Compressor

Abstract

The invention relates to the technical field of compressors, and discloses a compressor. The compressor comprises a shell defining an internal space and comprising a shell top cover arranged at the end; the rotor assembly is arranged in the internal space; the exhaust pipe is arranged on the top cover of the shell in a penetrating mode and comprises a first opening end arranged outside the shell and a second opening end arranged in the inner space, and the second opening end extends towards the rotor assembly in a linear mode till the length of the portion, extending into the inner space, of the exhaust pipe reaches a preset value, so that the length of the portion, extending into the inner space, of the exhaust pipe is lengthened in a linear mode. On the basis of a conventional exhaust pipe, the length of the part, extending into the internal space, of the exhaust pipe is linearly lengthened, gaseous refrigerants flow into the linearly-extending exhaust pipe and flow out of the exhaust pipe along a linear path, the flowing resistance is small, it can be ensured that refrigerant gas is exhausted at high pressure, and on the basis that the oil spitting rate is reduced, the oil spitting efficiency is improved. The flow speed stability of refrigerants is kept, and the efficiency of the compressor is improved.

Description

Technical Field

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

[0002] Currently, with the upgrading of compressors, miniaturization and high speed have become the development direction. Increasing the maximum operating frequency of the compressor allows for a smaller displacement to achieve a higher cooling capacity. However, increasing the compressor speed also leads to an increased oil discharge rate. An increased oil discharge rate results in less refrigerant oil inside the compressor, which cannot guarantee lubrication of the pump body friction pairs, leading to wear of the pump body friction pairs. Refrigerant oil discharged into the air conditioning system and adhering to the pipes also reduces the heat exchange efficiency of the pipes, thereby reducing the cooling capacity of the air conditioner.

[0003] The relevant technology configures the inner section of the exhaust pipe located inside the compressor housing as one or more straight pipe sections and one or more curved pipe sections, with one or more first oil return holes provided on the wall of the curved pipe section. The curved pipe section reduces the speed at which the refrigerant flows out of the compressor, changing the direction of refrigerant flow. Furthermore, the first oil return holes on the wall of the curved pipe section allow for the separation of oil from the refrigerant through centrifugal force, thus improving the oil-gas separation effect.

[0004] In the process of implementing the embodiments of this disclosure, at least the following problems were found in the related art:

[0005] In related technologies, the curved section of the exhaust pipe has a greater resistance to the flow of refrigerant gas, which will reduce the flow rate of refrigerant, thereby affecting the pressure of the refrigerant gas output by the compressor and thus affecting the cooling effect.

[0006] It should be noted that the information disclosed in the background section above is only used to enhance the understanding of the background of this application, and therefore may include information that does not constitute prior art known to those skilled in the art. Summary of the Invention

[0007] To provide a basic understanding of some aspects of the disclosed embodiments, a brief summary is given below. This summary is not intended as a general commentary, nor is it intended to identify key / important components or describe the scope of protection of these embodiments, but rather as a prelude to the detailed description that follows.

[0008] This disclosure provides a compressor that maintains refrigerant flow rate stability while reducing oil discharge rate, thereby improving compressor efficiency.

[0009] According to a first aspect of the present invention, a compressor is provided, comprising: a housing that encloses an internal space and includes a housing top cover at one end; a rotor assembly disposed in the internal space; and an exhaust pipe that passes through the housing top cover and includes a first opening end disposed outside the housing and a second opening end disposed in the internal space, the second opening end extending linearly toward the rotor assembly until the length of the exhaust pipe extending into the internal space reaches a preset value, so that the length of the exhaust pipe extending into the internal space is linearly increased.

[0010] Optionally, the ratio between the length H of the exhaust pipe extending into the internal space and the distance C from the inner surface of the housing top cover to the top of the rotor assembly satisfies: H / C≥0.2.

[0011] Optionally, the difference between the distance from the inner surface of the housing top cover to the top of the rotor assembly and the length of the exhaust pipe extending into the internal space is greater than or equal to 10 mm.

[0012] Optionally, the length of the exhaust pipe extending into the internal space is greater than or equal to 15 mm.

[0013] Optionally, the distance from the inner surface of the housing top cover to the top of the rotor assembly is greater than or equal to 50 mm.

[0014] Optionally, the minimum cross-sectional area value E of the exhaust pipe inner diameter, the distance C from the inner surface of the housing top cover to the top of the rotor assembly, and the compressor displacement value Q satisfy the following relationship: (E×C) / Q≥0.042.

[0015] Optionally, the minimum cross-sectional area value E of the exhaust pipe inner diameter, the distance C from the inner surface of the housing top cover to the top of the rotor assembly, and the compressor displacement value Q also satisfy the following: (E×C) / Q≤0.084.

[0016] Optionally, the compressor further includes: a stator core, disposed in the internal space and sleeved on the outside of the rotor assembly, including a first end face and a second end face disposed opposite to each other, the first end face being disposed towards the top cover of the housing and the second end face being disposed away from the top cover of the housing; a main bearing base, disposed in the internal space, located on the second end face side of the stator core, extending radially along the housing, and having a third end face disposed towards the second end face; wherein, the distance A between the first end face and the inner surface of the top cover of the housing, the distance B between the second end face and the third end face, and the compressor displacement Q satisfy: A / B / Q≥0.11.

