Electric compressor, air conditioning system and vehicle

Abstract

The invention discloses an electric compressor, an air conditioning system and a vehicle. The electric compressor comprises a shell assembly, wherein a high-pressure cavity and an oil pool connected with the high-pressure cavity are arranged in the shell assembly; the compression mechanism is arranged in the shell assembly and comprises a crankshaft, an air cylinder and a sealing cover part, the air cylinder is provided with an air cylinder cavity, the sealing cover part sleeves the crankshaft and is arranged on the end face of the air cylinder to seal the air cylinder cavity, and the crankshaft penetrates through the air cylinder and the sealing cover part; a medium-pressure oil storage cavity is formed between the inner circumferential face of the sealing cover component and the outer circumferential face of the crankshaft. A throttling oil supply structure communicated with the medium-pressure oil storage cavity and the oil pool is arranged on the sealing cover component. By arranging the medium-pressure oil storage cavity and the throttling oil supply structure, the leakage amount of lubricating oil flowing to the air suction cavity through the gap can be reduced, abrasion of internal parts is reduced, the oil spitting amount of the electric compressor is reduced, oil shortage damage of the electric compressor is reduced, and the volume efficiency and performance are improved.

Description

Technical Field

[0001] The present invention relates to the technical field of compressors, and in particular to an electric compressor, an air-conditioning system and a vehicle. Background Art

[0002] 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. During the use of the electric compressor, lubricating oil is required to lubricate the friction pair in the electric compressor to reduce the noise generated when the friction pair is working.

[0003] In electric compressors, the piston cavity in the cylinder is high pressure and the suction cavity is low pressure. The gap between them is sealed by the high coordination of the piston and the cylinder. However, during the entire working cycle, the existence of high pressure in the piston cavity allows the lubricating oil to leak through the gap to the low-pressure suction cavity. The leakage of lubricating oil will cause the suction in the cylinder suction cavity to heat and expand, and the infiltrated lubricating oil will occupy the suction volume. A large proportion of refrigerant is also dissolved in the leaked high-pressure lubricating oil. The refrigerant released after the pressure of the cold ice oil drops will also occupy the suction volume, resulting in a decrease in volumetric efficiency and a decrease in compressor performance. When there is too much leaked oil, it will also cause the hydraulic oil in the cylinder to compress the compressor liquid, and the bearing load will increase sharply, which is very easy to cause wear of the mechanical part. At the same time, when there is more oil in the cylinder, it will also cause the compressor to discharge more lubricating oil, resulting in an increase in the oil discharge rate of the compressor, a decrease in the oil level of the compressor, and the compressor is prone to oil shortage and damage. Summary of the invention

[0004] The present invention aims to solve at least one of the technical problems existing in the prior art. To this end, the present invention is to provide an electric compressor to improve the problem of excessive leakage of lubricating oil caused by excessive pressure difference between the inner cavity of the piston and the suction cavity.

[0005] The present invention further provides an air conditioning system having the electric compressor.

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

[0007] An electric compressor according to an embodiment of the present invention comprises: a shell assembly, wherein a high-pressure chamber and an oil pool connected to the high-pressure chamber are provided in the shell assembly; a compression mechanism, wherein the compression mechanism is arranged in the shell assembly, and the compression mechanism comprises a crankshaft, a cylinder and a cover component, wherein the cylinder is provided with a cylinder chamber, the cover component is sleeved on the crankshaft and is arranged on the end surface of the cylinder to cover the cylinder chamber, and the crankshaft passes through the cylinder and the cover component; wherein a medium-pressure oil storage chamber is provided between the inner circumferential surface of the cover component and the outer circumferential surface of the crankshaft; and a throttling oil supply structure which is respectively connected to the medium-pressure oil storage chamber and the oil pool is provided on the cover component.

[0008] According to the electric compressor of the embodiment of the present invention, by providing a medium-pressure oil storage chamber and a throttling oil supply structure, the throttling oil supply structure reduces the pressure difference between the medium-pressure oil storage chamber and the suction chamber, and can reduce the leakage of lubricating oil flowing into the suction chamber through the gap, thereby reducing the suction heating in the suction chamber caused by lubricating oil leakage, reducing the suction volume occupied by lubricating oil, and reducing the liquid refrigerant brought by the lubricating oil flowing into the suction chamber. After the consumption of lubricating oil to the suction chamber is reduced, the lubricating oil plays a greater role in lubrication, which is conducive to reducing the load of the cover component, reducing the wear of internal parts, reducing the oil discharge of the electric compressor, reducing the oil shortage damage of the electric compressor, and improving the volumetric efficiency and performance.

[0009] In some embodiments, the throttling oil supply structure includes an oil supply channel provided on the cover component and connected to the medium-pressure oil storage chamber at one end, and the throttling oil supply structure also includes at least one of the following structures:

[0010] A throttle tube, one end of which is disposed in the oil supply channel to communicate with the medium-pressure oil storage chamber, and the other end of which is located in the oil pool;

[0011] A throttle hole that is alternately opened and closed, wherein the throttle hole is a node at any point on the flow path of the oil supply channel, and the other end of the oil supply channel in this structure is connected to the oil pool;

[0012] A throttle valve is arranged at any position on the flow path of the oil supply channel. In this structure, the other end of the oil supply channel is connected to the oil pool.

[0013] In some specific embodiments, the throttling oil supply structure includes the throttling tube, and the inner diameter of the throttling tube ranges from 0.1 mm to 0.5 mm.

[0014] Specifically, the throttling oil supply structure includes the throttling tube, and the throttling oil supply structure also includes: a filter tube, and the filter tube is sleeved on the outside of the throttling tube.

[0015] Furthermore, one end of the filter tube is located in the oil supply channel, the other end of the filter tube is located in the oil pool and exceeds the throttling tube, and the end of the filter tube located in the oil pool is provided with a blockage.

[0016] In other specific embodiments, the throttling oil supply structure includes the throttling hole, and the throttling hole is alternately opened and closed by a sliding vane of the compression mechanism;

[0017] Wherein, a vane groove is provided on the cylinder, the vane reciprocates in the vane groove, one end of the vane groove away from the crankshaft is connected to the oil pool, and the throttle hole is opened on the inner wall of the vane groove.

[0018] Furthermore, the throttling oil supply structure is provided with a filtering structure at one end connected to the oil pool.

[0019] In some embodiments, the structure of the throttling oil supply structure satisfies: under a pressure difference of 0.25 MPa, the flow rate range of the throttling oil supply structure is 0.5 L / min-5 L / min.

[0020] In some embodiments, a low-pressure chamber separated from the high-pressure chamber is provided in the shell assembly, a refrigerant inlet connected to the low-pressure chamber is provided on the shell assembly, and the low-pressure chamber is provided on both axial sides of the cover component.

[0021] Specifically, a center hole is provided on the crankshaft, and the center hole penetrates the crankshaft in the axial direction, and the center hole is connected to the low-pressure chambers on both sides.

[0022] Furthermore, the section of the crankshaft surrounded by the cylinder and the cover component is a closed section without a communicating hole;

[0023] The communicating hole refers to a hole provided on the crankshaft, with one end located on the outer circumferential surface of the crankshaft and the other end located on the inner circumferential surface of the center hole.

[0024] In some embodiments, an oil outlet gap is provided between the inner circumferential surface of the cover component and the outer circumferential surface of the crankshaft on at least one side of the medium-pressure oil storage chamber in the axial direction.

[0025] In some embodiments, the compression mechanism is one of the following structures:

[0026] Structure 1: There is one cylinder, the cover component includes a first bearing and a second bearing, the first bearing and the second bearing are matched on both sides of the axial direction of the cylinder, and the medium-pressure oil storage chamber is arranged on the inner side of at least one of the first bearing and the second bearing;

[0027] Structure 2: There are at least two cylinders, and the covering component includes a middle partition plate arranged between two adjacent cylinders. The covering component also includes a first bearing and a second bearing. The first bearing and the second bearing are located on the side of the two outermost cylinders away from each other, and the medium-pressure oil storage chamber is arranged on the inner side of at least one of the middle partition plate, the first bearing, and the second bearing.

