered cavity, whose inner diameter gradually decreases, can guide and converge the lubricating oil as it flows towards the oil return hole 39, thereby improving the reliability of the oil return.

[0132] For example Figure 1 As shown, in the axial direction of the oil separator chamber 30, the converging chamber is located below the oil separator outlet 33, and the oil return hole 39 is also located below the oil separator outlet 33. It should be noted that since the refrigerant is gaseous and the lubricating oil is liquid, after the mixture of gaseous refrigerant and lubricating oil discharged from the compression chamber enters the oil separator chamber 30, the lubricating oil will flow downwards under its own gravity to the oil return hole 39, while the gaseous refrigerant will flow upwards to the oil separator outlet 33, thus separating the two and achieving the discharge and oil return of the electric rotary compressor 100.

[0133] In some embodiments, such as Figures 1-3 As shown, the axis of the first housing 21 extends laterally, the first connecting channel 32 is located at the top of the first housing 21 and extends vertically, the upper end of the first connecting channel 32 penetrates the top of the first housing 21 to form a refrigerant outlet 213, and the oil separator 30 extends downward at an angle from the lower end of the first connecting channel 32.

[0134] For example, the upper end of the first connecting channel 32 extends through the top of the first housing 21 to form a refrigerant outlet 213, which facilitates the processing and shaping of the refrigerant outlet 213. The extension direction of the oil separator 30 is roughly the same as the direction of gravity of the lubricating oil, which is beneficial for the separated lubricating oil to flow quickly along the oil separator 30 to the oil return hole 39 under its own gravity, thereby improving the oil return efficiency of the electric rotary compressor 100.

[0135] Alternatively, the first connecting channel 32 is located diagonally above the compression component 101 and its axis extends vertically. The oil separator 30 extends vertically downward from the lower end of the first connecting channel 32 and is located on the side of the compression component 101. In this case, the compression component 101 can be avoided. Thus, the extension direction of the oil separator 30 is the same as the direction of gravity of the lubricating oil, which is beneficial for the separated lubricating oil to flow quickly along the oil separator 30 to the oil return hole 39 under its own gravity, thereby improving the oil return efficiency of the electric rotary compressor 100.

[0136] It should be noted that the compression component 101 according to the embodiment of the present invention is a rotary compression mechanism, but the specific configuration is not limited, and it can be a single-cylinder compression mechanism or a multi-cylinder compression mechanism. In addition, the electric rotary compressor 100 is a horizontal compressor in which the central axis extends laterally or is slightly inclined to the horizontal line, or it can also be a vertical compressor in which the central axis extends vertically or is slightly inclined to the vertical line, etc.

[0137] The present invention also proposes an air conditioning system 1001.

[0138] like Figure 4 As shown, the air conditioning system 1001 according to an embodiment of the present invention includes the electric rotary compressor 100 described in any of the above embodiments.

[0139] According to an embodiment of the air conditioning system 1001 of the present invention, the electric rotary compressor 100 forms a first exhaust chamber 41 between the first bearing 15 and the first housing 21. The compression component 101 discharges the compressed high-pressure fluid into the first exhaust chamber 41, and then into the oil separator 30 for gas-liquid separation. The oil separator 30 does not directly intake air at the middle position (including the second bearing) of the housing component 102, reducing the strong correlation between the oil separator position, the exhaust position and the middle position structure of the housing component 102. The assembly difficulty of the electric rotary compressor 100 is low, and the difficulty of modifying the exhaust structure and the oil separator structure is low, which helps to improve the applicability of the parts of this electric rotary compressor 100. In this application, the intake and exhaust of the oil separator 30 are completed by forming a first connecting channel 32 and a second connecting channel 34 on the shell wall of the first housing 21. On the one hand, the number of pipes is reduced, and on the other hand, the strength and rigidity of the first housing 21 can be used to reduce the vibration caused by the impact of the exhaust airflow of the compression component 101, thereby helping to reduce the vibration and operating noise of the electric rotary compressor 100. This is beneficial for noise reduction and high-efficiency operation of the air conditioning system 1001.