[0017] Optionally, the distance A between the first end face and the inner surface of the housing top cover, the distance B between the second end face and the third end face, and the compressor displacement Q also satisfy the following condition: A / B / Q≤0.22.

[0018] Optionally, the distance A between the first end face and the inner surface of the housing top cover, the distance B between the second end face and the third end face, and the compressor displacement Q also satisfy the following: A≥40mm, B≥20mm, A / B / Q=0.14.

[0019] The compressor provided in this embodiment can achieve the following technical effects:

[0020] The second opening end of the exhaust pipe is located in the internal space and extends linearly towards the rotor assembly until the length of the exhaust pipe extending into the internal space reaches a preset value. This linearly extends the length of the exhaust pipe into the internal space compared to a conventional exhaust pipe, allowing gaseous refrigerant to flow into the linearly extended exhaust pipe and exit along a straight path. This minimizes flow resistance and ensures that the refrigerant gas is discharged at a higher pressure, maintaining refrigerant flow rate stability while reducing oil discharge rate and improving compressor efficiency. Furthermore, the linear flow of refrigerant gas from the exhaust pipe reduces collisions with the inner wall of the exhaust pipe during flow, lowering vibration and noise levels. Compared to the curved exhaust pipe designs in related technologies, the linearly extended exhaust pipe of this embodiment also reduces production costs.

[0021] The above general description and the description below are exemplary and illustrative only and are not intended to limit this application. Attached Figure Description

[0022] One or more embodiments are exemplarily described by corresponding drawings. These exemplary descriptions and drawings do not limit the embodiments. Elements with the same reference numerals in the drawings are shown as similar elements. The drawings do not constitute a scale limitation. In addition,

[0023] Figure 1 This is a schematic diagram of a compressor structure in the prior art, where the arrows indicate the flow direction of the refrigerant gas;

[0024] Figure 2 This is a schematic diagram of a compressor structure provided in an embodiment of the present disclosure, wherein the arrows indicate the flow direction of the refrigerant gas;

[0025] Figure 3 This is another schematic diagram of a compressor structure provided in an embodiment of this disclosure, wherein the arrow indicates the radial direction of the housing;

[0026] Figure 4 yes Figure 3 An enlarged schematic diagram of section G is shown below;

[0027] Figure 5 This is a schematic diagram showing the relationship between the oil discharge rate and the H / C curve of the compressor provided in this embodiment of the disclosure;

[0028] Figure 6 This is a schematic diagram comparing the curve relationship between the oil discharge rate and the compressor operating frequency of compressors in the prior art and the compressors provided in the embodiments of this disclosure;

[0029] Figure 7 This is a schematic diagram of a rotor assembly structure provided in an embodiment of this disclosure;

[0030] Figure 8 This is a schematic diagram of another rotor assembly structure provided in an embodiment of this disclosure.

[0031] Figure label:

[0032] 100: Compressor housing; 101: Conventional exhaust pipe; 102: Air inlet; 103: Top wall of housing;

[0033] 10: Shell; 11: Internal space; 12: Top cover of the shell;

[0034] 20: Rotor assembly; 21: Rotor core; 211: Groove; 22: Oil baffle cap; 23: Positioning pin;

[0035] 30: Exhaust pipe; 31: First open end; 32: Second open end;

[0036] 40: Stator core; 41: First end face; 42: Second end face;

[0037] 50: Main bearing; 51: Main bearing base; 511: Third end face; 52: Main bearing neck. Detailed Implementation

[0038] To provide a more detailed understanding of the features and technical content of the embodiments of this disclosure, the implementation of the embodiments of this disclosure will be described in detail below with reference to the accompanying drawings. The accompanying drawings are for illustrative purposes only and are not intended to limit the embodiments of this disclosure. In the following technical description, for ease of explanation, several details are used to provide a full understanding of the disclosed embodiments. However, one or more embodiments may still be implemented without these details. In other cases, well-known structures and devices may be simplified in their depiction to simplify the drawings.

[0039] The terms "first," "second," etc., used in the specification, claims, and accompanying drawings of this disclosure are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence. It should be understood that such data can be interchanged where appropriate for the embodiments of this disclosure described herein. Furthermore, the terms "comprising" and "having," and any variations thereof, are intended to cover non-exclusive inclusion.

[0040] In this disclosure, the terms "upper," "lower," "inner," "middle," "outer," "front," and "rear," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. These terms are primarily for better description of the embodiments of this disclosure and their implementations, and are not intended to limit the indicated devices, elements, or components to having a specific orientation, or to require them to be constructed and operated in a specific orientation. Furthermore, some of the aforementioned terms may be used to indicate other meanings besides orientation or positional relationship; for example, the term "upper" may in some cases indicate a dependency or connection relationship. Those skilled in the art can understand the specific meaning of these terms in the embodiments of this disclosure according to the specific circumstances.

