WO2025039769A1 - Electric rotary compressor, air conditioner system and vehicle - Google Patents

Abstract

An electric rotary compressor, an air condition system and a vehicle. The electric rotary compressor comprises: a first housing provided with an oil separation cavity, a first communication channel and a second communication channel being formed in the housing wall of the first housing, and an oil outlet of the oil separation cavity being communicated with a refrigerant discharge port by means of the first communication channel; and a compression component, comprising a cylinder assembly, a piston, a crankshaft, a first bearing and a second bearing, a first exhaust cavity being defined between the first bearing and the first housing, the compression component being provided with a first exhaust port communicated with the first exhaust cavity, and an oil inlet of the oil separation cavity being communicated with the first exhaust cavity by means of the second communication channel.

Description

Electric rotary compressor, air conditioning system and vehicle

CROSS-REFERENCE TO RELATED APPLICATIONS

This application is based on the Chinese patent application with application number 202311051175.0 and application date 2023-08-18, and claims the priority of the above-mentioned Chinese patent application. The entire content of the above-mentioned Chinese patent application is hereby introduced into this application as a reference.

Technical Field

The present application relates to the technical field of compressors, and in particular to an electric rotor compressor, an air conditioning system and a vehicle.

Background Art

The electric compressor is the core component of vehicle refrigeration equipment. It is a positive displacement compressor with high efficiency, low noise and smooth operation. As the third-generation vehicle compressor, it is widely used in automobile air-conditioning systems. In recent years, with the development of new energy vehicles, automobiles have further improved their requirements for air-conditioning compressor noise, vibration and durability. Electric compressors, such as scroll compressors and rolling rotor compressors, need to provide lubricating oil to lubricate the friction pairs in the electric compressor during use to reduce the noise generated when the friction pairs are working.

Summary of the invention

The present application aims to solve at least one of the technical problems existing in the related art. To this end, the present application proposes an electric rotor compressor.

The present application further proposes an air conditioning system having the electric rotor compressor.

The application also provides a vehicle having the above air conditioning system.

According to an embodiment of the present application, the electric rotor compressor includes: a shell component, the shell component includes a first shell, a refrigerant discharge port is formed on the first shell, the first shell is provided with an oil separation chamber, a first connecting channel and a second connecting channel are formed in the shell wall of the first shell, the oil separation outlet of the oil separation chamber is connected with the refrigerant discharge port through the first connecting channel; a compression component, at least part of the compression component is accommodated in the first shell, the compression component includes a cylinder assembly, a piston, a crankshaft, a first bearing and a second bearing, the piston is arranged in the cylinder assembly, the first bearing and the second bearing are matched at the axial ends of the cylinder assembly, the crankshaft is connected to the piston to drive the piston to rotate, a first exhaust chamber is defined between the first bearing and the first shell, the compression component has a first exhaust port and is connected with the first exhaust chamber, and the oil separation inlet of the oil separation chamber is connected with the first exhaust chamber through the second connecting channel.

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;

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

Exemplarily, an exhaust passage is provided in the compression component, and the second exhaust chamber is connected to the first exhaust chamber through the exhaust passage.

Furthermore, the compression component is fixed to the bracket through the second bearing, the end surface of the first bearing and the first shell are clearance-fitted, and a first sealing member is provided between the first bearing and the first shell to seal the first exhaust chamber.

Optionally, a fitting clearance between an end surface of the first bearing and the first housing is between 0.05 mm and 1 mm.

Optionally, the first sealing member is a rubber member or an elastic gasket.

In some specific embodiments, a first accommodating cavity is formed between the bracket and the first shell, a balancing channel is formed on the first shell, one end of the balancing channel is connected to the upper part of the first accommodating cavity, and the other end is connected to the first connecting channel.

Optionally, the electric rotary compressor further comprises a first muffler disposed in the first exhaust chamber.

Optionally, the electric rotary compressor further comprises a second muffler disposed in the second exhaust chamber.

In some embodiments, the first bearing comprises: a first flange and a first journal, the first journal having a first central hole, the first flange extending radially outward from an outer peripheral wall of the first journal; one side of the first flange is connected to the cylinder assembly, and a first outer seal is disposed between the other side and the first housing;

One end of the crankshaft is inserted into the first center hole, and a first inner seal is provided between the outer peripheral surface of the first journal and the first housing;

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

In some embodiments, the electric rotor compressor further comprises an oil separator inner tube disposed in the oil separator chamber, wherein the inner cavity of the oil separator inner tube is formed as an air outlet cavity connected to the oil separator outlet;

The oil inlet is located outside the oil inner tube and between two ends of the oil inner tube in the length direction.

Exemplarily, the flow area of the air outlet cavity 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.

Furthermore, an oil storage cavity is defined in the shell component, and an oil return hole communicating with the oil storage cavity is provided at the lower end of the oil separation cavity.

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

In some embodiments, the electric rotor compressor further comprises a filtering device disposed in the oil separation chamber, wherein the filtering device comprises a first filtering element located between the oil separation outlet and the oil separation inlet.

In some embodiments, the oil separation inlet extends along a tangential direction of the oil separation chamber.

Exemplarily, the oil separation chamber is formed in a shell wall of the first shell.

Further, the oil separation chamber is located on a side of the first exhaust chamber away from the second bearing.

The application also proposes an air conditioning system.

An air conditioning system according to an embodiment of the present application includes the electric rotary compressor described in any one of the above embodiments.

The application also proposes a vehicle.

A vehicle according to an embodiment of the present application includes: a vehicle body and an air-conditioning system mounted on the vehicle body, and the air-conditioning system is the air-conditioning system described in the above embodiment.

BRIEF DESCRIPTION OF THE DRAWINGS

In order to more clearly illustrate the technical solutions of the embodiments of the present application, the drawings required for use in the embodiments will be briefly introduced below. It should be understood that the following drawings only show certain embodiments of the present application and therefore should not be regarded as limiting the scope. For ordinary technicians in this field, other related drawings can be obtained based on these drawings without paying creative work.

FIG1 is a cross-sectional schematic diagram of an electric rotor compressor (partial parts such as a motor are omitted) according to an embodiment of the present application;

FIG2 is a cross-sectional schematic diagram of an electric rotor compressor (partial parts such as a motor are omitted) according to another embodiment of the present application;

FIG3 is a cross-sectional schematic diagram of a first housing according to another embodiment of the present application;

FIG. 4 is a schematic diagram of a vehicle according to an embodiment of the present application.