[0028] Furthermore, the cover component further comprises a partition plate connected to the housing assembly, and the first bearing is fixedly connected to the partition plate;

[0029] When it is the structure one, the throttling oil supply structure is arranged on at least one of the partition plate, the first bearing, and the second bearing; when it is the structure two, the throttling oil supply structure is arranged on at least one of the partition plate, the middle partition plate, the first bearing, and the second bearing.

[0030] In some specific embodiments, the shell assembly includes a first shell and a second shell, the first shell and the second shell are connected to opposite sides of the partition plate, a low-pressure chamber is formed between the first shell and the partition plate, and the high-pressure chamber is formed between the partition plate and the second shell;

[0031] The crankshaft is partially located in the first shell and partially located in the second shell, the end of the second bearing is closed and connected to the second shell, and the center hole in the crankshaft is axially penetrated to form another low-pressure chamber between the end of the second bearing and the second shell.

[0032] In some specific embodiments, when the compression mechanism is the structure 1, the medium-pressure oil storage chamber includes at least one of a first annular chamber and a second annular chamber;

[0033] When the compression mechanism is the second structure, the medium-pressure oil storage chamber includes at least one of the first annular chamber, the second annular chamber and the third annular chamber;

[0034] Wherein, the first annular cavity is an annular groove formed on the inner peripheral surface of the first bearing and having a first opening on the side facing the cylinder, and the first opening is covered by the piston in the cylinder and the eccentric part on the crankshaft;

[0035] The second annular cavity is an annular groove formed on the inner circumference of the second bearing and having a second opening on the side facing the cylinder, and the second opening is covered by the piston in the cylinder and the eccentric part on the crankshaft;

[0036] The third annular cavity is an annular cavity between the inner circumference of the shaft hole of the middle partition and the outer circumference of the crankshaft. Both sides of the third annular cavity are sealed by the piston in the cylinder and the eccentric part on the crankshaft.

[0037] An air conditioning system according to a second aspect of the present invention comprises an electric compressor according to any one embodiment of the first aspect of the present invention.

[0038] According to the air conditioning system of the present invention, by adopting the above-mentioned electric compressor, the wear of internal parts is reduced, the oil discharge amount of the electric compressor is reduced, the oil shortage damage of the electric compressor is reduced, and the volumetric efficiency and performance are improved.

[0039] A vehicle according to a third aspect 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 according to the second aspect of the present invention.

[0040] According to the vehicle of the present invention, when the above air conditioning system is used in the vehicle, the cooling efficiency of the vehicle can be improved and the energy consumption can be reduced.

[0041] Additional aspects and advantages of the present invention will be given in part in the following description and in part will be obvious from the following description, or will be learned through practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0042] Figure 1 is a cross-sectional schematic diagram of an electric compressor (some structural parts are hidden) according to some embodiments of the present invention;

[0043] Figure 2 is a cross-sectional view of a compression mechanism and a throttling oil supply structure of some embodiments of the present invention;

[0044] Figure 3 yes Figure 2 A cross-sectional view of the throttling oil supply structure in the illustrated embodiment;

[0045] Figure 4 are cross-sectional views of compression mechanisms and throttling oil supply structures of other embodiments of the present invention;

[0046] Figure 5 yes Figure 4 A partial enlarged view of the embodiment shown;

[0047] Figure 6 is a schematic diagram of a vehicle according to an embodiment of the present invention.

[0048] Reference numerals:

[0049] Electric compressor 100;

[0050] Shell assembly 1;

[0051] A first shell 11, a second shell 12, a low-pressure chamber 14, a high-pressure chamber 15, and an oil pool 16;

[0052] Compression mechanism 2;

[0053] Crankshaft 21, center hole 211, closed section 212, eccentric portion 213,

[0054] Cylinder 22, cylinder chamber 221, slide groove 222,

[0055] The cover member 23, the first bearing 231, the second bearing 232, the middle partition plate 233, the shaft hole 2331, the partition plate 234, the slide 24, the stop spring 241,

[0056] The medium pressure oil storage chamber 25, the first annular chamber 251, the first opening 2511, the second annular chamber 252, the second opening 2521, and the third annular chamber 253;

[0057] Piston 26, oil gap 27,

[0058] Throttling oil supply structure 5, oil supply channel 51, throttling tube 52, throttling hole 53, filtering structure 54, filtering tube 541, plugging 55, sealing ring 56,

[0059] Air conditioning system 200 and vehicle 300 . DETAILED DESCRIPTION

[0060] Embodiments of the present invention 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 invention, and cannot be understood as limiting the present invention.

[0061] In the description of the present invention, it is to be understood that the terms “center”, “longitudinal”, “lateral”, “length”, “up”, “down”, “front”, “back”, “left”, “right”, “vertical”, “horizontal”, “top”, “bottom”, “inside”, “outside”, “axial”, “radial”, “circumferential”, etc., indicating orientations or positional relationships are based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as limiting the present invention.

[0062] In addition, the terms "first" and "second" are used for descriptive purposes only and should not be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features. Therefore, the features defined as "first" and "second" may explicitly or implicitly include one or more of the features. In the description of the present invention, the meaning of "plurality" is two or more, unless otherwise clearly and specifically defined.

[0063] Hereinafter, a motor-driven compressor 100 , an air-conditioning system 200 , and a vehicle 300 according to embodiments of the present invention will be described with reference to the accompanying drawings.

[0064] According to the electric compressor 100 of the embodiment of the present invention, Figure 1 As shown, it comprises: a housing assembly 1 and a compression mechanism 2. A high pressure chamber 15 is provided in the housing assembly 1, and an oil pool 16 connected to the high pressure chamber 15 is also provided in the housing assembly 1, or a part of the high pressure chamber 15 is used as the oil pool 16.

[0065] Specifically, a refrigerant outlet and a refrigerant inlet are provided on the shell assembly 1. External refrigerant enters the electric compressor 100 from the refrigerant inlet, and the high-pressure refrigerant compressed by the electric compressor 100 is discharged from the refrigerant outlet. Therefore, the pressure of the refrigerant inlet is a suction pressure with a lower air pressure, and the pressure of the refrigerant outlet is a discharge pressure with a higher air pressure.

[0066] In the present application, a low-pressure chamber 14 may be provided in the shell assembly 1, and the refrigerant inlet is connected to the low-pressure chamber 14. The compression mechanism 2 takes in air from the low-pressure chamber 14, and the pressure in the low-pressure chamber 14 is a suction pressure with a lower air pressure. The low-pressure chamber 14 may not be provided in the shell assembly 1, and the refrigerant inlet directly delivers the suction pressure with a lower air pressure to the compression mechanism 2 for compression. In the present application, the refrigerant outlet is connected to the high-pressure chamber 15, and the high-pressure refrigerant compressed by the compression mechanism 2 is directly discharged to the high-pressure chamber 15, and then discharged from the refrigerant outlet. Therefore, the high-pressure chamber 15 has a higher exhaust pressure, and the hydraulic pressure at the oil pool 16 is higher.

[0067] In the present application, when a low-pressure chamber 14 is provided, the shell assembly 1 can divide the interior of the shell assembly 1 into a low-pressure chamber 14 and a high-pressure chamber 15 through the partition plate 234 mentioned below, and the shell assembly 1 can also directly divide the interior of the shell assembly 1 into a low-pressure chamber 14 and a high-pressure chamber 15 through the first bearing 231 mentioned below. The formation structure of each chamber is not limited here.

[0068] Reference Figure 1 and Figure 2 , Figure 4The compression mechanism 2 is arranged in the housing assembly 1, and the compression mechanism 2 includes a crankshaft 21, a cylinder 22 and a cover component 23. The cylinder 22 is provided with a cylinder cavity 221, and the cover component 23 is sleeved on the crankshaft 21 and arranged on the end surface of the cylinder 22 to cover the cylinder cavity 221, and the crankshaft 21 passes through the cylinder 22 and the cover component 23.