[0041] Furthermore, the terms "set up," "connect," and "fix" should be interpreted broadly. For example, "connection" can be a fixed connection, a detachable connection, or an integral structure; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, or it can be an internal connection between two devices, components, or parts. Those skilled in the art can understand the specific meaning of the above terms in the embodiments of this disclosure according to the specific circumstances.

[0042] Unless otherwise stated, the term "multiple" means two or more.

[0043] In this embodiment of the disclosure, the character " / " indicates that the objects before and after it are in an "or" relationship. For example, A / B means: A or B.

[0044] The term "and / or" describes an association between objects, indicating that three relationships can exist. For example, A and / or B means: A or B, or A and B.

[0045] It should be noted that, unless otherwise specified, the embodiments and features described in the present disclosure can be combined with each other.

[0046] The compressor is usually placed vertically, and the compressor refrigerant oil is located at the bottom of the compressor housing 10. Since the compressor needs to lubricate the various friction pairs in the pump body assembly, the refrigerant oil in the oil sump at the bottom of the compressor is pumped into the various friction pairs of the pump body by the oil guide plates of the crankshaft and the central oil hole. The refrigerant oil in the friction pairs will reach the cylinder compression chamber or the top of the main bearing through the gap and fully contact the compressed or discharged refrigerant gas. The refrigerant oil will be carried into the refrigerant gas in the form of tiny oil droplets, reach the upper space of the motor through the air gap of the motor assembly, and then be discharged from the compressor exhaust pipe.

[0047] like Figure 1As shown, in current technology, the conventional exhaust pipe 101 used in compressors typically has a relatively short length extending into the compressor housing 100, and the inlet end of the conventional exhaust pipe 101 is closer to the top wall 103 of the housing. In compressors using the conventional exhaust pipe 101, the refrigerant gas flows in the following direction: Figure 1 As shown, when the refrigerant flows out from the air gap of the motor assembly, it will directly enter the conventional exhaust pipe 101 through the air inlet 102. The refrigeration oil droplets carried in the refrigerant gas will be discharged from the conventional exhaust pipe 101 along with the refrigerant gas, resulting in a high oil discharge rate of the compressor.

[0048] Combination Figure 2-4 As shown, this disclosure provides a compressor, including a housing 10, a rotor assembly 20, and an exhaust pipe 30.

[0049] The housing 10 encloses an internal space 11, including a housing top cover 12 at one end; the rotor assembly 20 is disposed in the internal space 11; the exhaust pipe 30 passes through the housing top cover 12, including a first opening end 31 outside the housing 10 and a second opening end 32 inside the internal space 11, the second opening end 32 extends in a straight line toward the rotor assembly 20 until the length of the exhaust pipe 30 extending into the internal space 11 reaches a preset value, so that the length of the exhaust pipe 30 extending into the internal space 11 increases in a straight line.

[0050] The compressor provided in this application is applicable to compressors such as high-speed twin-cylinder rotary compressors.

[0051] The length of the exhaust pipe 30 extending into the internal space 11 affects the oil-gas separation effect between the refrigerant gas and the refrigeration oil. Figure 3 As shown in Figure H, the distance from the inner surface of the housing top cover 12 to the topmost point of the rotor assembly 20 is as follows: Figure 3 As shown in C. The length of the exhaust pipe 30 extending into the internal space 11 and the distance from the inner surface of the housing top cover 12 to the top of the rotor assembly 20 are both in mm.

[0052] Since the rotor assembly 20 includes an oil baffle cap 22 and a balance block, combined with Figure 3-4 As shown, the top of the rotor assembly 20 refers to the position of the rotor assembly 20 closest to the top cover 12 of the housing, and in this embodiment, it refers to the top of the oil baffle cap 22.

[0053] The exhaust pipe 30 extends in a straight line. After the length of the exhaust pipe 30 extending into the internal space 11 reaches a preset value, it can change the flow direction of the refrigerant gas, preventing the oil-containing refrigerant gas flowing out from the air gap of the motor structure from flowing directly out through the exhaust pipe 30. Instead, it flows towards the inner surface of the housing top cover 12 and recirculates in the space between the inner surface of the housing top cover 12 and the rotor assembly 20. The flow direction of the refrigerant gas in the compressor with the extended exhaust pipe is as follows: Figure 2 As shown, the refrigerant gas carrying refrigerant oil droplets swirls multiple times in the internal space 11 between the rotor assembly 20 and the housing top cover 12, making full contact with the inner surface of the housing top cover 12 and the inner surface of the side wall of the housing 10. This causes the oil carried in the refrigerant gas to adhere to the inner surface of the housing 10, and then flows back to the bottom of the compressor along the inner surface of the housing 10, completing the oil-gas separation. The refrigerant gas is then discharged from the exhaust pipe 30, thereby effectively reducing the oil discharge rate.

[0054] Air conditioning compressors need to compress low-temperature, low-pressure refrigerant into high-temperature, high-pressure refrigerant. Therefore, the refrigerant gas must be kept at a high pressure when it is discharged from the compressor.