Reference numerals:

Vehicle 1000, air conditioning system 1001;

Electric rotary compressor 100;

Compression component 101, cylinder assembly 12, cylinder 121, middle partition plate 122, crankshaft 14;

A first bearing 15, a first flange 151, a first journal 152, a second bearing 16, a second flange 161, a second journal 162, a first muffler 17, and a second muffler 18;

Housing member 102;

The first shell 21, the refrigerant outlet 213, the matching wall 22, the first convex ring 221, the second convex ring 222, and the second shell 23;

The oil separator chamber 30, the oil separator inlet 31, the first communication channel 32, the oil separator outlet 33, the second communication channel 34, and the oil return hole 39;

A first exhaust cavity 41, a second exhaust cavity 42, an exhaust channel 43, and a balance channel 44;

The oil separator inner tube 52, the air outlet cavity 521, the cyclone cavity 522, the first tube section 523, the second tube section 524, and the third tube section 525;

A first seal 61, a first outer seal 611, a first inner seal 612, a second outer seal 621, and a second inner seal 622;

Bracket 70;

The first accommodating chamber 81 , the oil storage chamber 812 , and the second accommodating chamber 82 .

Embodiments of the present invention

The embodiments of the present application are described in detail below, and examples of the embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present application, and cannot be understood as limiting the present application.

In the description of the present application, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "up", "down", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "axial", "radial", "circumferential" and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present application and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present application. In addition, features defined as "first" and "second" may explicitly or implicitly include one or more of the features. In the description of the present application, unless otherwise specified, "multiple" means two or more.

In the description of this application, it should be noted that, unless otherwise clearly specified and limited, the terms "installed", "connected", and "connected" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection, or it can be indirectly connected through an intermediate medium, or it can be the internal communication of two components. For ordinary technicians in this field, the specific meanings of the above terms in this application can be understood according to specific circumstances.

In the related art, an oil separation structure is provided in the electric compressor, and the oil separation structure is used to separate the mixed fluid of the refrigerant and the lubricating oil discharged from the compression chamber of the electric compressor. In some schemes, it is proposed that in the rotor compressor, all the exhaust gas is gathered into the exhaust chamber between the main bearing and the bracket, and then the exhaust gas is discharged outward from the exhaust chamber into the oil separation chamber. In this scheme, since the refrigerant discharge port and the oil separation outlet of the compressor are strongly related to the exhaust chamber, and the position of the exhaust chamber is between the main bearing and the bracket, on the one hand, a longer exhaust pipe needs to be erected between the exhaust chamber and the oil separation chamber, and on the other hand, when the exhaust structure and the oil separation structure need to be changed, the bracket also needs to be changed, which makes it difficult to change the structural design.

In order to solve the above problems, an electric rotary compressor 100 according to an embodiment of the present application is described below with reference to the accompanying drawings.

According to an embodiment of the present application, an electric rotary compressor 100 , referring to FIGS. 1 and 2 , includes a housing component 102 and a compression component 101 .

The housing component 102 includes a first housing 21 . A refrigerant discharge port 213 is formed on the first housing 21 . At least a portion of the compression component 101 is accommodated in the first housing 21 .

Exemplarily, the housing component 102 further includes a second housing 23, an inner cavity is formed between the second housing 23 and the first housing 21, and the compression component 101 is located in the inner cavity. In some schemes, the housing component 102 further includes a bracket 70, the bracket 70 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 in the inner cavity. In some examples, as shown in FIG. 1, the second housing 23, the first housing 21 and the bracket 70 are all independently processed parts, and the second housing 23 and the first housing 21 are connected to opposite sides of the bracket 70. In other examples, the bracket 70 is an independently processed part and is placed in the inner cavity as a whole, and the bracket 70 is connected to the second housing 23 or the first housing 21. In some other examples, the bracket 70 is integrally formed on the second housing 23. When the housing component 102 includes the bracket 70, a first accommodating cavity 81 is formed between the bracket 70 and the first housing 21, and a second accommodating cavity 82 is formed between the bracket 70 and the second housing 23, and the first accommodating cavity 81 and the second accommodating cavity 82 can be connected or spaced apart from each other.

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 arranged in the cylinder assembly 12. The first bearing 15 and the second bearing 16 are matched at the axial ends of the cylinder assembly 12. The crankshaft 13 is connected to the piston to drive the piston to rotate.

Exemplarily, the cylinder assembly 12 includes at least one cylinder 121. Each cylinder 121 is provided with a cylinder cavity and a vane groove, and a reciprocating vane is provided in the vane groove. The crankshaft 14 passes through the cylinder cavity, and the eccentric portion of the crankshaft 14 is located in the cylinder cavity. The piston sleeve is arranged on the eccentric portion to rotate eccentrically in the cylinder cavity. One end of the vane stops on the outer peripheral surface of the piston to separate the cavity outside the piston in the cylinder into an intake cavity and a compression cavity. The setting of the eccentric portion allows the piston to rotate eccentrically, thereby driving the vane to reciprocate in the vane groove. Among them, a stop spring is provided in the vane groove, and the stop spring presses against one end of the vane, so that the other end of the vane maintains a stop state with the outer peripheral surface of the piston. Of course, the stop spring in the present application can also be replaced by other structures.

Of course, the type of compression component 101 in the present application is not limited to this. In some schemes, one end of the slide is rotatably connected to the piston, so the slide swings back and forth in the cylinder assembly 12. In the cylinder cavity and outside the piston, one side of the slide is an air suction chamber, and the pump suction port of the compression component 101 is connected to the refrigerant inlet of the shell component 102 or the low-pressure chamber in the shell component 102 to inhale the low-pressure refrigerant gas, so the pressure of the air suction chamber is relatively low. The other side of the slide is a compression chamber, which compresses the gas and discharges it from the pump outlet. The pressure of the compression chamber is higher than the pressure of the air suction chamber. After the exhaust gas is discharged to the oil separation chamber 30 for gas-liquid separation, it is discharged from the refrigerant discharge port 213 of the shell component 102. The cylinder assembly 12 is provided with a first bearing 15 and a second bearing 16 on both sides of the axial direction to close the above-mentioned compression chamber and the air suction chamber.

In some embodiments, the compression component 101 is 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 matched at the axial ends of the cylinder 121. In this case, the compression component 101 may have an exhaust port, which is called the first exhaust port.

In other embodiments, as shown in FIG. 1 and FIG. 2 , the compression component 101 is a multi-cylinder structure, that is, the cylinder assembly 12 includes at least two cylinders 121, and a middle partition 122 is provided between two adjacent cylinders 121. The first bearing 231 and the second bearing 232 are located on the side of the two outermost cylinders 121 away from each other. The multiple cylinder cavities of this compression component 101 can be a series structure, such as multiple cylinders 121 are arranged in sequence along the left and right directions, and the compression component 101 forms a first exhaust port at the right end. In the direction from left to right, the left cylinder pump inhales air, and then compresses the fluid and exhausts it from the pump outlet. The pump outlet of the left cylinder is connected to the pump inlet of the right cylinder, and the gas is discharged into the cylinder cavity on the right and compressed again, thereby increasing the gas pressure. Multiple cylinder chambers can also be parallel structures. For example, in the example of Figure 1, the pump suction ports of multiple cylinders are in parallel, and are respectively connected to the refrigerant inlet of the shell component 102 or the low-pressure chamber in the shell component 102. The pump outlets of multiple cylinders are also in parallel, and are respectively connected to the exhaust chamber. That is, the fluid in each cylinder is no longer compressed after being compressed, but is discharged into the exhaust chamber and then enters the oil separation chamber 30 for oil and 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 the exhaust port, which is called the first exhaust port. The compression component 101 may also have multiple exhaust ports, and the pump outlets of multiple cylinders 121 respectively select appropriate exhaust ports for exhaust. When the compression component 101 is provided with exhaust ports at both ends of the axial direction, 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.