[0069] Specifically, at least one cylinder 22 is provided in the compression mechanism 2. Each cylinder 22 is provided with a cylinder cavity 221 and a vane groove 222, and a reciprocating vane 24 is provided in the vane groove 222. The crankshaft 21 passes through the cylinder cavity 221, and the eccentric portion 213 of the crankshaft 21 is located in the cylinder cavity 221. The piston 26 is sleeved on the eccentric portion 213 to rotate eccentrically in the cylinder cavity 221. One end of the vane 24 abuts against the outer peripheral surface of the piston 26, and the eccentric rotation of the piston 26 drives the vane 26 to reciprocate in the vane groove 222. Among them, as Figure 4 As shown, a stop spring 241 is provided in the slide groove 222, and the stop spring 241 presses against one end of the slide 24, so that the other end of the slide 24 is kept in a stop state with the outer peripheral surface of the piston 26. Of course, the stop spring 241 in the present application can also be replaced by other structures.

[0070] Of course, the type of compression mechanism 2 in the present application is not limited to this. In some schemes, one end of the slide 24 is rotatably connected to the piston 26, so the slide 24 swings back and forth in the cylinder 22. In the cylinder cavity 221 and outside the piston 26, one side of the slide 24 is an air suction cavity, which sucks low-pressure refrigerant gas from the refrigerant inlet or the low-pressure cavity 14, so the pressure of the air suction cavity is relatively low. One side of the slide 24 is a compression cavity, which compresses the gas and discharges it, and the pressure of the compression cavity is higher than the pressure of the air suction cavity. The cylinder 22 is provided with a cover component 23 on both sides of the axial direction to seal the above-mentioned compression cavity and the air suction cavity.

[0071] Of course, the electric compressor 100 in the present application also includes a motor (not shown in the figure), which is located in the housing assembly 1 and connected to the crankshaft 21, and drives the piston 26 to work by driving the crankshaft 21 to rotate. Here, the motor and the compression mechanism 2 can be located in the high-pressure chamber 15, and the motor can also be located in the low-pressure chamber 14, which is not limited here. Since the motor is a known structure in the prior art, its structure and working principle are not described in detail here.

[0072] It is understandable that since the suction chamber in the cylinder 22 is at low pressure, while the pressure in the piston chamber is relatively high, the lubricating oil in the piston chamber is usually driven by the pressure difference between the high pressure and the low pressure. If the pressure difference between the two is too large, the high-pressure lubricating oil in the piston chamber is easy to leak into the low-pressure suction chamber through the gap, resulting in adverse effects.

[0073] To solve this problem, the present application proposes to set a medium-pressure oil storage chamber 25 between the inner circumference of the cover component 23 and the outer circumference of the crankshaft 21, and the electric compressor 100 also includes a throttling oil supply structure 5, which is arranged on the cover component 23. The throttling oil supply structure 5 can be connected to the medium-pressure oil storage chamber 25 at one end to supply lubricating oil to the medium-pressure oil storage chamber 25. The throttling oil supply structure 5 can be connected to the oil pool 16 at the other end to suck lubricating oil from the oil pool 16. In this way, the throttling oil supply structure 5 supplies the lubricating oil in the oil pool 16 to the medium-pressure oil storage chamber 25, and since the medium-pressure oil storage chamber 25 is located between the inner circumference of the cover component 23 and the outer circumference of the crankshaft 21, the lubricating oil flows along the outer circumference of the crankshaft 21 and is replenished into the inner cavity of the piston. Among them, since the suction chamber in the cylinder 22 is in a low-pressure environment, under the action of the pressure difference, the lubricating oil in the high-pressure environment will flow toward the low-pressure environment. Thus, the lubricating oil flows driven by the pressure difference, and the lubricating oil in the oil pool 16 can be automatically supplied to the medium-pressure oil storage chamber 25, and the lubricating oil in the medium-pressure oil storage chamber 25 automatically flows to the suction chamber, thereby lubricating the moving parts inside the compression mechanism 2, such as the contact surface between the crankshaft 21 and the piston 26, the contact surface between the piston 26 and the slide 24 and the cover part 23, etc., thereby reducing friction and loss. It should be noted that the "high pressure", "medium pressure" and "low pressure" mentioned in the present invention do not specifically refer to specific pressure values, but are only used to indicate the difference in pressure between the two chambers.

[0074] In the present application, the throttling oil supply structure 5 is provided so that the oil pool 16 is restricted by throttling when flowing toward the medium-pressure oil storage chamber 25. That is to say, the amount of oil supplied to the medium-pressure oil storage chamber 25 is lower than the amount of oil flowing from the oil pool 16 to the medium-pressure oil storage chamber 25 when it is driven entirely by the pressure difference. Such a throttling setting can make the hydraulic pressure in the medium-pressure oil storage chamber 25 lower than the hydraulic pressure in the oil pool 16. Since the pressure in the suction chamber in the cylinder 22 is often relatively low, after the throttling oil supply structure 5 is provided, the hydraulic pressure in the medium-pressure oil storage chamber 25 is still higher than that in the suction chamber, but the pressure difference is lower than when the throttling oil supply structure 5 is not provided. Although the pressure difference is reduced, the pressure difference that still exists will still drive the refrigerant oil in the medium-pressure oil storage chamber 25 to flow toward the suction chamber in the cylinder 22, thereby lubricating the contact surface between the crankshaft 21 and the piston 26, the contact surface between the piston 26 and the slide 24 and the cover component 23, etc.

[0075] That is to say, the "medium pressure" mentioned in the naming of the "medium pressure oil storage chamber 25" of the present application does not limit the specific pressure value of the oil storage chamber, but is only a modifier added to distinguish the oil storage chamber from other oil storage chambers. The hydraulic pressure of the oil storage chamber will be lower than the oil pool 16 due to the flow restriction of the lubricating oil by the throttling oil supply structure 5; due to the cooperation between the piston 26 and the sealing component 23 in the compression mechanism 2, the flow of the lubricating oil from the inner cavity of the piston to the suction chamber is restricted, and the hydraulic pressure of the oil storage chamber will be higher than the suction chamber, so the oil storage chamber is referred to as the "medium pressure oil storage chamber 25" in the present application.

[0076] The setting of the throttling oil supply structure 5 reduces the pressure difference between the medium-pressure oil storage chamber 25 and the suction chamber, which can reduce the leakage of lubricating oil flowing into the suction chamber through the gap, thereby reducing the suction heating in the suction chamber caused by lubricating oil leakage, reducing the suction volume occupied by lubricating oil, and reducing the liquid refrigerant brought by the lubricating oil flowing into the suction chamber. After the consumption of lubricating oil to the suction chamber is reduced, the lubricating oil plays a greater role in lubrication, which is conducive to reducing the load of the cover component 23, reducing the wear of internal parts, reducing the oil discharge of the electric compressor 100, reducing the oil shortage damage of the electric compressor 100, and improving the volumetric efficiency and performance.

[0077] In some embodiments, the electric compressor 100 is a horizontal compressor, the crankshaft 21 is arranged horizontally, and the throttling oil supply structure 5 is arranged at the lower part of the compression mechanism 2. Further, the lower end of the throttling oil supply structure 5 can be connected to the bottom of the oil pool 16 to absorb the lubricating oil.

[0078] In some embodiments, Figure 1 As shown, a low-pressure chamber 14 is provided in the shell assembly 1, and the low-pressure chamber 14 is separated from the high-pressure chamber 15, and can be separated by the compression mechanism 2 itself or by the shell assembly 1, which is not limited here. Among them, on both axial sides of the cover part 23, the low-pressure chamber 14 can be provided on only one side, or there can be low-pressure chambers 14 on both sides. When there are low-pressure chambers 14 on both sides, a refrigerant inlet connected to the low-pressure chambers 14 is provided on the shell assembly 1, and the refrigerant inlet can be directly connected to one of the low-pressure chambers 14, and then other structures are used to make the two low-pressure chambers 14 communicate with each other. The refrigerant inlet can also be indirectly connected to the two low-pressure chambers 14 through an intermediate structure.

[0079] It is understandable that the crankshaft 21 is not only in contact with the piston 26 in the cylinder 22, but the cover component 23 also supports the rotation of the crankshaft 21, and there is a large friction between the two due to the relative rotation. Therefore, by forming low-pressure chambers 14 on both axial sides of the cover component 23, there is a pressure difference between the medium-pressure oil storage chamber 25 and the low-pressure chamber 14, so that the pressure difference can drive the lubricating oil from the medium-pressure oil storage chamber 25 to the low-pressure chamber 4, which is conducive to efficient lubrication of the contact surface between the cover component 23 and the crankshaft 21, and reducing the friction loss between the two.