[0055] Combination Figure 1-3 As shown, in the compressor provided by this embodiment, the second opening end 32 of the exhaust pipe 30 is located in the internal space 11 and extends linearly towards the rotor assembly 20 until the length of the exhaust pipe 30 extending into the internal space 11 reaches a preset value. This allows the length of the exhaust pipe 30 extending into the internal space 11 to be linearly extended compared to a conventional exhaust pipe 101, enabling gaseous refrigerant to flow into the linearly extended exhaust pipe 30 and out along a straight path. This results in low flow resistance and ensures that the refrigerant gas is discharged at a higher pressure. While reducing the oil discharge rate, this maintains the stability of the refrigerant flow rate and improves the compressor efficiency. Furthermore, compared to the curved pipe section design in related technologies, the linearly extended exhaust pipe 30 of this embodiment also reduces production costs.

[0056] Optionally, the ratio between the length H of the exhaust pipe 30 extending into the internal space 11 and the distance C from the inner surface of the housing top cover 12 to the top of the rotor assembly 20 satisfies: H / C≥0.2.

[0057] The length H of the exhaust pipe 30 extending into the internal space 11 and the distance C from the inner surface of the housing top cover 12 to the top of the rotor assembly 20 are as follows: Figure 3 As shown.

[0058] The compressor also includes a stator core 40 and a main bearing base 51. The stator core 40 is located in the internal space 11 and sleeved on the outside of the rotor assembly 20. It includes a first end face 41 and a second end face 42 that are disposed opposite to each other. The first end face 41 is disposed towards the top cover 12 of the housing, and the second end face 42 is disposed away from the top cover 12 of the housing. The main bearing base 51 is located in the internal space 11, on the side of the second end face 42 of the stator core 40, extends radially along the housing 10, and has a third end face 511 disposed towards the second end face 42.

[0059] Using the compressor provided in this embodiment, with the compressor operating at 60Hz, the distance between the first end face 41 and the inner surface of the housing top cover 12 being 82mm, and the distance between the second end face 42 and the third end face 511 being 25mm, the relationship between the H / C ratio and the oil discharge rate was tested. Specific test data are shown in the table below.

[0060]

[0061] The relationship between the compressor's oil discharge rate and H / C is shown in the curve. Figure 5 As shown. Combined with Figure 5 As can be seen from the data in the table above, compared to the case where H / C < 0.2, the oil discharge rate of the compressor is significantly reduced when H / C ≥ 0.2. Within the range of H / C ≥ 0.2, the oil discharge rate gradually decreases as the H / C ratio gradually increases. For example, compared to the oil discharge rate of 0.5% when H / C = 0.08, the oil discharge rate is 0.25% when H / C = 0.23, a decrease of 50%.

[0062] The compressor provided in this embodiment can significantly reduce the oil discharge rate when H / C ≥ 0.2, preventing the refrigerant oil inside the compressor from being discharged from the exhaust pipe 30, reducing the oil content of the refrigerant, and ensuring the lubrication requirements of the friction pairs. At the same time, the refrigerant gas flowing out from the straight exhaust pipe 30 can also reduce the collision with the inner wall of the exhaust pipe during the flow process, reducing vibration and noise levels.

[0063] It is understandable that since the length H of the exhaust pipe 30 extending into the internal space 11 is less than the distance C from the inner surface of the housing top cover 12 to the top of the rotor assembly 20, the ratio between the two still satisfies H / C < 1. That is, when 0.2 ≤ H / C < 1, the oil discharge rate can be significantly reduced.

[0064] It is understandable that the H / C ratio can be any value within the range of [0.2, 1). For example, 0.2, 0.23, 0.38, 0.46, 0.54, 0.62, and 0.69, etc.

[0065] Optionally, the difference between the distance from the inner surface of the housing top cover 12 to the top of the rotor assembly 20 and the length of the exhaust pipe 30 extending into the internal space 11 is greater than or equal to 10 mm.

[0066] The increased length of the exhaust pipe 30 extending into the internal space 11 facilitates the refrigerant gas carrying the refrigerant oil droplets to flow back to the inner surface of the housing top cover 12. Simultaneously, a gap must be maintained between the second open end 32 of the exhaust pipe 30 and the top of the rotor assembly 20 to allow refrigerant gas to flow in, and to prevent direct contact between the rotor assembly 20 and the exhaust pipe 30 during high-speed rotation, which could cause wear or noise. When the ratio H / C between the length of the exhaust pipe 30 extending into the internal space 11 and the distance from the inner surface of the housing top cover 12 to the top of the rotor assembly 20 is ≥0.2, and the difference between the distance from the inner surface of the housing top cover 12 to the top of the rotor assembly 20 and the length of the exhaust pipe 30 extending into the internal space 11 is greater than or equal to 10 mm, an appropriate gap for refrigerant gas flow can be maintained between the exhaust pipe 30 and the top of the rotor assembly 20, while also ensuring the stability and reliability of the rotor assembly 20 during operation.

[0067] Optionally, the length of the exhaust pipe 30 extending into the internal space 11 is greater than or equal to 15 mm.