Of course, in the present application, the electric rotor compressor 100 also includes a motor (not shown in the figure), which is located in the housing component 102 and is connected to the crankshaft 14, and drives the piston to do work by driving the crankshaft 14 to rotate. 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 discharge port 213, or a low-pressure cavity connected to the refrigerant inlet. Or after the inner cavity is separated by the bracket 70, one side is a high-pressure cavity and the other side is a low-pressure cavity. Therefore, the motor and the compression component 101 can be located in the high-pressure cavity, the motor and the compression component 101 can be located in the low-pressure cavity, or the compression component 101 is located in the high-pressure cavity and the motor is located in the low-pressure cavity, and there is no restriction here. Since the motor is a known structure in the prior art, its structure and working principle are not described in detail in this article.

It should be noted that the "high pressure" and "low pressure" mentioned in this application do not specifically refer to specific pressure values, but are only used to indicate the difference in pressure between the two chambers. For example, in the example of Figure 1, under the spacing of the bracket 70, the second accommodating chamber 82 between the bracket 70 and the second shell 23 is connected to the refrigerant inlet, resulting in a lower pressure, which is called a low-pressure chamber. The first accommodating chamber 81 formed between the bracket 70 and the first shell 21 is connected to the refrigerant outlet 213, resulting in a cavity pressure higher than the second accommodating chamber 82, so the first accommodating chamber 81 is called a high-pressure chamber.

1 and 2, the first shell 21 is provided with an oil separation chamber 30, and a first connecting channel 32 and a second connecting channel 34 are formed in the shell wall of the first shell 21, and the oil separation outlet 33 of the oil separation chamber 30 is connected with the refrigerant discharge outlet 213 through the first connecting channel 32. It should be noted that the above-mentioned "the first shell 21 is provided with an oil separation chamber 30" should be understood in a broad sense, for example, it may include: the oil separation chamber 30 is defined by a tube body assembled on the first shell 21, that is, the first shell 21 and the tube body are of a split design, so that it is convenient to freely design the axis and cross-sectional area of the oil separation chamber 30 defined by the tube body to meet different design requirements. Or, for example, it may also include: as shown in Figures 1 and 2, the oil separation chamber 30 can be formed integrally on the first shell 21, so that the oil separation chamber 30 does not need to be assembled separately, which is conducive to simplifying the production steps.

Exemplarily, as shown in Figures 1 and 2, 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, and the oil separation inlet 31 of the oil separation chamber 30 is connected to the first exhaust chamber 41 through the second connecting channel 34.

It is understandable that the compression component 101 requires lubricating oil to work, and the refrigerant will be mixed with lubricating oil when it is discharged. The setting of the oil separation chamber 30 can separate the lubricating oil mixed in the refrigerant, prevent the electric rotor compressor 100 from discharging too much lubricating oil, ensure that there is enough lubricating oil lubrication in the electric rotor compressor 100, and ensure that there is no excessive lubricating oil in other pipelines and structures outside the electric rotor compressor 100 and occupy the flow channel. The oil separation chamber 30 separates the lubricating oil, which can facilitate the oil return of the electric rotor compressor 100 to improve the performance of the electric rotor compressor 100.

During the actual operation of the electric rotary compressor 100, the mixed fluid of the gaseous refrigerant and the lubricating oil discharged from the compression chamber can be discharged from the first exhaust port, and the mixed fluid enters the oil separation chamber 30 via the second connecting channel 34 and the oil separation inlet 31, and then the mixed fluid is separated into gas and liquid in the oil separation chamber 30, that is, the gaseous refrigerant and the lubricating oil in the mixed fluid are separated. Then, the gaseous refrigerant enters the first connecting channel 32 via the oil separation outlet 33, and flows through the first connecting channel 32 and is discharged from the refrigerant outlet 213, thereby realizing the exhaust of the electric rotary compressor 100. The lubricating oil flows back to the compression component 101 to lubricate and protect the kinematic pair, ensuring the efficient and reliable operation of the electric rotary compressor 100.

Optionally, as shown in FIG2 , an oil storage chamber 812 is defined in the housing component 102, and the lubricating oil separated by the oil separation chamber 30 returns to the oil storage chamber 812 through the oil return hole 39, and the lubricating oil can be provided to the compression component 101 through the oil storage chamber 812. Alternatively, the oil separation chamber 30 can also directly provide the separated lubricating oil to the compression component 101 through other oil discharge paths.

In the present application, by defining a first exhaust chamber 41 between the first bearing 15 and the first housing 21, the compression component 101 discharges the high-pressure fluid to the first exhaust chamber 41, and then enters the oil separation chamber 30 for gas-liquid separation. In the arrangement of this scheme, the oil separation chamber 30 does not directly take in air from the exhaust chamber at the second bearing 16, thus avoiding the strong correlation between the structural parameters and position parameters of the oil separation chamber 30 and the second bearing 16. The second bearing 16 is located in the middle position of the housing component 102, so when the exhaust structure and the oil separation structure need to be changed, the structure in the middle position of the housing component 102 is less affected. For example, in the examples of Figures 1 and 2, when the volume of the first exhaust chamber 41 and the volume of the oil separation chamber 30 need to be increased or reduced, the second housing 23, the bracket 70 and the structure between the two of the electric rotor compressor 100 can remain unchanged, and the structure and parameters of the compression component 101 can also remain unchanged. It is only necessary to change the structural parameters of the first housing 21 and the structural parameters of the oil separation chamber 30, and the volume of the first exhaust chamber 41 and the oil separation chamber 30 can be adjusted. Therefore, the structural solution of the present application can reduce the difficulty of structural modification and is also conducive to reducing the difficulty of assembly. The parts of the electric rotor compressor 100 are highly versatile and have a wide range of applications.

It can be understood that in the present application, the first connecting channel 32 is formed by using the shell wall of the first shell 21, and the gaseous refrigerant separated by the oil separation chamber 30 is directly discharged to the refrigerant outlet 213 through the first connecting channel 32, instead of the oil separation outlet 33 of the oil separation chamber 30 exhausting to the refrigerant outlet 213 through the first accommodating chamber 81. In this way, on the one hand, the external impact of the high-pressure airflow on the compression component 101 is reduced, and the vibration is reduced. On the other hand, since the first accommodating chamber 81 surrounds the compression component 101, the compression component 101 inevitably flows out lubricating oil at the connection point of the parts, and reducing the flow of high-pressure air through the first accommodating chamber 81 can reduce the airflow from taking away more lubricating oil. In some schemes, a part of the first accommodating chamber 81 is the oil storage chamber 812. If the exhaust takes away the lubricating oil stored in the first accommodating chamber 81, the oil separation efficiency of the oil separation chamber 30 gas-liquid separation in the early stage is reduced. Therefore, the present application directly uses the first connecting channel 32 of the oil separation chamber 30 to exhaust the refrigerant outlet 213, which is conducive to maintaining a higher oil-gas separation rate.