[0080] Furthermore, if Figure 2 As shown, an oil outlet gap 27 is provided between the inner circumferential surface of the cover component 23 and the outer circumferential surface of the crankshaft 21 on at least one side of the medium-pressure oil storage chamber 25 in the axial direction.

[0081] It is understandable that, since the cover part 23 is used to support the crankshaft 21 to rotate, there is a certain gap between the two to prevent the cover part 23 from locking the crankshaft 21. Therefore, even without the oil outlet gap 27 of the present application, the conventional assembly gap between the cover part 23 and the crankshaft 21 can allow the lubricating oil to flow. It should be noted here that the assembly gap between the cover part 23 (such as the bearing mentioned below) and the crankshaft 21 has been standardized in the industry. The oil outlet gap 27 provided in the present application is larger than the standardized assembly gap in the prior art, which is conducive to the inflow of more lubricating oil, thereby further reducing the load on the crankshaft 21 and improving its lubrication and protection effect on the moving parts in the compression mechanism 2.

[0082] In addition, in order to avoid affecting the rotation support function of the cover member 23 on the crankshaft 21, an oil outlet gap 27 is usually formed only between a portion of the inner circumference of the cover member 23 and the outer circumference of the crankshaft 21. Figure 2 In the embodiment, only in a section of the first bearing 231 and the second bearing 232 adjacent to the cylinder 22 , an oil outlet gap 27 is formed between the inner circumference of the cover member 23 at this position and the outer circumference of the crankshaft 21 through deformation of the inner circumference.

[0083] In addition, the oil outlet gap 27 is set to be in a gap shape, and its purpose is also to perform throttling control when the lubricating oil flows from the medium-pressure oil storage chamber 25 to the low-pressure chambers 14 on both sides, so as to avoid excessive outflow of lubricating oil from the oil outlet gap 27 and cause oil shortage inside the cylinder 22, and to avoid gas leakage from the oil outlet gap 27 to the low-pressure chamber 14, thereby ensuring operating efficiency.

[0084] Optionally, the oil outlet gap 27 can be set on one side or on both sides of the medium-pressure oil storage chamber 25. One or at least two intervals can be set on each side. Each oil outlet gap 27 can be set at a full angle (i.e. 360 degrees) or only at a partial angle (i.e. less than 360 degrees) relative to the axis of the crankshaft 21.

[0085] In some specific embodiments, Figure 1 and Figure 2 As shown, a center hole 211 is provided on the crankshaft 21, and the center hole 211 penetrates the crankshaft 21 axially, and the center hole 211 connects the low-pressure chambers 14 on both sides. In this way, low-pressure chambers 14 are provided on both axial sides of the cover component 23, and the structure is easier to implement. In the present application, if the center hole 211 is not used to form low-pressure chambers 14 on both sides of the cover component 23, a connecting channel can also be formed in the shell wall of the shell component 1 with the help of the shell component 1, and then one end of the connecting channel is connected to a low-pressure chamber 14 connected to the refrigerant inlet, and the other end extends to the closed chamber formed by the cover component 23 and the shell component 1. After the connection, the closed chamber also becomes a low-pressure chamber 14.

[0086] Specifically, when the crankshaft 21 is provided with a center hole 211 and is connected to the low-pressure chamber 14, the section of the crankshaft 21 surrounded by the cylinder 22 and the cover member 23 is a closed section 212 without a connecting hole. The connecting hole here refers to a hole provided on the crankshaft 21, with one end located on the outer circumference of the crankshaft 21 and the other end located on the inner circumference of the center hole 211. In other words, there is no hole connected to the center hole 211 on the closed section 212 surrounded by the cylinder 22 and the cover member 23, and in particular, there is no radial connecting hole provided on the closed section 212. In this way, the pressure drop in the medium-pressure oil storage chamber 25 will not be too large, which is conducive to maintaining the pressure difference between the medium-pressure oil storage chamber 25 and the suction chamber in the cylinder 22, and ensuring the oil supply flow path of the lubricating oil under the action of the pressure difference. It can also avoid unnecessary losses caused by excessive lubricating oil flowing into the center hole 211.

[0087] Of course, the present application is not limited to this. In some solutions, when a connecting hole is provided, a throttling structure can be provided on the connecting hole to prevent excessive flow of lubricating oil to the center hole 211.

[0088] In some embodiments, the structure of the throttling oil supply structure 5 satisfies: under a pressure difference of 0.25MPa, the flow rate of the throttling oil supply structure 5 is in the range of 0.5L / min-5L / min. Of course, in actual use, the pressure difference between the oil pool 16 and the medium-pressure oil storage chamber 25 will fluctuate up and down, and when it fluctuates, the flow rate of the throttling oil supply structure 5 will also fluctuate. When the pressure difference increases, the flow rate will increase, and when the pressure difference decreases, the flow rate will decrease.

[0089] It can be understood here that the limitation of this parameter is a structural limitation of the throttling oil supply structure 5. When the pressure difference at both ends of the throttling oil supply structure 5 is 0.25 MPa, the fluid flow rate flowing from the throttling oil supply structure 5 to the medium-pressure oil storage chamber 25 is 0.5L / min-5L / min due to the structural limitation of the throttling oil supply structure 5. For example, under a pressure difference of 0.25 MPa, the flow rate of the throttling oil supply structure 5 can be 0.5L / min, 1.2L / min, 1.5L / min, 2.1L / min, 3.0L / min, 3.5L / min, 4.0L / min, 4.5L / min, 5.0L / min, etc.

[0090] Among them, under the pressure difference of 0.25 MPa, the flow rate of the throttling oil supply structure 5 is at least 0.5L / min, which ensures that sufficient lubricating oil is continuously supplied to the compression mechanism 2 and reduces the possibility of interruption. In addition, the compression mechanism 2 is unstable under extreme working conditions, so the flow rate is limited to at least 0.5L / min, so that when the pressure difference at both ends of the throttling oil supply structure 5 fluctuates greatly under extreme working conditions, it can still effectively ensure its continuous flow, improve lubrication reliability, and reduce the stuck phenomenon caused by transition wear under extreme working conditions. Under the pressure difference of 0.25 MPa, the flow rate of the throttling oil supply structure 5 should not exceed 5L / min. On the one hand, the oil amount in the medium-pressure oil storage chamber 25 is kept appropriate to avoid accumulation caused by excessive oil, which is conducive to maintaining appropriate pressure in the medium-pressure oil storage chamber 25 and will not rise too high. On the other hand, after the lubricating oil flows to the compression mechanism 2, it takes a period of time to return to the oil pool 16, so the flow rate of the throttling oil supply structure 5 is limited to avoid interruption caused by untimely reflux due to excessive consumption of the oil pool 16.

[0091] Of course, in some solutions, when other safeguards are provided, the range of the flow rate through the throttling oil supply structure 5 may be appropriately relaxed to meet the requirements of different compressors.

[0092] In the present application, the structural type of the throttling oil supply structure 5 is not limited. For example, in some embodiments, the throttling oil supply structure 5 includes an oil supply channel 51, which is provided on the cover component 23, one end of which is connected to the medium-pressure oil storage chamber 25, and the aperture of the oil supply channel 51 is set to be extremely small, thereby reducing the flow rate. Of course, this structure has high requirements for the aperture control of the oil supply channel 51. In order to reduce the processing cost requirements of the oil supply channel 51, other structures can also be used to complete the designed flow rate restriction.

[0093] For example, in some specific embodiments, Figure 2 and Figure 3 As shown, the throttling oil supply structure 5 further includes a throttling tube 52, one end of which is arranged in the oil supply channel 51 to communicate with the medium-pressure oil storage chamber 25, and the other end of the throttling tube 52 is located in the oil pool 16. That is, the throttling tube 52 is arranged separately, and the throttling tube 52 is inserted into the oil supply channel 51, and the inner diameter of the throttling tube 52 is used to limit the flow rate of the throttling oil supply structure 5. With such a design, the inner diameter of the oil supply channel 51 directly processed on the cover component 23 can be enlarged, and the processing difficulty can be greatly reduced.