[0068] The fact that the exhaust pipe 30 extends into the housing 10 with a length greater than or equal to 15 mm optimizes the flow path of refrigerant gas carrying refrigerant oil droplets within the internal space 11, improving oil-liquid separation. It also provides a longer refrigerant gas flow channel, reducing resistance during exhaust and thus improving compressor exhaust efficiency, helping to ensure stable compressor performance under high load or high speed. Simultaneously, the longer exhaust pipe 30 acts as a buffer, reducing airflow pulsation and noise.

[0069] It is understandable that the length of the exhaust pipe 30 extending into the internal space 11 can be 15mm, 16mm, 18mm, 20mm, 30mm, 40mm, and 45mm, etc.

[0070] Optionally, the distance from the inner surface of the housing top cover 12 to the topmost point of the rotor assembly 20 is greater than or equal to 50 mm.

[0071] The distance from the inner surface of the housing top cover 12 to the top of the rotor assembly 20 is greater than or equal to 50mm, which can provide a larger flow space for the refrigerant gas. The larger distance provides a better separation space for oil and gas, increases the contact area between oil and gas and the inner surface of the housing 10, and enables more complete oil and gas separation. This reduces the possibility of oil being carried into the exhaust pipe 30 by the refrigerant gas, allowing more oil to settle back into the oil sump and reducing the oil discharge rate.

[0072] It is understandable that the distance from the inner surface of the housing top cover 12 to the top of the rotor assembly 20 can be 50mm, 51mm, 53mm, 55mm, 60mm and 65mm, etc.

[0073] When the length of the exhaust pipe 30 extending into the internal space 11 is greater than or equal to 15 mm, and the distance from the inner surface of the housing top cover 12 to the top of the rotor assembly 20 is greater than or equal to 50 mm, the oil discharge rate can be reduced more effectively while maintaining the stability of the refrigerant flow rate. The maximum values ​​of the distance from the inner surface of the housing top cover 12 to the top of the rotor assembly 20 and the maximum value of the length of the exhaust pipe 30 extending into the internal space 11 can be limited according to the size requirements of the compressor.

[0074] Optionally, the minimum cross-sectional area value E of the inner diameter of the exhaust pipe 30, the distance C from the inner surface of the housing top cover 12 to the top of the rotor assembly 20 and the compressor displacement value Q satisfy the following: (E×C) / Q≥0.042.

[0075] The unit for the minimum cross-sectional area of ​​the 30mm inner diameter exhaust pipe is mm. 2 The distance from the inner surface of the casing top cover 12 to the topmost point of the rotor assembly 20 is measured in mm. The compressor's displacement is typically expressed in cm. 3 To measure this, this application converts the compressor displacement value Q to mm. 3 .

[0076] After the refrigerant gas flows out through the air gaps such as the flow holes in the rotor assembly 20, it flows into the internal space 11 between the rotor assembly 20 and the housing top cover 12, and then is discharged through the exhaust pipe 30. The cross-sectional area of ​​the inner diameter of the exhaust pipe 30 also has a significant impact on the pressure loss of the fluid. Increasing the cross-sectional area of ​​the inner diameter of the exhaust pipe 30 will reduce the gas velocity in the pipe, reduce the gas pressure, thereby reducing resistance loss and also reducing the possibility of oil leakage. Since the second end of the exhaust pipe 30 can be infinitely close to the top of the rotor assembly 20, as long as there is enough space for the refrigerant gas to flow, the distance from the inner surface of the housing top cover 12 to the top of the rotor assembly 20 can be regarded as the maximum length that the exhaust pipe 30 can reach into the internal space 11. In this embodiment, the product (E×C) between the minimum cross-sectional area value E of the inner diameter of the exhaust pipe 30 and the distance C from the inner surface of the housing top cover 12 to the top of the rotor assembly 20 represents the internal volume of the exhaust pipe 30 and is used to measure the gas pressure inside the exhaust pipe 30. The compressor displacement value Q is used to measure the gas pressure in the compressor pump body compression chamber. Within a certain range, increasing the internal volume of the exhaust pipe 30 can reduce the airflow pressure within the exhaust pipe 30, thereby allowing the refrigerant gas to flow from the higher-pressure space within the compressor pump body into the relatively lower-pressure space within the exhaust pipe 30, improving the smoothness of fluid flow. When (E×C) / Q≥0.042, it can reduce the pressure loss of the refrigerant fluid, lower the oil discharge rate, and help improve the compressor efficiency and reduce power consumption.

[0077] Optionally, the minimum cross-sectional area value E of the inner diameter of the exhaust pipe 30, the distance C from the inner surface of the housing top cover 12 to the top of the rotor assembly 20, and the compressor displacement value Q also satisfy the following: (E×C) / Q≤0.084.

[0078] The product of the minimum cross-sectional area E of the inner diameter of the exhaust pipe 30 and the distance C from the inner surface of the top cover 12 of the housing to the top of the rotor assembly 20 needs to be controlled within a certain range to avoid the inner diameter of the exhaust pipe 30 being too large, which would affect the gas flow rate within the exhaust pipe 30 and ensure the performance of the compressor and the stability of the system. When 0.042≤(E×C) / Q≤0.084, the oil discharge rate of the compressor can be kept low while ensuring the normal flow of refrigerant gas.