It is also understandable that, due to the limitation of the pump body structure, the compression component is arranged in the center of the first accommodating chamber in the existing rotary compressor, and it is difficult for the oil separation chamber to be coaxially arranged with the refrigerant discharge port. Due to this limitation, the oil separation chamber of the rotary compressor is prone to problems such as being unable to be processed, having a small diameter, and being unable to be installed.

In the embodiment of the present application, by setting the first connecting channel 32 in the shell wall of the first shell 21 (i.e., in the wall thickness space), and the first connecting channel 32 connects the oil outlet 33 and the refrigerant outlet 213, it is possible to avoid the oil outlet 33 from being directly connected to the refrigerant outlet 213, so that the size and position of the refrigerant outlet 213 do not affect the oil separation 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, it is beneficial for the oil separation chamber 30 to achieve the best oil separation efficiency as much as possible, to ensure the oil return lubrication requirements under some conditions such as high load conditions, to reduce the occurrence of blowby or refrigerant leakage, thereby improving the cooling capacity and compression efficiency of the electric rotor compressor 100, and even meeting the reliability requirements of the electric rotor compressor 100.

In the present application, the second connecting channel 34 is formed by utilizing the shell wall of the first shell 21, and the airflow in the first exhaust chamber 41 is discharged to the oil separation chamber 30 through the second connecting channel 34, which is beneficial to reduce the number of pipes. The connection relationship between the first connecting channel 32, the second connecting channel 34 and the oil separation chamber 30 is utilized to ensure the controllability of the direction of the fluid in and out of the oil separation chamber 30. Moreover, in this arrangement, the air inlet and outlet positions of the oil separation chamber 30 are both connected to the first shell 21, and the strength and rigidity of the first shell 21 can be utilized to resist the impact of the airflow and reduce the vibration of the electric rotor compressor 100.

In addition, the shell wall of the first shell 21 is used to form the second connecting channel 34, instead of the first exhaust chamber 41 exhausting air to the first accommodating chamber 81 and then supplying air from the first accommodating chamber 81 to the oil separation chamber 30, so as to maintain the flow rate of the airflow. In some schemes of the present application, the mixed fluid flows along the circumference of the oil separation chamber 30 in the oil separation chamber 30, and the lubricating oil is thrown out of the gaseous refrigerant by centrifugal force to complete the gas-liquid separation. The greater the flow rate of the mixed liquid, the stronger the centrifugal force, and the better the gas-liquid separation effect. Therefore, the first exhaust chamber 41 supplies air to the oil separation chamber 30 through the second connecting channel 34, which is conducive to maintaining a good gas-liquid separation effect.

The second connecting passage 34 is formed on the shell wall of the first shell 21 instead of the first bearing 15, so as to avoid direct connection between the oil separation structure and the compression component 101. In particular, when the oil separation structure includes a tube body, the large vibration of the tube body caused by the vibration of the compression component 101 is reduced, which is conducive to ensuring the connection reliability of the tube body and reducing the probability of fracture and leakage at the connection.

In summary, according to the electric rotor compressor 100 of the embodiment of the present application, by forming the first exhaust chamber 41 between the first bearing 15 and the first housing 21, the compression component 101 discharges the compressed high-pressure fluid to the first exhaust chamber 41, and then enters the oil separation chamber 30 for gas-liquid separation. The oil separation chamber 30 is not directly inlet at the middle position of the housing component 102 (including the second bearing), which reduces the strong correlation between the oil separation position, the exhaust position and the structure of the middle position of the housing component 102. The assembly difficulty of the electric rotor compressor 100 is low, and the difficulty of modifying the exhaust structure and the oil separation structure is low when they need to be modified, which is useful for improving the application scope of the parts of the electric rotor compressor 100. In the present application, by forming the first connecting channel 32 and the second connecting channel 34 on the shell wall of the first housing 21, the air inlet and outlet of the oil separation chamber 30 are completed, which reduces the number of pipes on the one hand, and can use the strength and rigidity of the first housing 21 on the other hand 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 rotor compressor 100.

In some embodiments, as shown in FIG. 1 and FIG. 2 , the housing component 102 includes a bracket 70, the compression component 101 is located between the bracket 70 and the first housing 21, and one end of the crankshaft 13 passes through the bracket 70 to be connected to the motor. The second bearing 16 is connected to the bracket 70, and a second exhaust chamber 42 is defined between the second bearing 16 and the bracket 70. The compression component 101 has a second exhaust port and is in communication with the second exhaust chamber 42, and the second exhaust chamber 42 is in communication with the first exhaust chamber 41.

That is to say, the exhaust position of the compression component 101 is not limited to the first bearing 15, and a second exhaust port can also be set on the second bearing 16. This compression component 101 can be a multi-cylinder structure, so that each cylinder 121 can select an exhaust position nearby, reducing the difficulty of designing the exhaust path of the cylinder 121. Of course, the structure of the present application is not limited to this. In some single-cylinder compression components 101, due to the large exhaust volume or high exhaust frequency, there are exhaust positions on both axial sides of the compression component 101, which can exhaust as soon as possible and reduce exhaust resistance.

Here, although the 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 separation chamber 30 through the second connecting passage 341 for gas-liquid separation. Here, the fluid in the second exhaust chamber 42 is not directly discharged to the first accommodating chamber 81, which can reduce the external impact of the high-pressure gas on the compression component 101 on the one hand, and reduce the amount of lubricating oil taken away on the other hand.

Moreover, in some solutions of the present application, the mixed fluid generates different centrifugal forces in the oil separation chamber 30 by flowing in the circumferential direction to achieve gas-liquid separation. Therefore, the second exhaust chamber 42 supplies gas to the oil separation chamber 30 through the first exhaust chamber 41, which is conducive to maintaining the flow speed of the mixed fluid and ensuring the gas-liquid separation effect.

For example, as shown in Fig. 2, an exhaust passage 43 is provided in the compression component 101, and the second exhaust chamber 42 is connected to the first exhaust chamber 41 through the exhaust passage 43. Of course, the structure of the present application is not limited thereto, and the exhaust passage 43 may be formed in the shell wall of the first shell 21, or a pipe may be provided in the first accommodating chamber 81, one end of the pipe being connected to the first exhaust chamber 41 and the other end being connected to the second exhaust chamber 42.

Compared with the other two solutions, directly setting the exhaust passage 43 inside the compression component 101 can shorten the exhaust path, reduce the difficulty of assembly sealing, and reduce the number of parts.