[0094] In addition, after the throttle tube 52 is set, its material is not restricted by the material selection of the cover member 23, and its length can also be redesigned as required. When the throttle tube 52 is long, it can be inserted into the bottom of the oil pool 16 very conveniently, thereby the fully separated lubricating oil is sucked away.

[0095] When the throttling tube 52 is provided, the throttling tube 52 can be processed into a straight tube or a curved tube and can be designed arbitrarily, and the design flexibility is high.

[0096] Optionally, the inner diameter d1 of the throttle tube 52 is greater than or equal to 0.1 mm and does not exceed 0.5 mm. Optionally, the inner diameter d1 can be 0.1 mm, 0.2 mm, 0.3 mm, 0.4 mm, 0.5 mm, etc. This is conducive to controlling the flow rate of the throttling oil supply structure 5 within a suitable range. Among them, the inner diameter d1 of the throttle tube 52 should not be too small to reduce the probability of being blocked by impurities. The inner diameter d1 of the throttle tube 52 should not be too large to avoid the throttle tube 52 being too thick and occupying too much space.

[0097] Of course, the throttle tube 52 of the present application can be provided as one or at least two as required, and the inner diameter d1 of the throttle tube 52 can be adjusted appropriately.

[0098] In other specific embodiments, Figure 4 and Figure 5 As shown, the other end of the oil supply channel 51 is connected to the oil pool 16. The throttling oil supply structure 5 also includes a throttling hole 53, which is a node on the flow path of the oil supply channel 51. If this node is disconnected, the oil supply channel 51 is cut off at this point, and the oil supply channel 51 is cut off. If this node is opened, the oil supply channel 51 is connected at this point.

[0099] The throttle hole 53 can be opened and closed alternately, and the position of the throttle hole 53 on the oil supply channel 51 is not limited, and can be anywhere on its flow path. Therefore, the flow rate of the throttling oil supply structure 5 can also be limited, and in this structure, the flow control is only performed at the node, the control accuracy is high, and the probability of flow blockage at other positions is reduced, so that the flow reliability of the throttling oil supply structure 5 can be improved.

[0100] In an optional example, a solenoid valve for opening and closing the throttle hole 53 may be provided, and the throttle hole 53 may be controlled by the activity of the solenoid valve. The positions of the solenoid valve and the throttle hole 53 may be selected flexibly.

[0101] In another alternative example, Figure 4 and Figure 5 As shown, the throttle hole 53 is alternately opened and closed by the slide vane 24 of the compression mechanism 2, which can save the number of parts and avoid the oil supply channel 51 being blocked or uncontrolled oil supply caused by the loss of the solenoid valve.

[0102] Specifically, the cylinder 22 is provided with a slide groove 222, and the slide 24 reciprocates in the slide groove 222. The end of the slide groove 222 away from the crankshaft 21 is connected to the oil pool 16, and one end of the throttle hole 53 is located on the inner wall of the slide groove 222, and the other end of the throttle hole 53 is located on the inner wall of the throttle channel 51. This can also increase the lubrication efficiency of the lubricating oil on the slide 24. In addition, the reciprocating movement of the slide 24 is driven by the crankshaft 21. When there is foreign matter at the throttle hole 53, the slide 24 can be used to clean the throttle hole 53, remove dirt, and ensure smooth flow.

[0103] Of course, the scheme of the present application may not be limited to the above scheme. For example, the throttling oil supply structure 5 may also include a throttle valve, and the location of the throttle valve is also a node on the flow path of the oil supply channel 51. The location of the throttle valve on the oil supply channel 51 is not limited, and can be anywhere on its flow path. The throttle valve can use a throttle valve structure known in the prior art, which is mature in technology and has a wide range of throttling effect options.

[0104] Alternatively, a flow control pump is provided to supply oil to the medium-pressure oil storage chamber 25 , but relatively speaking, the above solution has higher cost and stronger reliability.

[0105] In some specific embodiments, the throttling oil supply structure 5 is provided with a filter structure 54 at one end connected to the oil pool 16, thereby reducing the probability of blockage of the oil supply path and reducing the probability of impurities being introduced into the compression mechanism 2 and causing scratches on the surface of the parts. Here, the filter structure 54 can be flexibly arranged, for example, a filter net can be covered on the end of the throttling oil supply structure 5, or a filter element can be inserted at the end.

[0106] In some optional embodiments, such as Figure 2 and Figure 3 As shown, the throttling oil supply structure 5 includes a throttling tube 52, and the throttling oil supply structure 5 also includes: a filter tube 541, and the filter tube 541 is sleeved on the outside of the throttling tube 52. In this way, the filtering effect of the tube wall is utilized, the filtering area is relatively large, the filtering speed is fast, and the probability of the mesh being completely blocked is low.

[0107] Specifically, one end of the filter tube 541 is located in the oil supply channel 51, and the other end of the filter tube 541 is located in the oil pool 16 and exceeds the throttling tube 52. The end of the filter tube 541 located in the oil pool 16 is provided with a plug 55. This filter tube 541 has low cost and is easy to assemble.

[0108] Furthermore, the throttling oil supply structure 5 also includes a sealing ring 56, which is sleeved outside the filter tube 541 to ensure that the filter tube 541 and the throttling tube 52 are tightly connected here and reduce the risk of the throttling tube 52 and the filter tube 541 falling off.

[0109] Optionally, a positioning groove is provided on the outer peripheral surface of the filter tube 541 , and the positioning groove is an annular groove. The sealing ring 56 is sleeved in the positioning groove to prevent the sealing ring 56 from falling off.

[0110] During assembly, the filter tube 541 can be firstly put on the outside of the throttle tube 52, and then the plug 55 can be inserted on one end of the throttle tube 52. The sealing ring 56 can be put on the filter tube 541 before the sleeve, or the sealing ring 56 can be put on the filter tube 541 after the sleeve. Then the end with the sealing ring 56 is inserted into the oil supply channel 51, and the sealing ring 56 and the oil supply channel 51 are interference fit, so that the throttle tube 52 and the filter tube 541 can be clamped. In some examples, the filter tube 541 has a certain elasticity, and is deformed after being clamped, thereby clamping the throttle tube 52.

[0111] Furthermore, a plurality of protrusions are provided on the inner wall of the filter tube 541 at one end in contact with the throttling tube 52, thereby increasing the clamping capacity and preventing the two from loosening.

[0112] Further optionally, only one end of the filter tube 541 is in contact with and connected to the throttling tube 52, and the inner diameter of the remaining portion of the filter tube 541 is larger than the outer diameter of the throttling tube 52, forming a gap therebetween to facilitate accommodating the filtered lubricating oil.

[0113] In the above embodiment, the shape of the throttling tube 52 is not limited, and it can be a round tube, a square tube, or a square outer tube and a round inner tube.

[0114] In order to further understand the position and structural arrangement of the medium-pressure oil storage chamber 25 and the throttling oil supply structure 5 in the present application scheme, the following is a description in combination with different embodiments.

[0115] In some embodiments, the compression mechanism 2 is structure one: the compression mechanism 2 is a single-cylinder structure, that is, there is one cylinder 22, and the cover component 23 includes a first bearing 231 and a second bearing 232. The first bearing 231 is matched on one side of one cylinder 22, and the second bearing 232 is matched on the other side of another cylinder 22. The first bearing 231 and the second bearing 232 are located at the axial ends of the cylinder group composed of all cylinders 22, and the medium-pressure oil storage chamber 25 is arranged on the inner side of at least one of the first bearing 231 and the second bearing 232.

[0116] In other embodiments, Figure 2 and Figure 4As shown, the compression mechanism 2 is structure two: the compression mechanism 2 is a multi-cylinder structure, there are at least two cylinders 22, the cover component 23 includes a middle partition 233 arranged between two adjacent cylinders 22, the cover component 23 also includes a first bearing 231 and a second bearing 232, the first bearing 231 and the second bearing 232 are located on the side of the two outermost cylinders 22 away from each other, and the medium-pressure oil storage chamber 25 is arranged on the inner side of at least one of the middle partition 233, the first bearing 231, and the second bearing 232.