[0140] The present invention also proposes a vehicle 1000.

[0141] like Figure 4 As shown, a vehicle 1000 according to an embodiment of the present invention includes: a vehicle body and an air conditioning system 1001 mounted on the vehicle body, wherein the air conditioning system 1001 is the air conditioning system 1001 described in the above embodiment.

[0142] According to an embodiment of the vehicle 1000 of the present invention, the electric rotary compressor 100 of its air conditioning system 1001 forms a first exhaust chamber 41 between the first bearing 15 and the first housing 21. The compression component 101 discharges the compressed high-pressure fluid into the first exhaust chamber 41, and then into the oil separator 30 for gas-liquid separation. The oil separator 30 does not directly intake air at the middle position (including the second bearing) of the housing component 102, reducing the strong correlation between the oil separator position, exhaust position and the middle position structure of the housing component 102. The assembly difficulty of the electric rotary compressor 100 is low, and the difficulty of modifying the exhaust structure and oil separator structure is low, which helps to improve the applicability of the parts of this electric rotary compressor 100. In this application, the intake and exhaust of the oil separator 30 are completed by forming a first connecting channel 32 and a second connecting channel 34 on the shell wall of the first housing 21. On the one hand, the number of pipes is reduced, and on the other hand, the strength and rigidity of the first housing 21 can be used to reduce the vibration caused by the impact of the exhaust airflow of the compression component 101, thereby helping to reduce the vibration and operating noise of the electric rotary compressor 100. In summary, this is beneficial for reducing vehicle noise by 1000.

[0143] It should be noted that in this invention, the specific type of the vehicle 1000 is not limited. For example, the vehicle 1000 can be a traditional fuel vehicle or a new energy vehicle. The new energy vehicle includes, but is not limited to, pure electric vehicles, range-extended electric vehicles, hybrid electric vehicles, fuel cell electric vehicles, hydrogen engine vehicles, etc.

[0144] In some embodiments, the new energy vehicle can be a pure electric vehicle with an electric motor as the main driving force. In other embodiments, the new energy vehicle can also be a hybrid vehicle with both an internal combustion engine and an electric motor as the main driving force. Regarding the internal combustion engine and electric motor mentioned in the above embodiments that provide driving power for the new energy vehicle, the internal combustion engine can use gasoline, diesel, hydrogen, etc. as fuel, and the method of providing electrical energy to the electric motor can use power batteries, hydrogen fuel cells, etc., without special limitations. It should be noted that this is merely an exemplary description of the structure of new energy vehicles, etc., and is not intended to limit the scope of protection of this invention.

[0145] In the description of this specification, references to terms such as "embodiment," "example," 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 the invention. In this specification, 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.

[0146] Although embodiments of the invention 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 the invention, the scope of which is defined by the claims and their equivalents.

Claims

1. An electric rotary compressor, characterized in that, include: The housing component includes a first housing, on which a refrigerant outlet is formed, and an oil separator chamber is provided in the first housing. A first connecting channel and a second connecting channel are formed in the shell wall of the first housing, and the oil separator outlet of the oil separator chamber is connected to the refrigerant outlet through the first connecting channel. A compression component, at least a portion of which is housed within a first housing, the compression component including a cylinder assembly, a piston, a crankshaft, a first bearing, and a second bearing, the piston being disposed within the cylinder assembly, the first bearing and the second bearing engaging at both axial ends of the cylinder assembly, the crankshaft being connected to the piston to drive the piston to rotate, a first exhaust chamber being defined between the first bearing and the first housing, the compression component having a first exhaust port communicating with the first exhaust chamber, and the oil inlet of the oil separator communicating with the first exhaust chamber through a second communicating channel; The first bearing includes: a first flange and a first journal, the first journal having a first central hole, and the first flange extending radially outward from the outer peripheral wall of the first journal; The first flange is connected to the cylinder assembly on one side, and a first external seal is provided between the other side and the first housing; one end of the crankshaft passes through the first central hole, and a first internal seal is provided between the outer peripheral surface of the first journal and the first housing; The first bearing and the first housing are jointly defined by the first outer seal and the first inner seal to form a first exhaust chamber, which is located radially outside the first journal and between the first flange and the first housing.