In the present application, the arrangement form of the oil separation chamber 30 may not be limited. For example, in some embodiments, the oil separation chamber 30 as described above is defined by a tube body mounted on the first shell 21. Specifically, an oil separation outer tube (not shown) is mounted on the first shell 21, and the inner cavity of the oil separation outer tube forms at least a part of the oil separation chamber 30. In other words, the oil separation outer tube and the first shell 21 are a split structure, and the oil separation outer tube is plugged into the first shell 21. As a result, there is no need to process the oil separation chamber 30 on the first shell 21, which reduces the structural requirements and wall thickness requirements for the first shell 21, and the first shell 21 can be flexibly designed.

In some specific embodiments, the lower end of the outer tube has a reducer, and the lower end of the reducer is connected to the oil return hole 39 .

For example, the axial cross-section shape of the tube wall of the reducer may be configured as a straight line, or the axial cross-section shape of the tube wall of the reducer may be configured as an arc line, which is not limited here.

For example, the inner diameter of one end of the reducer connected to the oil separation outer tube is the same as the inner diameter of the oil separation outer tube, that is, the inner diameter of one end of the reducer connected to the oil separation outer tube is the same as the inner diameter of the oil separation chamber 30, so that the lubricating oil can enter the reducer along the cavity wall of the oil separation chamber 30, and in the flow direction of the lubricating oil, the inner diameter of the reducer gradually decreases to connect the oil return hole 39 at the end of the reducer away from the oil separation outer tube. Optionally, the diameter of the oil return hole 39 is smaller than the inner diameter of the oil separation chamber 30.

Therefore, by providing the tapered tube, when the lubricating oil flows to the oil return hole 39, the inner wall of the tapered tube with a gradually decreasing inner diameter can guide and converge the lubricating oil, thereby improving the oil return reliability.

In other embodiments of the present application, as shown in FIG3 , an oil separation chamber 30 is formed in the shell wall of the first shell 21. In other words, the oil separation chamber 30 is integrally formed on the first shell 21, or the first shell 21 itself can form a complete oil separation chamber 30. As a result, the step of assembling the oil separation outer pipe is omitted, parts are reduced, costs are reduced, and production steps are simplified, thereby improving production efficiency.

Exemplarily, a portion of the shell wall of the first shell 21 is thicker, which is used to form the oil separation chamber 30. The shell portion is called the matching wall 22, and the oil separation inlet 31 is formed on the matching wall 22. Further, the first connecting channel 32, the oil separation outlet 33, and the second connecting channel 34 are also formed on the matching wall 22. Furthermore, the refrigerant discharge port 213 is formed on the matching wall 22, and optionally, the refrigerant discharge port 213 is located at the top of the matching wall 22.

Furthermore, the oil separation chamber 30 is located on the side of the first exhaust chamber 41 away from the second bearing 16. As shown in Figures 1 and 2, the shell wall of the first housing 21 opposite to the bracket 70 is the matching wall 22, so that the exhaust structure and the oil separation structure are concentrated at the same end of the housing component 102, on the one hand, the exhaust path and the oil return path length are 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.

In some specific embodiments, as shown in FIG. 1 and FIG. 2 , the compression component 101 is fixed to the bracket 70 through 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, and the compression component 101 remains fixed in the housing component 102 when the bracket 70 is fixed to the first housing 21 or the second housing 23. At this time, a gap can be maintained between the end face of the first bearing 15 and the first housing 21 to avoid the defective rate caused by the interference of the end faces of the first housing 21 and the first bearing 15 due to over-positioning.

When there is a gap between the end surface of the first bearing 15 and the first housing 21 , a first seal 61 may be provided between the first bearing 15 and the first housing 21 to achieve spacing between the first exhaust cavity 41 and the first accommodating cavity 81 .

Optionally, the matching clearance between the end surface of the first bearing 15 and the first housing 21 is between 0.05 mm and 1 mm. By setting the clearance width in this way, on the one hand, it can ensure that the two do not interfere with each other, and on the other hand, it can reduce the difficulty of sealing at the clearance.

When the first seal 61 is provided, it is best to use a seal with strong elasticity, such as a rubber piece, an elastic gasket, etc. By utilizing its strong elasticity, when the above-mentioned fitting clearance has a large fluctuation due to processing errors, the first seal 61 can adapt to the fitting clearance. In addition, it is easy to ensure that the first seal 61, the first bearing 15, and the first housing 21 are all in a compressed state, thereby improving the sealing reliability.

The use of rubber parts and elastic gaskets can prolong the service life. Of course, the first sealing member 61 can also be other sealing members with strong elasticity, such as a silicone ring.

In some specific embodiments, as shown in FIG. 1 and FIG. 2 , the first bearing 15 includes: a first flange 151 and a first journal 152, the first journal 152 having a first center hole, and the first flange 151 extending radially outward from the outer peripheral wall of the first journal 152. One side of the first flange 151 is connected to the cylinder assembly 12, and a first outer seal 611 is provided between the other side and the first housing 21. One end of the crankshaft 13 is inserted into the first center hole, and a first inner seal 612 is provided between the outer peripheral surface of the first journal 152 and the first housing 21. The first exhaust chamber 41 is located radially outside the first journal 152 and between the first flange 151 and the first housing 21. In this way, high-pressure gas can be prevented from leaking from the first center hole. By providing the first outer seal 611 and the first inner seal 612, on the one hand, assembly is facilitated, and on the other hand, sufficient volume space is provided for the first exhaust chamber 41. Moreover, the first bearing 15 is supported at the first outer seal 611 and the first inner seal 612.

For example, as shown in FIGS. 1 to 3 , a first convex ring 221 is provided on the mating wall 22, the first journal 152 is inserted into the first convex ring 221, and a first inner seal 612 is provided between the first convex ring 221 and the first journal 152. Of course, the present application may not be limited thereto, for example, a groove may 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.

For example, the matching wall 22 is provided with a second convex ring 222 near the edge, and the end face of the first flange 151 faces the second convex ring 222, such as the diameter of the first flange 151 is larger than the outer diameter of the second convex ring 222. A first outer seal 611 is provided between the end face of the first flange 151 and the second convex ring 222. With such a configuration, the end face of the first flange 151 has little interference with other positions of the matching wall 22, and is easy to assemble.

In some specific embodiments, as shown in FIG. 1 and FIG. 2 , the second bearing 16 includes: a second flange 161 and a second journal 162, the second journal 162 having a second center hole, and the second flange 161 extending radially outward from the outer peripheral wall of the second journal 162. One side of the second flange 161 is connected to the cylinder assembly 12, and a second outer seal 621 is provided between the other side and the bracket 70. One end of the crankshaft 13 is successively penetrated through the second center hole and the bracket 70, and a second inner 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 outside the second journal 162 and between the second flange 162 and the bracket 70. In this way, high-pressure gas can be prevented from leaking from the second center hole, and the second bearing 16 is supported.

In some specific embodiments, as shown in FIG. 2 and FIG. 3 , a first accommodating chamber 81 is formed between the bracket 70 and the first shell 21, and a balancing channel 44 is formed on the first shell 21, one end of the balancing channel 44 is connected to the first accommodating chamber 81, and the other end is connected to the first connecting channel 32. In this way, the high-pressure gaseous refrigerant after the gas-liquid separation is completed can be sent to the first accommodating chamber 81 through the balancing channel 44, and the first accommodating chamber 81 maintains a high-pressure environment, avoiding a small pressure difference between the first accommodating chamber 81 and the first exhaust chamber 41, and reducing air leakage in the first exhaust chamber 41.