[0117] That is to say, in the present application scheme, whether the compression mechanism 2 is a single-cylinder structure or a multi-cylinder structure, a medium-pressure oil storage chamber 25 can be provided to supply oil. When it is structure one, the throttling oil supply structure 5 is provided on at least one of the first bearing 231 and the second bearing 232; when it is structure two, the throttling oil supply structure 5 is provided on at least one of the middle partition plate 233, the first bearing 231, and the second bearing 232.

[0118] Regardless of the single-cylinder structure or the multi-cylinder structure, the cover component 23 may further include a partition plate 234 connected to the housing assembly 1, and the first bearing 231 is fixedly connected to the partition plate 234. When it is structure 1, the throttling oil supply structure 5 is provided on at least one of the partition plate 234, the first bearing 231, and the second bearing 232; when it is structure 2, the throttling oil supply structure 5 is provided on at least one of the partition plate 234, the middle partition plate 233, the first bearing 231, and the second bearing 232.

[0119] The partition plate 13 is provided to facilitate assembly on the one hand, and to improve the overall structural rigidity of the housing assembly 1 on the other hand, thereby increasing its anti-seismic, anti-bending and anti-torsion properties.

[0120] In some specific embodiments, Figure 1 As shown, the housing assembly 1 includes a first housing 11 and a second housing 12, the first housing 11 and the second housing 12 are connected to opposite sides of a partition plate 234, a low-pressure chamber 14 is formed between the first housing 11 and the partition plate 234, and a high-pressure chamber 15 is formed between the partition plate 234 and the second housing 12. The arrangement of the partition plate 13 enables the housing assembly 1 to form different pressure chambers on both sides thereof to meet the operation requirements of the compression mechanism 2. The motor is located in the low-pressure chamber 14, and most of the parts of the compression mechanism 2 are located in the high-pressure chamber 15.

[0121] Specifically, the crankshaft 21 is partially located in the first housing 11 and partially located in the second housing 12, the end of the second bearing 232 is closed and connected to the second housing 12, and the center hole 211 in the crankshaft 21 is axially penetrated, so that another low-pressure chamber 14 is formed between the end of the second bearing 232 and the second housing 12. In this way, low-pressure chambers 14 are provided on both axial sides of the cover component 23, and the structure is easy to implement. In this way, it is very convenient to form low-pressure chambers 14 on both axial sides of the cover component 23, and there is a pressure difference between the medium-pressure oil storage chamber 25 and the low-pressure chamber 14, so that the pressure difference can drive the lubricating oil from the medium-pressure oil storage chamber 25 to the low-pressure chamber 4, which is conducive to efficient lubrication of the contact surface between the cover component 23 and the crankshaft 21, and reduce the friction loss between the two.

[0122] In some specific embodiments, when the compression mechanism 2 is structure 1, the medium-pressure oil storage chamber 25 includes at least one of the first annular chamber 251 and the second annular chamber 252. When the compression mechanism 2 is structure 2, the medium-pressure oil storage chamber 25 includes at least one of the first annular chamber 251, the second annular chamber 252 and the third annular chamber 253.

[0123] The first annular cavity 251 is an annular groove formed on the inner circumference of the first bearing 231 and having a first opening 2511 on the side facing the cylinder 22 . The first opening 2511 is sealed by the piston 26 in the cylinder 22 and the eccentric portion 213 on the crankshaft 21 .

[0124] The second annular cavity 252 is an annular groove formed on the inner circumference of the second bearing 232 and having a second opening 2521 on the side facing the cylinder 22 . The second opening 2521 is sealed by the piston 26 in the cylinder 22 and the eccentric portion 213 on the crankshaft 21 .

[0125] The third annular cavity 253 is an annular cavity between the inner circumference of the through-shaft hole 2331 of the middle diaphragm 233 and the outer circumference of the crankshaft 21. Both sides of the third annular cavity 253 are sealed by the piston 26 in the cylinder 22 and the eccentric portion 213 on the crankshaft 21. That is, the middle diaphragm 233 is provided with a through-shaft hole 2331, and the crankshaft 21 is passed through the through-shaft hole 2331 of the middle diaphragm 233. The inner diameter of the through-shaft hole 2331 is larger than the outer diameter of the crankshaft 21, and the third annular cavity 253 can be formed between the two.

[0126] With this arrangement, the medium-pressure oil storage chamber 25 and the inner chamber of the adjacent piston 22 can be directly connected, and the lubricating oil in the medium-pressure oil storage chamber 25 can be quickly supplied to the interior of the piston 22 for lubrication.

[0127] Here, the medium-pressure oil storage chamber 25 may include one or more of the first annular chamber 251, the second annular chamber 252 and the third annular chamber 253. When the medium-pressure oil storage chamber 25 includes two of the first annular chamber 251, the second annular chamber 252 and the third annular chamber 253, the throttling oil supply structure 5 may be connected to one or two of them, or each annular chamber may be connected to the throttling oil supply structure 5. Since each annular chamber 251 is connected to the adjacent piston inner chamber, the internal medium-pressure lubricating oil may flow to another adjacent annular chamber through the piston inner chamber.

[0128] In some specific embodiments, the medium-pressure oil storage chamber 25 includes a first annular cavity 251 and a second annular cavity 252 , but does not include a third annular cavity 253 . In this case, the throttling oil supply structure 5 can be connected to both the first annular cavity 251 and the second annular cavity 252 .

[0129] In other specific embodiments, Figure 4 As shown, the medium-pressure oil storage chamber 25 includes the third annular chamber 253, but does not include the first annular chamber 251 and the second annular chamber 252. At this time, the throttling oil supply structure 5 can be connected only to the third annular chamber 253 to supply oil to the piston cavities on both sides.

[0130] In short, this solution is conducive to the distribution of lubricating oil to the surfaces of various moving parts, and is conducive to the uniform distribution of lubricating oil inside the compression mechanism 2.

[0131] In some specific embodiments, a motor is disposed in the first housing 11 . The motor includes a stator and a rotor. The rotor can rotate relative to the stator. The rotor is connected to the crankshaft 21 to drive the crankshaft 21 to rotate.

[0132] The assembly of the electric compressor 100 includes the following steps: S1, installing the stator in the first housing 11; S2, installing the throttling oil supply structure 5 on the cover component 23; S3, after step S2, installing the compression mechanism 2 without the partition plate 234 in the second housing 12; S4, after step S3, installing the partition plate 234 to one end of the second housing 12, and sleeve the partition plate 234 on the first bearing 231; S5, after step S4, installing the rotor and the crankshaft 21; S6, after step S5, placing the first housing 11 on the other side of the partition plate 234, and adjusting the assembly gap between the rotor and the stator;

[0133] S7. After step S6, the second shell 12 and the first shell 11 are fixedly connected to the partition plate 234 respectively, and the sealing of the connection is ensured.

[0134] Among them, in step S1, the stator and the first housing 11 can be assembled by screws, and the stator can also be fixed in the first housing 11 by a shrink-fit process. In step S2, the throttling oil supply structure 5 is installed by first putting a filter tube 541 on the outside of the throttling tube 52, and then putting a sealing ring 56 on the outer sleeve of the filter tube 541, and then plugging a plug 55 at one end of the filter tube 541. The other end of the filter tube 541 is provided with a sealing ring 56, and this end is inserted into the oil supply channel 51. The sealing ring 56 and the oil supply channel 51 are interference fit. The first bearing 231, the second bearing 232, the middle partition plate 233, and the cylinder 22 of the compression mechanism 2 can be assembled by bolting and then fixed on the partition plate 234. The welding process can also be used to fix the compression mechanism 2 in the second housing 12.

[0135] It should be noted that the specific type of the electric compressor 100 is not limited, and for example, it may be a horizontal compressor in which the axis of the crankshaft 21 extends in the horizontal direction or is slightly inclined to the horizontal line.

[0136] Other structures of the electric compressor 100 according to the embodiment of the present invention, such as the electric control principle and the operation thereof, are known to those skilled in the art and will not be described in detail here.

[0137] The air conditioning system 200 according to the embodiment of the present invention comprises the electric compressor 100 of any one of the above embodiments. Thus, by adopting the above electric compressor 100, the wear of internal parts is reduced, the oil discharge amount of the electric compressor 100 is reduced, the oil shortage damage of the electric compressor 100 is reduced, and the volumetric efficiency and performance are improved.