[0079] It is understandable that the ratio of (E×C) / Q can be 0.042, 0.053, 0.065, 0.072, and 0.084, etc.

[0080] Optionally, combined Figure 3-4As shown, the compressor also includes a stator core 40 and a main bearing base 51. The stator core 40 is located in the internal space 11 and sleeved on the outside of the rotor assembly 20. The stator core 40 includes a first end face 41 and a second end face 42 that are disposed opposite to each other. The first end face 41 is disposed towards the top cover 12 of the housing, and the second end face 42 is disposed away from the top cover 12 of the housing. The main bearing base 51 is located in the internal space 11, on the side of the second end face 42 of the stator core 40, extends radially along the housing 10, and has a third end face 511 disposed towards the second end face 42. The distance A between the first end face 41 and the inner surface of the top cover 12, the distance B between the second end face 42 and the third end face 511, and the compressor displacement Q satisfy the following condition: A / B / Q≥0.11.

[0081] The distance between the first end face 41 and the inner surface of the top cover 12 of the housing is as follows: Figure 3 As shown in Figure A, the distance between the second end face 42 and the third end face 511 is as follows: Figure 3 As shown in Figure B, the distance A between the first end face 41 and the inner surface of the housing top cover 12, and the distance B between the second end face 42 and the third end face 511, are both in mm. The compressor displacement value Q is in mm. 3 .

[0082] The stator core 40 and rotor assembly 20 belong to the compressor's motor assembly, while the main bearing 50 belongs to the compressor's pump body assembly. The compressor is usually placed vertically, with the pump body assembly, motor assembly, and housing top cover 12 arranged sequentially from bottom to top, and there is space between the three.

[0083] The compressor's main bearing 50 includes a main bearing base 51 and a main bearing neck 52, such as Figure 3 As shown, the main bearing 50 is located entirely on the second end face 42 side of the stator core 40. The main bearing base 51 extends radially and has a third end face 511 disposed toward the second end face 42, and the main bearing neck 52 is disposed on the main bearing base 51 and extends toward the second end face 42.

[0084] The distance A between the first end face and the inner surface of the housing top cover is taken as the spatial distance between the housing top cover 12 and the motor assembly. The distance B between the second end face and the third end face is taken as the spatial distance between the motor assembly and the pump body assembly.

[0085] After the refrigerant gas is discharged from the pump body assembly, it first flows into the space with a distance of B between the second end face 42 and the third end face 511. Then, it flows through the air gap of the motor assembly into the space with a distance of A between the first end face 41 of the upper part of the motor assembly and the inner surface of the top cover 12 of the housing. The volume of these two spaces will affect the flow effect of the gas in the air gap of the motor assembly.

[0086] Since the cross-sectional areas of the internal spaces 11 located at the stator core 40 and the main bearing 50 are the same, the ratio of the distance A between the first end face 41 and the inner surface of the housing top cover 12, and the distance B between the second end face 42 and the third end face 511, can be used to represent the volume ratio of the upper and lower spaces of the motor assembly. The larger the volume of the space, the lower the gas pressure. The ratio of A to B can be used to measure the pressure ratio of the gas flow paths in these two spaces, thereby measuring the smoothness of fluid flow within the space. To make the gas flow smoother, A should be greater than B. This allows gas to flow from the lower space of the motor assembly into the air gap of the motor assembly, and then into the upper space of the motor assembly. This is equivalent to enlarging the gas flow space, enabling gas to flow from high pressure to low pressure, reducing flow resistance, and improving flow smoothness.

[0087] The compressor's displacement value Q represents the volume of the compression chamber in the pump assembly, while A / B / Q measures the volume ratio of the critical spaces traversed by the refrigerant gas throughout the entire flow path. Within a certain range, the larger the A / B / Q ratio, the lower the fluid resistance loss, the lower the overall energy consumption, and the higher the compressor's energy efficiency.

[0088] When A / B / Q≥0.11, the distance A between the first end face 41 and the inner surface of the housing top cover 12 is larger. The increased distance between the first end face 41 and the inner surface of the housing top cover 12 can increase the inner surface area of ​​the housing 10 between the two, allowing the refrigerant to fully contact the inner surface of the housing 10, and allowing more refrigerant oil droplets to adhere to the inner surface of the housing 10. While improving the gas flow effect, it can also improve the oil-gas separation effect and reduce the compressor oil discharge rate.

[0089] Optionally, the distance A between the first end face 41 and the inner surface of the housing top cover 12, the distance B between the second end face 42 and the third end face 511, and the compressor displacement value Q also satisfy the following: A / B / Q≤0.22.