Exemplarily, the bottom of the first accommodating chamber 81 forms an oil storage chamber 812, and the balancing channel 44 is opened above the oil storage chamber 812. In this way, the oil storage chamber 812 is in a high pressure state, which facilitates the use of pressure difference to transport the lubricating oil in the oil storage chamber 812 to the compression component 101 for lubrication.

Optionally, the balancing channel 44 is opened on the wall of the first shell 21 along a direction parallel to the axis of the compression component 101, thereby facilitating processing.

Of course, as described above, the oil return method in the present application is not limited to passing through the oil storage chamber 812. In some schemes, one end of the oil return hole 39 is opened on the inner side of the first convex ring 221, and the lubricating oil is pressed into the compression component 101 from the shaft hole of the crankshaft 14 or the outer peripheral surface of the crankshaft 14 by using the pressure difference. Optionally, a throttling structure (throttle valve) is set in the oil return hole 39, or the flow area of the oil return hole 39 is set to be smaller, so that the oil return flow rate can be properly controlled when returning the oil, which is conducive to matching the oil return speed with the gas-oil separation speed.

In some optional embodiments of the present application, the electric rotor compressor 100 further includes a first muffler 17 disposed in the first exhaust chamber 41, and a first muffler chamber is formed between the first bearing 15 and the first muffler 17, thereby reducing the exhaust noise of the airflow in the compression component 101 discharged to the first exhaust chamber 41. Optionally, the first muffler 17 can be provided with one or more layers.

In some optional embodiments of the present application, the electric rotor compressor 100 further includes a second muffler 18 disposed in the second exhaust chamber 42. A second muffler chamber is formed between the second bearing 16 and the second muffler 18, thereby reducing the exhaust noise of the airflow in the compression component 101 discharged to the second exhaust chamber 42. Optionally, the second muffler 18 may be provided in one or more layers.

In some embodiments, as shown in Fig. 2, the oil inlet 31 extends along the tangential direction of the oil chamber 30. This is conducive to the circumferential rotation of the fluid along the oil chamber 30, achieving the effect of cyclone separation.

Of course, the present application is not limited thereto, and the principle of cyclone separation may be achieved other than by tangential entry. For example, a filter device (not shown) may be provided in the oil separation chamber 30 to achieve oil-gas separation by filtering. Of course, both cyclone separation and filter device may be used.

Optionally, the filtering device includes a first filter element located between the oil separator outlet 33 and the oil separator inlet 31. In this way, the mixed fluid that has not been separated from the gas and liquid can be completely blocked below the first filter element, which is conducive to ensuring that all the fluids are filtered before being discharged. The first filter element is set here, which is easy to assemble and easy to observe during maintenance.

Further optionally, the filter device may adopt a filter mesh structure to reduce flow resistance.

In some optional embodiments, the first filter element is in the shape of a thin sheet, the edge of the first filter element is fixed on the inner wall of the oil separation chamber 30, and the middle part of the first filter element protrudes downward, which helps the mixed fluid to flow in a cyclonic manner in the oil separation chamber 30.

In some embodiments, as shown in FIGS. 1 to 3 , the electric rotor compressor 100 further includes an oil separator inner tube 52 disposed in the oil separator chamber 30, the inner cavity of the oil separator inner tube 52 is formed as an outlet cavity 521 connected to the oil separator outlet 33, and a cyclone cavity 522 is formed between the oil separator chamber 30 and the oil separator inner tube 52. The oil separator inlet 31 is located outside the oil separator inner tube 52 and between the two ends in the length direction of the oil separator inner tube 52, so that the oil separator inlet 31 is arranged toward the cyclone cavity 522. In this way, the cyclone cavity 522 provides a space for the exhaust gas to enter and rotate and flow.

Here, placing the oil inlet 31 between the two ends of the oil inner tube 52 in the length direction helps drive the mixed flow to swirl along the cyclone separation space, thereby improving the gas-liquid separation effect.

At this time, the oil inlet 31 can be further extended along the tangential direction of the oil chamber 30, which can further help the mixed fluid to rotate along the circumferential cyclone and achieve gas-liquid separation of lubricating oil and gaseous refrigerant. It can be understood that the larger the rotation radius of the fluid, the greater the centrifugal force generated. The oil inlet 31 is extended along the tangential direction of the oil chamber 30, so that the fluid is immediately guided to rotate by the inner wall of the oil chamber 30 after entering the oil chamber 30 from the oil inlet 31, and the fluid maintains a larger rotation radius as soon as it enters, so that the lubricating oil liquid in the mixed fluid can be thrown out from the gas and flow along the oil chamber 30, while the gaseous refrigerant quickly enters the air outlet cavity 521 from the bottom due to its smaller mass and is discharged. In addition, extending the oil inlet 31 along the tangential direction of the oil chamber 30 can reduce excessive disturbances between the newly entered fluid and the positively rotating fluid, which is conducive to more fluids to keep rotating around the cyclone chamber 522.

Optionally, the cyclone chamber 522 is annular, so that the outer peripheral surface of the oil separator inner tube 52 forming the cyclone chamber 522 is a cylindrical surface, which is easy to process. Moreover, the cyclone chamber 522 is annular, which can maximize the use of this part of the space, so that the flow has a larger rotation radius.

In some specific embodiments, as shown in FIG. 2 , the oil separator inner tube 52 includes a first tube segment 523 , a second tube segment 524 , and a third tube segment 525 sequentially connected along its length direction, and the first tube segment 523 is adjacent to the first connecting channel 32 .

Exemplarily, the diameter of the second pipe section 524 gradually decreases in the direction from the first pipe section 523 to the third pipe section 525. Among them, the first pipe section 523 has a large diameter, which is convenient for placing the first pipe section 523 at the oil outlet 33. The third pipe section 525 has a relatively small diameter, which is convenient for forming a cyclone chamber 522 between the inner wall of the oil chamber 30. The second pipe section 524 has a gradually decreasing diameter structure, which is convenient for processing.

More illustratively, during assembly, the oil separator inner tube 52 is inserted from the refrigerant discharge port 213 , and the first tube section 523 is interference-fitted at the oil separator outlet 33 .

In some specific embodiments, a section of the oil separation chamber 30 connected to the oil separation outlet 33 is a cylindrical cavity. The oil separation inner tube 52 includes a first tube section 523, a second tube section 524, and a third tube section 525 connected in sequence. The first tube section 523 and the third tube section 525 are circular tubes, and the second tube section 524 is a tapered tube whose diameter gradually decreases toward the third tube section 525. The outer diameter of the third tube section 525 is smaller than the inner diameter of the cylindrical cavity of the oil separation chamber 30. The two are coaxially arranged, and a circle around the third tube section 525 forms a circular cyclone cavity 522. One end of the second connecting channel 34 forms an oil separation inlet 31, and is tangentially arranged along the cyclone cavity 522. The axis of the second connecting channel 34 is perpendicular to the axis of the oil separation inner tube 52. In the example shown in FIG. 2, the cross section presented in the figure passes through the axis of the oil separation inner tube 52. In the examples shown in FIG. 1 and FIG. 3, the cross section presented in the figure passes through the axis of the second connecting channel 34.