[0138] It should be noted that the specific application scenarios of the air-conditioning system 200 according to the embodiment of the present invention are not limited, such as indoor air conditioning, indoor refrigerator, vehicle air conditioning, etc. When the application scenario is determined, technical personnel in this field can know other components of the air-conditioning system 200. For example, when used for indoor air conditioning or indoor refrigerator, it can also include an evaporator, a condenser, a throttling element, etc. For example, when used for a vehicle air conditioner, it can also include an in-vehicle condenser, an in-vehicle evaporator, an outdoor condenser, an outdoor evaporator, at least one of the throttling components, etc., which will not be repeated here.

[0139] like Figure 6 As shown, a vehicle 300 according to an embodiment of the present invention comprises: a vehicle body and an air conditioning system 200 mounted on the vehicle body, wherein the air conditioning system 200 is the air conditioning system 200 of any of the above embodiments. Since the internal parts of the electric compressor 100 included in the air conditioning system 200 of any of the above embodiments have reduced wear, reduced oil discharge, and improved volumetric efficiency and performance, when the air conditioning system 200 is used in the vehicle 300, the cooling efficiency of the vehicle can be improved and energy consumption can be reduced.

[0140] It should be noted that the specific type of the vehicle 300 according to the embodiment of the present invention is not limited, for example, it can be a new energy vehicle, and the new energy vehicle can include a pure electric vehicle, a hybrid vehicle, etc., which will be described in detail here. In addition, when the type of the vehicle 300 is specifically determined, those skilled in the art can know other components of the vehicle 300, which will not be described in detail here.

[0141] The electric compressor 100 according to some specific embodiments of the present invention is described below.

[0142] First embodiment

[0143] like Figure 1-Figure 3 As shown, the exemplary electric compressor 100 is a rotary electric compressor, comprising a housing assembly 1 and a compression mechanism 2. The compression mechanism 2 is used to compress and convert a low-pressure refrigerant into a high-pressure refrigerant.

[0144] The housing assembly 1 includes a first housing 11 and a second housing 12 , the compression mechanism 2 includes a crankshaft 21 , a cylinder 22 , a slide vane 24 , a piston 26 and a cover component 23 , and the cover component 23 includes a first bearing 231 , a second bearing 232 , a middle partition plate 233 and a partition plate 234 .

[0145] The first shell 11 and the second shell 12 are connected to opposite sides of the partition plate 234, a low-pressure chamber 14 is formed between the first shell 11 and the partition plate 234, and a high-pressure chamber 15 is formed between the partition plate 234 and the second shell 12. Most of the parts of the compression mechanism 2 are arranged in the high-pressure chamber 15 and are fixedly connected to the shell assembly 1 through the partition plate 234.

[0146] The compression mechanism 2 is a two-cylinder compression mechanism, with two cylinders 22. The middle partition 233 is arranged between two adjacent cylinders 22. The first bearing 231 and the second bearing 232 are located on the side of the two cylinders 22 away from each other. The crankshaft 21 passes through the partition 234, the first bearing 231, one cylinder 22, the middle partition 233, another cylinder 22, and the second bearing 232 in sequence.

[0147] In each cylinder 22, the crankshaft 21 has an eccentric portion 213, and the plug 26 is sleeved on the eccentric portion 213 to rotate eccentrically in the cylinder chamber 221. One end of the slide 24 abuts against the outer peripheral surface of the piston 26, and the eccentric rotation of the piston 26 drives the slide 26 to reciprocate in the slide groove 222.

[0148] The crankshaft 21 is partially located in the first housing 11 and partially located in the second housing 12. The end of the second bearing 232 is closed and connected to the second housing 12. The center hole 211 in the crankshaft 21 penetrates axially to form another low-pressure chamber 14 between the end of the second bearing 232 and the second housing 12.

[0149] The compression mechanism 2 is provided with a medium-pressure oil storage chamber 25, which includes a first annular chamber 251, a second annular chamber 252 and a third annular chamber 253. The first annular chamber 251 is an annular groove formed on the inner circumference of the first bearing 231 and having a first opening 2511 on the side facing the cylinder 22, the second annular chamber 252 is an annular groove formed on the inner circumference of the second bearing 232 and having a second opening 2521 on the side facing the cylinder 22, and the third annular chamber 253 is an annular chamber between the inner circumference of the through-shaft hole 2331 of the middle partition plate 233 and the outer circumference of the crankshaft 21.

[0150] The electric compressor 100 also includes a throttling oil supply structure 5, which is arranged on the second bearing 232. The throttling oil supply structure 5 supplies the lubricating oil in the oil pool 16 to the second annular cavity 252. The lubricating oil in the second annular cavity 252 flows through the inner cavity of the piston to the third annular cavity 253 and the first annular cavity 251, thereby lubricating the moving contact surfaces in the two cylinders 22 through the pressure difference.

[0151] In addition, an oil outlet gap 27 is provided between the inner circumferential surfaces of the first bearing 231 and the second bearing 232 and the outer circumferential surface of the crankshaft 21 , respectively, so as to throttle the oil outlet and lubricate the inner circumferential surfaces of the first bearing 231 and the second bearing 232 and the outer circumferential surface of the crankshaft 21 .

[0152] The throttling oil supply structure 5 includes an oil supply channel 51 provided on the second bearing 232 , and also includes a throttling tube 52 and a filter tube 541 , which supplies the filtered lubricating oil to the second annular cavity 252 .

[0153] Second embodiment

[0154] like Figure 4 and Figure 5 As shown, the second embodiment is basically the same as the first embodiment, except that the oil supply channel 51 is provided on the middle partition plate 233, and the throttling oil supply structure 5 includes a throttling hole 53. Specifically, one end of the throttling hole 53 is located on the inner wall of the vane groove 222, and the other end of the throttling hole 53 is located on the inner wall of the throttling channel 51 and serves as the opening of the oil supply channel 51. The vane 24 reciprocates in the vane groove 222, and the end of the vane groove 222 away from the crankshaft 21 is connected to the oil pool 16, so as to realize the alternating opening and closing of the throttling hole 53.

[0155] Third embodiment

[0156] The third embodiment (not shown) is basically the same as the first embodiment, except that the compression mechanism 2 is a single-cylinder structure, including only one cylinder 22 and eliminating the middle partition plate 233. The medium-pressure oil storage chamber 25 includes a first annular chamber 251 and a second annular chamber 252, while the third annular chamber 253 is eliminated.

[0157] Fourth embodiment

[0158] The fourth embodiment (not shown) is basically the same as the third embodiment, except that there are two throttling oil supply structures 5, which are respectively arranged on the first bearing 231 and the second bearing 232, one of the throttling oil supply structures 5 is connected to the first annular cavity 251, and the other throttling oil supply structure 5 is connected to the second annular cavity 252.

[0159] Fifth embodiment

[0160] The fifth embodiment (not shown) is substantially the same as the first embodiment, except that the partition plate 234 is removed from the electric compressor 100, the housing assembly 1 is substantially filled with the high-pressure chamber 15, and the compression mechanism 2 is directly placed in the high-pressure chamber 15. The low-pressure refrigerant at the refrigerant inlet directly enters the suction chamber of the compression mechanism 2 through the suction pipe.

[0161] In order to support the rotation of the crankshaft 21 , bearings may be further provided at opposite ends of the housing assembly 1 .

[0162] Sixth embodiment

[0163] The sixth embodiment (not shown) is substantially the same as the first embodiment, except that the throttling oil supply structure 5 is disposed on the first bearing 231 .

[0164] Seventh embodiment

[0165] The seventh embodiment (not shown) is basically the same as the first embodiment, except that the throttling oil supply structure 5 is arranged on the partition plate 234 and the first bearing 231, wherein a part of the oil supply channel 51 is located on the first bearing 231 to connect to the first annular cavity 251, and another part of the oil supply channel 51 is located on the partition plate 234, and the throttling tube 52 is installed on the partition plate 234.

[0166] Eighth embodiment

[0167] The eighth embodiment (not shown) is substantially the same as the first embodiment, except that the throttle tube 52 is replaced by a throttle valve.