[0090] The distance between the first end face 41 and the inner surface of the housing top cover 12 is sufficient to ensure that the refrigerant gas flows smoothly from the pump assembly into the air gap of the motor assembly and into the upper space of the motor assembly. At the same time, a certain pressure is required to allow the refrigerant gas to flow from the upper space into the exhaust pipe 30, and then out of the internal space 11 of the housing 10. When 0.11 ≤ A / B / Q ≤ 0.22, the gas flow effect in the internal space 11 can be improved, the compressor oil discharge rate can be reduced, and the gas flow effect out of the exhaust pipe 30 can be guaranteed.

[0091] It is understandable that the ratio of A / B / Q can be 0.11, 0.15, 0.18, 0.20, and 0.22, etc.

[0092] Optionally, the distance A between the first end face 41 and the inner surface of the housing top cover 12, the distance B between the second end face 42 and the third end face 511, and the compressor displacement Q also satisfy the following: A≥40mm, B≥20mm, A / B / Q=0.14.

[0093] When A≥40mm, B≥20mm, and A / B / Q=0.14, the oil discharge rate can be reduced more effectively, minimizing the oil discharge rate of the compressor.

[0094] Optionally, combined Figure 7 As shown, the rotor assembly 20 includes a rotor core 21. A groove 211 is provided on one side of the end face of the rotor core 21 along the axial direction. The groove 211 is eccentrically arranged relative to the axis of the rotor core 21 so that the solid on the other side of the end face forms a built-in counterweight balance part.

[0095] This embodiment eliminates the external balance block. Instead, an internal counterweight balance section is formed by eccentrically setting a groove 211 on one side of the axial end face of the rotor core 21. This is equivalent to embedding the balance block inside the rotor core 21, preventing collisions between the balance block and refrigerant and refrigerant oil droplets, reducing the stirring effect of the balance block on the refrigerant oil droplets, and thus lowering the oil discharge rate. At this time, the absence of a balance block interferes with the flow field between the oil baffle cap 22 and the rotor core 21, and the gap is radially symmetrical along the oil baffle cap 22. This allows oil droplets to be evenly and smoothly thrown out onto the inner surface of the side wall of the housing 10 under centrifugal force after flowing through the flow holes of the rotor core 21, and then flow into the bottom of the compressor, reducing the oil discharge rate.

[0096] It is understandable that a groove 211 can be provided on one end face of the rotor core 21 along the axial direction, or a groove 211 can be provided on both end faces of the rotor core 21 along the axial direction.

[0097] Optionally, combined Figure 3-4 and Figure 8 As shown, the rotor assembly 20 also includes an oil baffle cap 22, which covers the rotor core 21 on the side facing the housing top cover 12 and has a gap between it and the rotor core 21. The gap is radially symmetrical along the oil baffle cap 22.

[0098] As mentioned in the above embodiments, lengthening the exhaust pipe 30 or increasing the distance between the inner surface of the housing top cover 12 and the rotor assembly 20 can improve the oil-gas separation effect, thereby reducing the oil discharge rate. Based on this, an oil baffle cap 22 is provided on the side of the rotor core 21 facing the housing top cover 12. The oil baffle cap 22 can stop the oil, preventing the refrigerant oil droplets from flowing out directly, but instead allowing them to flow out from the side through the gap between the oil baffle cap 22 and the rotor core 21. Under the guiding action of the oil baffle cap 22, the refrigerant oil droplets are allowed to flow back, thereby reducing oil loss and improving the oil return effect. The gap between the oil baffle cap 22 and the rotor core 21 is arranged symmetrically along the radial direction of the oil baffle cap 22, reducing flow resistance when the oil flows out from the side.

[0099] Specifically, the oil baffle cap 22 is provided with multiple positioning posts 23 extending toward the rotor core 21. The multiple positioning posts 23 are arranged symmetrically around the circumference of the oil baffle cap 22. The rotor core 21 is provided with multiple positioning holes around the circumference. After the rivets pass through the positioning posts 23, they cooperate with the positioning holes, which can fix the oil baffle cap 22 to the end face of the rotor core 21. The obstruction of the external balance block between the oil baffle cap 22 and the rotor core 21 is eliminated. The multiple positioning posts 23 are arranged symmetrically around the circumference of the oil baffle cap 22, which can divide the gap between the end face of the oil baffle cap 22 and the rotor core 21 into multiple symmetrical gaps.

[0100] The straight, extended exhaust pipe 30 provided in this application allows the refrigerant to flow to the inner surface of the housing top cover 12 after exiting the air gap of the motor assembly, and then flow back to the second opening end 32 of the exhaust pipe 30. This creates a vortex in the internal space 11 between the motor assembly and the housing top cover 12. Most of the refrigerant oil droplets carried in the refrigerant adhere to the inner surface of the housing 10 through full contact with it, and then flow downwards along the housing 10 into the oil sump at the bottom of the compressor. A portion of the refrigerant oil droplets drips directly onto the oil baffle cap 22 during the downward flow from the inner surface of the housing top cover 12, and are then thrown back onto the inner surface of the housing 10 by the centrifugal force of the high-speed rotation of the oil baffle cap 22, thus flowing downwards along the inner surface of the housing 10 back into the compressor oil sump. This effectively achieves gas-liquid separation and reduces the compressor's oil discharge rate.