Further, there is at least one second communication channel 34. When there are at least two second communication channels 34, the second communication channels 34 are sequentially distributed along the axis of the oil separator inner tube 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 far as possible, and the annular flow formed by the two streams of fluid is sequentially distributed along the axis of the oil separator inner tube 52, so that the space of the cyclone chamber 522 can be fully utilized.

Optionally, as shown in FIG. 2 , the distance L between the oil inlet 31 and the end of the oil inner tube 52 away from the oil outlet 33 is at least 5 mm, which is conducive to the fluid making at least one rotation in the cyclone chamber 522 .

Exemplarily, the flow area of the air outlet cavity 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, and S2 accounts for 25% to 60% of S1. Optionally, the proportion of S2 to S1 can be 25%, 30%, 40%, 45%, 50%, 55%, 58%, 60%, etc. In this way, it is ensured that the air inlet caliber of the oil separation chamber 30 is sufficient, the tangential rotation force is sufficient, the efficiency of cyclone separation of refrigerant and lubricating oil can be improved, and the exhaust efficiency and oil return efficiency can be improved.

In some specific embodiments, as shown in Figures 2 and 3, an oil storage chamber 812 is defined in the shell component 102, and an oil return hole 39 connected to the oil storage chamber 812 is provided at the lower end of the oil separation chamber 30, thereby reducing the possibility of oil supply interruption caused by leakage of gaseous refrigerant into the oil storage chamber 812.

Optionally, the oil return hole 39 is arranged on the first housing 21 along a direction parallel to the axis of the compression component 101 and is arranged adjacent to the bottom of the oil storage chamber 812 .

Exemplarily, the flow area of the air outlet cavity 521 is S1, there is at least one oil return hole 39, the sum of the flow areas of all oil return holes 39 is S3, and 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.

This ensures that the return oil can flow back to the oil storage chamber 812 as quickly as possible, reducing the oil storage in the oil separation chamber 30, leaving space for air flow to pass through, and reducing the lubricating oil carried away by the refrigerant gas.

In some embodiments, as shown in FIG. 1-FIG . 3 , the oil separation chamber 30 is a long chamber extending vertically, and may be a vertical straight extension or an inclined extension, and the axis of the oil separation chamber 30 may also be a curve.

Optionally, the lower end of the oil separation chamber 30 has a tapered cavity, and the lower end of the tapered cavity is connected to the oil return hole 39. By providing the tapered cavity, when the lubricating oil flows to the oil return hole 39, the inner wall of the tapered cavity with a gradually decreasing inner diameter can guide and converge the lubricating oil, thereby improving the reliability of oil return.

For example, as shown in FIG1 , in the axial direction of the oil separation chamber 30, the tapered chamber is located below the oil separation outlet 33, and the oil return hole 39 is located below the oil separation outlet 33. It should be noted that since the refrigerant is a gaseous refrigerant and the lubricating oil is a liquid, after the mixed fluid of the gaseous refrigerant and the lubricating oil discharged from the compression chamber enters the oil separation chamber 30, the lubricating oil will flow downward under the action of its own gravity to flow to the oil return hole 39, and the gaseous refrigerant will flow upward to the oil separation outlet 33, so as to separate the two, thereby realizing the exhaust and oil return of the electric rotary compressor 100.

In some embodiments, as shown in Figures 1-3, the axis of the first shell 21 extends horizontally, the first connecting channel 32 is located at the top of the first shell 21 and extends vertically, the upper end of the first connecting channel 32 passes through the top of the first shell 21 to form a refrigerant discharge port 213, and the oil separation chamber 30 extends downward from the lower end of the first connecting channel 32.

For example, the upper end of the first connecting channel 32 passes through the top of the first shell 21 to form a refrigerant outlet 213, so as to facilitate the processing and forming of the refrigerant outlet 213. The extension direction of the oil separation chamber 30 is substantially the same as the gravity direction of the lubricating oil, which is conducive to the separated lubricating oil being able to quickly flow along the oil separation chamber 30 to the oil return hole 39 under the action of its own gravity, and is conducive to improving the oil return efficiency of the electric rotary compressor 100.

Alternatively, the first communication channel 32 is located obliquely above the compression component 101 and the axis extends vertically, the oil separation chamber 30 extends vertically downward from the lower end of the first communication channel 32, and the oil separation chamber 30 is located on the side of the compression component 101. In this case, the compression component 101 can also be avoided. Therefore, the extension direction of the oil separation chamber 30 is the same as the gravity direction of the lubricating oil, which is conducive to the separated lubricating oil being able to quickly flow along the oil separation chamber 30 to the oil return hole 39 under the action of its own gravity, which is conducive to improving the oil return efficiency of the electric rotor compressor 100.

It should be noted that the compression component 101 according to the embodiment of the present application is a rotary compression mechanism, but the specific structure is not limited, and it can be a single-cylinder compression mechanism or a multi-cylinder compression mechanism. In addition, the central axis of the electric rotary compressor 100 extends horizontally or is slightly inclined to the horizontal line. For example, it can also be a vertical compressor whose central axis extends vertically or is slightly inclined to the vertical line, etc.

The present application also proposes an air conditioning system 1001 .

As shown in FIG. 4 , an air conditioning system 1001 according to an embodiment of the present application includes the electric rotary compressor 100 described in any one of the above embodiments.

According to the air conditioning system 1001 of the embodiment of the present application, the electric rotor compressor 100 forms a first exhaust chamber 41 between the first bearing 15 and the first housing 21, and the compression component 101 discharges the compressed high-pressure fluid to the first exhaust chamber 41, and then enters the oil separation chamber 30 for gas-liquid separation. The oil separation chamber 30 is not directly inlet at the middle position of the housing component 102 (including the second bearing), which reduces the strong correlation between the oil separation position, the exhaust position and the structure of the middle position of the housing component 102. The assembly difficulty of the electric rotor compressor 100 is low, and the difficulty of modifying the exhaust structure and the oil separation structure is low when they need to be modified, which is useful for improving the application range of the parts of the electric rotor compressor 100. In the present application, the first connecting channel 32 and the second connecting channel 34 are formed on the shell wall of the first housing 21 to complete the inlet and outlet of the oil separation chamber 30, which reduces the number of pipes on the one hand, and can use the strength and rigidity of the first housing 21 on the other hand 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 rotor compressor 100. This is beneficial to the noise reduction and high-efficiency operation of the air-conditioning system 1001.

The present application also proposes a vehicle 1000 .

As shown in FIG. 4 , a vehicle 1000 according to an embodiment of the present application includes: a vehicle body and an air-conditioning system 1001 mounted on the vehicle body, and the air-conditioning system 1001 is the air-conditioning system 1001 described in the above embodiment.