2. The electric rotary compressor according to claim 1, characterized in that, The housing component includes a bracket, the compression component is located between the bracket and the first housing, and one end of the crankshaft passes through the bracket; The second bearing is connected to the bracket, and a second exhaust chamber is defined between the second bearing and the bracket. The compression component has a second exhaust port and communicates with the second exhaust chamber. The second exhaust chamber communicates with the first exhaust chamber.

3. The electric rotary compressor according to claim 2, characterized in that, The compression component is provided with an exhaust channel, and the second exhaust chamber is connected to the first exhaust chamber through the exhaust channel.

4. The electric rotary compressor according to claim 2, characterized in that, The compression component is fixed to the bracket by the second bearing. The end face of the first bearing and the first housing are in clearance fit. A first outer seal and a first inner seal are provided between the first bearing and the first housing to seal the first exhaust chamber.

5. The electric rotary compressor according to claim 4, characterized in that, The clearance between the end face of the first bearing and the first housing is between 0.05 mm and 1 mm.

6. The electric rotary compressor according to claim 4, characterized in that, The first outer seal and the first inner seal are rubber parts or elastic gaskets.

7. The electric rotary compressor according to claim 2, characterized in that, A first receiving cavity is formed between the bracket and the first housing. A balancing channel is formed on the first housing. One end of the balancing channel is connected to the upper part of the first receiving cavity, and the other end is connected to the first connecting channel.

8. The electric rotary compressor according to claim 1, characterized in that, It also includes a first muffler disposed in the first exhaust chamber.

9. The electric rotary compressor according to claim 2, characterized in that, It also includes a second muffler located in the second exhaust chamber.

10. The electric rotary compressor according to any one of claims 1-9, characterized in that, It also includes an inner oil separator tube disposed in the oil separator chamber, the inner cavity of the inner oil separator tube being formed as an exhaust chamber communicating with the oil separator outlet, and a cyclone chamber being formed between the oil separator chamber and the inner oil separator tube; The oil separator inlet is located outside the inner oil separator tube and between the two ends of the inner oil separator tube along its length.

11. The electric rotary compressor according to claim 10, characterized in that, The flow area of ​​the air outlet chamber is S1, there is at least one second connecting channel, the sum of the flow areas of all the second connecting channels is S2, and S2 accounts for 25% to 60% of S1.

12. The electric rotary compressor according to claim 10, characterized in that, The housing component defines an oil storage chamber, and the lower end of the oil distribution chamber is provided with an oil return hole that communicates with the oil storage chamber.

13. The electric rotary compressor according to claim 12, characterized in that, The flow area of ​​the air outlet chamber is S1, the oil return hole is at least one, the sum of the flow areas of all the oil return holes is S3, and S3 accounts for 60% to 120% of S1.

14. The electric rotary compressor according to any one of claims 1-9, characterized in that, It also includes a filtration device disposed within the oil separator chamber, the filtration device comprising a first filter element located between the oil separator outlet and the oil separator inlet.

15. The electric rotary compressor according to any one of claims 1-9, characterized in that, The oil inlet extends tangentially along the oil separation chamber.

16. The electric rotary compressor according to any one of claims 1-9, characterized in that, The oil separator is formed inside the shell wall of the first housing.

17. The electric rotary compressor according to claim 16, characterized in that, The oil separator chamber is located on the side of the first exhaust chamber away from the second bearing.

18. An air conditioning system, characterized in that, Including the electric rotary compressor according to any one of claims 1-17.

19. A vehicle, characterized in that, include: The vehicle body and the air conditioning system mounted on the vehicle body, wherein the air conditioning system is the air conditioning system according to claim 18.

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