[0101] The oil discharge rate of a compressor using the conventional exhaust pipe 101 scheme in the prior art and a compressor using the extended exhaust pipe 30 scheme provided in this embodiment were tested at different operating frequencies. The conventional exhaust pipe 101 scheme and the extended exhaust pipe 30 scheme used the same model of compressor and were installed and tested in the same batch. Under the same test conditions, the distance from the inner surface of the housing top cover to the top of the rotor assembly was 65mm. The length of the conventional exhaust pipe 101 extending into the internal space 11 was 5mm, and the length of the exhaust pipe 30 provided in this embodiment extending into the internal space 11 was 35mm.

[0102] The specific test data is shown in the table below.

[0103]

[0104] The curve relationship between oil discharge rate and compressor operating frequency of the compressor in the prior art and the compressor provided in the embodiments of this disclosure is as follows: Figure 6 As shown. Combined with Figure 6 As shown in the table above, at the same frequency, the oil discharge rate of the compressor using the extended exhaust pipe 30 is significantly lower than that of the compressor using the conventional exhaust pipe 101. With increasing compressor operating frequency, the oil discharge rate of the compressor using the conventional exhaust pipe 101 increases significantly, while the oil discharge rate of the compressor using the extended exhaust pipe 30 provided in this embodiment increases, but the increase is small. Moreover, under high-frequency operation, the reduction in oil discharge rate of the compressor using the extended exhaust pipe 30 provided in this embodiment is more significant compared to the compressor using the conventional exhaust pipe 101 in the prior art.

[0105] The foregoing description and accompanying drawings fully illustrate embodiments of the present disclosure to enable those skilled in the art to practice them. Other embodiments may include structural and other changes. The embodiments represent only possible variations. Individual components and functions are optional unless explicitly required, and the order of operation may vary. Parts and features of some embodiments may be included or substituted for parts and features of other embodiments. Embodiments of the present disclosure are not limited to the structures described above and shown in the accompanying drawings, and various modifications and changes may be made without departing from its scope. The scope of the present disclosure is limited only by the appended claims.

Claims

1. A compressor, characterized in that, include: The shell, which encloses the internal space, includes a shell top cover located at the end; The rotor assembly is located within the internal space; An exhaust pipe is installed on the top cover of the housing and includes a first opening end located outside the housing and a second opening end located inside the housing. The second opening end extends in a straight line toward the rotor assembly until the length of the exhaust pipe extending into the housing reaches a preset value, so that the length of the exhaust pipe extending into the housing increases in a straight line.

2. The compressor according to claim 1, characterized in that, The ratio between the length H of the exhaust pipe extending into the internal space and the distance C from the inner surface of the housing top cover to the top of the rotor assembly satisfies: H / C≥0.

2.

3. The compressor according to claim 2, characterized in that, The difference between the distance from the inner surface of the housing top cover to the top of the rotor assembly and the length of the exhaust pipe extending into the internal space is greater than or equal to 10 mm.

4. The compressor according to claim 2, characterized in that, The length of the exhaust pipe extending into the internal space is greater than or equal to 15mm.

5. The compressor according to claim 2, characterized in that, The distance from the inner surface of the housing top cover to the top of the rotor assembly is greater than or equal to 50 mm.

6. The compressor according to any one of claims 1 to 5, characterized in that, The minimum cross-sectional area value E of the exhaust pipe inner diameter, the distance C from the inner surface of the housing top cover to the top of the rotor assembly, and the compressor displacement value Q satisfy the following condition: (E×C) / Q≥0.

042.

7. The compressor according to claim 6, characterized in that, The minimum cross-sectional area value E of the exhaust pipe inner diameter, the distance C from the inner surface of the housing top cover to the top of the rotor assembly, and the compressor displacement value Q also satisfy the following: (E×C) / Q≤0.

084.

8. The compressor according to any one of claims 1 to 5, characterized in that, Also includes: The stator core is located in the internal space and is sleeved on the outside of the rotor assembly. It includes a first end face and a second end face that are arranged opposite to each other. The first end face is arranged towards the top cover of the housing, and the second end face is arranged away from the top cover of the housing. The main bearing base is located in the internal space, on the second end face side of the stator core, extends radially along the housing, and has a third end face facing the second end face; Among them, the distance A between the first end face of the stator core and the inner surface of the top cover of the housing, the distance B between the second end face of the stator core and the third end face of the main bearing base, and the compressor displacement Q satisfy the following condition: A / B / Q≥0.

11.

9. The compressor according to claim 8, characterized in that, The distance A between the first end face of the stator core and the inner surface of the top cover of the housing, the distance B between the second end face of the stator core and the third end face of the main bearing base, and the compressor displacement Q also satisfy the following: A / B / Q≤0.

22.

10. The compressor according to claim 8, characterized in that, The distance A between the first end face of the stator core and the inner surface of the top cover of the housing, the distance B between the second end face of the stator core and the third end face of the main bearing base, and the compressor displacement Q also satisfy the following: A≥40mm, B≥20mm, A / B / Q=0.14.

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