According to the vehicle 1000 of the embodiment of the present application, the electric rotor compressor 100 of the air conditioning system 1001 thereof forms a first exhaust chamber 41 between the first bearing 15 and the first housing 21, and the compression component 101 discharges the compressed high-pressure fluid to the first exhaust chamber 41, and then enters the oil separation chamber 30 for gas-liquid separation. The oil separation chamber 30 is not directly inlet at the middle position of the housing component 102 (including the second bearing), which reduces the strong correlation between the oil separation position, the exhaust position and the structure of the middle position of the housing component 102. The assembly difficulty of the electric rotor compressor 100 is low, and the difficulty of modifying the exhaust structure and the oil separation structure is low when they need to be modified, which is useful for improving the application range of the parts of the electric rotor compressor 100. In the present application, the first connecting channel 32 and the second connecting channel 34 are formed on the shell wall of the first housing 21 to complete the inlet and outlet of the oil separation chamber 30, which reduces the number of pipes on the one hand, and can use the strength and rigidity of the first housing 21 on the other hand 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 rotor compressor 100. In summary, this is beneficial to noise reduction of the vehicle 1000 .

It should be noted that in the present application, the specific type of the above-mentioned vehicle 1000 is not limited. For example, the vehicle 1000 can be a traditional fuel vehicle or a new energy vehicle. The so-called new energy vehicles include but are not limited to pure electric vehicles, extended-range electric vehicles, hybrid vehicles, fuel cell electric vehicles, hydrogen engine vehicles, etc.

In some embodiments, the new energy vehicle may be a pure electric vehicle with a motor as the main driving force. In other embodiments, the new energy vehicle may also be a hybrid vehicle with both an internal combustion engine and a motor as the main driving force. Regarding the internal combustion engine and the motor mentioned in the above embodiments that provide driving power for the new energy vehicle, the internal combustion engine may use gasoline, diesel, hydrogen, etc. as fuel, and the way to provide electrical energy to the motor may use a power battery, a hydrogen fuel cell, etc., which are not specifically limited here. It should be noted that this is only an exemplary description of the structure of new energy vehicles, etc., and does not limit the scope of protection of this application.

In the description of this specification, the description with reference to the terms "embodiment", "example", etc. means that the specific features, structures, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the present application. In this specification, the schematic representation of the above terms does not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described can be combined in any one or more embodiments or examples in a suitable manner.

Although the embodiments of the present application have been shown and described, those skilled in the art will appreciate that various changes, modifications, substitutions and variations may be made to the embodiments without departing from the principles and spirit of the present application, and that the scope of the present application is defined by the claims and their equivalents.

Claims (20)

An electric rotor compressor, comprising: A shell component, the shell component includes a first shell, a refrigerant discharge port is formed on the first shell, the first shell is provided with an oil separation chamber, a first communication channel and a second communication channel are formed in the shell wall of the first shell, and the oil separation outlet of the oil separation chamber is connected with the refrigerant discharge port through the first communication channel; A compression component, at least part of which is housed in the first housing, the compression component comprising a cylinder assembly, a piston, a crankshaft, a first bearing and a second bearing, the piston being arranged in the cylinder assembly, the first bearing and the second bearing being fitted 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 and being communicated with the first exhaust chamber, and the oil separation inlet of the oil separation chamber being communicated with the first exhaust chamber through the second communicating channel. The electric rotary compressor according to claim 1, wherein the housing member includes a bracket, the compression member 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, a second exhaust chamber is defined between the second bearing and the bracket, the compression component has a second exhaust port and is connected to the second exhaust chamber, and the second exhaust chamber is connected to the first exhaust chamber. The electric rotor compressor according to claim 2, wherein an exhaust passage is provided in the compression component, and the second exhaust chamber is connected to the first exhaust chamber through the exhaust passage. The electric rotor compressor according to claim 2 or 3, wherein the compression component is fixed to the bracket through the second bearing, the end surface of the first bearing and the first shell are clearance-fitted, and a first seal is provided between the first bearing and the first shell to seal the first exhaust chamber. The electric rotor compressor according to claim 4, wherein the fitting clearance between the end surface of the first bearing and the first housing is between 0.05 mm and 1 mm. The electric rotor compressor according to claim 4 or 5, wherein the first sealing member is a rubber member or an elastic gasket. An electric rotor compressor according to any one of claims 2-6, wherein a first accommodating cavity is formed between the bracket and the first shell, a balancing channel is formed on the first shell, one end of the balancing channel is connected to the upper part of the first accommodating cavity, and the other end is connected to the first connecting channel. The electric rotary compressor according to any one of claims 1-7, further comprising a first muffler arranged in the first exhaust chamber. The electric rotary compressor according to any one of claims 2 to 7, further comprising a second muffler disposed in the second exhaust chamber. The electric rotor compressor according to any one of claims 1 to 9, wherein the first bearing comprises: a first flange and a first journal, the first journal having a first central hole, the first flange extending radially outward from an outer peripheral wall of the first journal; One side of the first flange is connected to the cylinder assembly, and a first outer seal is provided between the other side and the first housing; One end of the crankshaft is inserted into the first center hole, and a first inner seal is provided between the outer peripheral surface of the first journal and the first housing; The first exhaust chamber is located radially outside the first journal and between the first flange and the first housing. The electric rotor compressor according to any one of claims 1 to 10, further comprising an oil separator inner tube disposed in the oil separator chamber, wherein the inner cavity of the oil separator inner tube is formed as an air outlet cavity connected to the oil separator outlet, and a cyclone cavity is formed between the oil separator chamber and the oil separator inner tube; The oil inlet is located outside the oil inner tube and between two ends of the oil inner tube in the length direction. The electric rotor compressor according to claim 11, wherein the flow area of the air outlet cavity 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. The electric rotor compressor according to claim 11, wherein an oil storage chamber is defined in the shell component, and an oil return hole communicating with the oil storage chamber is provided at the lower end of the oil separation chamber. The electric rotor compressor according to claim 13, wherein the flow area of the air outlet cavity is S1, there is at least one oil return hole, the sum of the flow areas of all the oil return holes is S3, and S3 accounts for 60% to 120% of S1. The electric rotor compressor according to any one of claims 1-14, further comprising a filtering device arranged in the oil separation chamber, the filtering device comprising a first filter element located between the oil separation outlet and the oil separation inlet. The electric rotary compressor according to any one of claims 1 to 15, wherein the oil separator inlet extends along a tangential direction of the oil separator chamber. The electric rotor compressor according to any one of claims 1 to 16, wherein the oil separation chamber is formed in the shell wall of the first shell. The electric rotor compressor according to claim 17, wherein the oil separation chamber is located on a side of the first exhaust chamber away from the second bearing. An air conditioning system, comprising an electric rotary compressor according to any one of claims 1-18. A vehicle comprises: a vehicle body and an air conditioning system mounted on the vehicle body, wherein the air conditioning system is the air conditioning system according to claim 19.