[0168] Ninth embodiment

[0169] The ninth embodiment (not shown) is basically the same as the first embodiment, except that the throttling oil supply structure 5 includes two oil supply channels 51, one located on the first bearing 231 and the other located on the second bearing 232, and there are two throttling tubes 52, which are respectively located at the two oil supply channels 51.

[0170] Tenth embodiment

[0171] The tenth embodiment (not shown) is basically the same as the first embodiment, except that the throttling oil supply structure 5 includes two oil supply channels 51, one of which is located on the middle partition plate 233 and the other is located on the second bearing 232, and a throttling tube 52 is inserted into the oil supply channel 51 on the second bearing 232. The throttling oil supply structure 5 includes a throttling hole 53 arranged on the middle partition plate 233, one end of the throttling hole 53 is located on the inner wall of the slide groove 222, and the other end of the throttling hole 53 is located on the inner wall of the throttling channel 51 and serves as the opening of the oil supply channel 51. When the slide 24 reciprocates in the slide groove 222, the throttling hole 53 is alternately opened and closed.

[0172] Eleventh Embodiment

[0173] The eleventh embodiment (not shown) is substantially the same as the first embodiment, except that, in the first embodiment, the axis of the crankshaft 21 extends horizontally, and the electric compressor 100 is a horizontal compressor. In the eleventh embodiment, the axis of the crankshaft 21 extends vertically, and the electric compressor 100 is a vertical compressor.

[0174] 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 invention. 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.

[0175] Although the embodiments of the present invention have been shown and described, it will be appreciated by those skilled in the art that various changes, modifications, substitutions and variations may be made to the embodiments without departing from the principles and spirit of the present invention, and that the scope of the present invention is defined by the claims and their equivalents.

Claims

1. An electric compressor, characterized in that: include: A shell component, wherein a high-pressure chamber and an oil pool connected to the high-pressure chamber are provided in the shell component; A compression mechanism, the compression mechanism is arranged in the housing assembly, the compression mechanism comprises a crankshaft, a cylinder and a cover component, the cylinder is provided with a cylinder cavity, the cover component is sleeved on the crankshaft and arranged on the end surface of the cylinder to cover the cylinder cavity, the crankshaft passes through the cylinder and the cover component; Wherein, a medium-pressure oil storage chamber is provided between the inner circumferential surface of the cover component and the outer circumferential surface of the crankshaft; The sealing cover component is provided with a throttling oil supply structure which is connected with the medium-pressure oil storage cavity and the oil pool respectively.

2. The electric compressor according to claim 1, characterized in that: The throttling oil supply structure includes an oil supply channel provided on the cover component and connected to the medium-pressure oil storage chamber at one end, and the throttling oil supply structure also includes at least one of the following structures: A throttle tube, one end of which is disposed in the oil supply channel to communicate with the medium-pressure oil storage chamber, and the other end of which is located in the oil pool; A throttle hole that is alternately opened and closed, wherein the throttle hole is a node at any point on the flow path of the oil supply channel, and the other end of the oil supply channel in this structure is connected to the oil pool; A throttle valve is arranged at any position on the flow path of the oil supply channel. In this structure, the other end of the oil supply channel is connected to the oil pool.

3. The electric compressor according to claim 2, characterized in that: The throttling oil supply structure includes the throttling tube, and the inner diameter of the throttling tube ranges from 0.1mm to 0.5mm.

4. The electric compressor according to claim 2, characterized in that: The throttling oil supply structure includes the throttling tube, and the throttling oil supply structure also includes: a filter tube, and the filter tube is sleeved on the outer side of the throttling tube.

5. The electric compressor according to claim 4, characterized in that: One end of the filter tube is located in the oil supply channel, the other end of the filter tube is located in the oil pool and exceeds the throttling tube, and the end of the filter tube located in the oil pool is provided with a blockage.

6. The electric compressor according to claim 2, characterized in that: The throttling oil supply structure includes the throttling hole, and the throttling hole is alternately opened and closed by the sliding vane of the compression mechanism; Wherein, a vane groove is provided on the cylinder, the vane reciprocates in the vane groove, one end of the vane groove away from the crankshaft is connected to the oil pool, and the throttle hole is opened on the inner wall of the vane groove.

7. The electric compressor according to claim 1, characterized in that: The throttling oil supply structure is provided with a filtering structure at one end connected to the oil pool.

8. The electric compressor according to any one of claims 1 to 7, characterized in that: The structure of the throttling oil supply structure satisfies: under a pressure difference of 0.25 MPa, the flow rate range of the throttling oil supply structure is 0.5L / min-5L / min.

9. The electric compressor according to any one of claims 1 to 7, characterized in that: A low-pressure chamber separated from the high-pressure chamber is provided in the shell component, a refrigerant inlet communicating with the low-pressure chamber is provided on the shell component, and the low-pressure chambers are provided on both axial sides of the cover component.

10. The electric compressor according to claim 9, characterized in that: An oil outlet gap is provided between the inner circumferential surface of the cover component and the outer circumferential surface of the crankshaft on at least one side of the medium-pressure oil storage chamber in the axial direction.

11. The electric compressor according to claim 9, characterized in that: The crankshaft is provided with a center hole, which penetrates the crankshaft in the axial direction and communicates with the low-pressure chambers on both sides.

12. The electric compressor according to claim 11, characterized in that: The section of the crankshaft surrounded by the cylinder and the cover component is a closed section without a communicating hole; The communicating hole refers to a hole provided on the crankshaft, with one end located on the outer circumferential surface of the crankshaft and the other end located on the inner circumferential surface of the center hole.

13. The electric compressor according to any one of claims 1 to 7, characterized in that: The compression mechanism is one of the following structures: Structure 1: There is one cylinder, the cover component includes a first bearing and a second bearing, the first bearing and the second bearing are matched on both sides of the axial direction of the cylinder, and the medium-pressure oil storage chamber is arranged on the inner side of at least one of the first bearing and the second bearing; Structure 2: There are at least two cylinders, and the covering component includes a middle partition plate arranged between two adjacent cylinders. The covering component also includes a first bearing and a second bearing located on both sides of all the cylinders, and the medium-pressure oil storage chamber is arranged on the inner side of at least one of the middle partition plate, the first bearing, and the second bearing.

14. The electric compressor according to claim 13, characterized in that: The cover component further comprises a partition plate connected to the housing assembly, and the first bearing is fixedly connected to the partition plate; When the compression mechanism is the structure 1, the throttling oil supply structure is provided on at least one of the partition plate, the first bearing and the second bearing; When the compression mechanism is the second structure, the throttling oil supply structure is arranged on at least one of the partition plate, the middle partition plate, the first bearing, and the second bearing.

15. The electric compressor according to claim 14, characterized in that: The shell assembly comprises a first shell and a second shell, wherein the first shell and the second shell are connected to opposite sides of the partition plate, a low-pressure chamber is formed between the first shell and the partition plate, and a high-pressure chamber is formed between the partition plate and the second shell; The crankshaft is partially located in the first shell and partially located in the second shell, the end of the second bearing is closed and connected to the second shell, and the center hole in the crankshaft is axially penetrated to form another low-pressure chamber between the end of the second bearing and the second shell.

16. The electric compressor according to claim 13, characterized in that: When the compression mechanism is structure 1, the medium-pressure oil storage chamber includes at least one of a first annular chamber and a second annular chamber; When the compression mechanism is the second structure, the medium-pressure oil storage chamber includes at least one of the first annular chamber, the second annular chamber and the third annular chamber; Wherein, the first annular cavity is an annular groove formed on the inner peripheral surface of the first bearing and having a first opening on the side facing the cylinder, and the first opening is covered by the piston in the cylinder and the eccentric part on the crankshaft; The second annular cavity is an annular groove formed on the inner circumference of the second bearing and having a second opening on the side facing the cylinder, and the second opening is covered by the piston in the cylinder and the eccentric part on the crankshaft; The third annular cavity is an annular cavity between the inner circumference of the shaft hole of the middle partition and the outer circumference of the crankshaft. Both sides of the third annular cavity are sealed by the piston in the cylinder and the eccentric part on the crankshaft.

17. An air conditioning system, characterized in that: The invention comprises the electric compressor according to any one of claims 1 to 16.

18. A vehicle, characterized in that: include: 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 17.

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