Compressor

Abstract

The utility model 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] The present application relates to the technical field of compressors, and in particular to a compressor. Background Art

[0002] At present, with the upgrade of compressors, miniaturization and high speed have become the development direction of compressors. Increasing the maximum operating frequency of the compressor can achieve a smaller displacement and a higher cooling capacity. However, when the compressor speed is increased, the oil discharge rate will also increase. The increase in the oil discharge rate will lead to a decrease in the refrigerant oil in the compressor, and the lubrication of the friction pair of the pump body cannot be guaranteed, resulting in wear of the friction pair of the pump body. The refrigeration oil is spit out into the air-conditioning system and adheres to the pipeline, which will also reduce the heat exchange efficiency of the pipeline, thereby reducing the cooling capacity of the air conditioner.

[0003] The related technology sets the inner section of the exhaust pipe located in the compressor housing as one or more straight pipe sections and one or more curved pipe sections, and one or more first oil return holes are set on the pipe wall of the curved pipe section. The curved pipe section can reduce the speed of the refrigerant flowing out of the compressor and change the refrigerant flow direction. In addition, the first oil return hole is opened on the pipe wall of the curved pipe section to separate the oil from the refrigerant by centrifugal force, which can improve the oil-gas separation effect.

[0004] In the process of implementing the embodiments of the present disclosure, it is found that there are at least the following problems in the related art:

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

[0006] It should be noted that the information disclosed in the above background technology section is only used to enhance the understanding of the background of the present application, and therefore may include information that does not constitute the prior art known to ordinary technicians in the field. Utility Model Content

[0007] In order to provide a basic understanding of some aspects of the disclosed embodiments, a brief summary is given below. The summary is not an extensive review, nor is it intended to identify key / critical components or delineate the scope of protection of these embodiments, but rather serves as a prelude to the detailed description that follows.

[0008] The disclosed embodiment provides a compressor, which can maintain the flow rate stability of the refrigerant while reducing the oil discharge rate, thereby improving the efficiency of the compressor.

[0009] According to a first aspect of an embodiment of the utility model, a compressor is provided, comprising: a shell, enclosing an internal space, including a shell top cover arranged at an end; a rotor assembly, arranged in the internal space; an exhaust pipe, passing through the shell top cover, including a first opening end arranged outside the shell and a second opening end arranged 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 lengthened.

[0010] Optionally, a ratio between a length H of the exhaust pipe extending into the internal space and a distance C from an inner surface of the housing top cover to the top end 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 end 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 topmost end 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 value C from the inner surface of the shell top cover to the top of the rotor assembly and the compressor displacement value Q satisfy: (E×C) / Q≥0.042.

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

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

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

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

[0019] The compressor provided by the embodiment of the present disclosure can achieve the following technical effects:

[0020] The second open end of the exhaust pipe is arranged in the internal space and extends linearly toward the rotor assembly until the length of the exhaust pipe extending into the internal space reaches a preset value. On the basis of the conventional exhaust pipe, the length of the exhaust pipe extending into the internal space can be linearly lengthened, and the gaseous refrigerant can flow into the exhaust pipe extending linearly and flow out of the exhaust pipe along a linear path. The flow resistance is small, and the refrigerant gas can be ensured to be discharged at a higher pressure. On the basis of reducing the oil discharge rate, the flow rate stability of the refrigerant is maintained, thereby improving the efficiency of the compressor. At the same time, the refrigerant gas flowing out of the linear exhaust pipe can also reduce the collision with the inner wall of the exhaust pipe during the flow process, and reduce the vibration and noise level. At the same time, compared with the design of the curved pipe section of the exhaust pipe in the related art, the exhaust pipe of the embodiment of the present disclosure adopts a linear extension and lengthening setting, which can also reduce production costs.

[0021] The above general description and the following description are exemplary and explanatory only and are not intended to limit the present application. BRIEF DESCRIPTION OF THE DRAWINGS

[0022] One or more embodiments are exemplarily described by corresponding drawings, which do not limit the embodiments. Elements with the same reference numerals in the drawings are shown as similar elements, and the drawings do not constitute a scale limitation, and wherein:

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

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

[0025] Figure 3 is another schematic diagram of the structure of a compressor provided by an embodiment of the present disclosure, wherein arrows indicate the radial direction of the housing;

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

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

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

[0029] Figure 7 is a schematic diagram of the structure of a rotor assembly provided by an embodiment of the present disclosure;

[0030] Figure 8 It is a schematic diagram of another rotor assembly structure provided by an embodiment of the present disclosure.

[0031] Reference numerals:

[0032] 100: compressor housing; 101: conventional exhaust pipe; 102: air inlet; 103: housing top wall;

[0033] 10: Shell; 11: Internal space; 12: Shell top cover;

[0034] 20: rotor assembly; 21: rotor core; 211: groove; 22: oil retaining cap; 23: positioning column;

[0035] 30: exhaust pipe; 31: first opening end; 32: second opening end;

[0036] 40: stator core; 41: first end surface; 42: second end surface;

[0037] 50: main bearing; 51: main bearing base; 511: third end face; 52: main bearing neck. DETAILED DESCRIPTION

[0038] In order to be able to understand the features and technical contents of the embodiments of the present disclosure in more detail, the implementation of the embodiments of the present disclosure is described in detail below in conjunction with the accompanying drawings. The attached drawings are for reference only and are not used to limit the embodiments of the present disclosure. In the following technical description, for the convenience of explanation, a full understanding of the disclosed embodiments is provided through multiple details. However, one or more embodiments can still be implemented without these details. In other cases, to simplify the drawings, well-known structures and devices can be simplified for display.

[0039] The terms "first", "second", etc. in the specification and claims of the disclosed embodiments and the above-mentioned drawings are used to distinguish similar objects, and are not necessarily used to describe a specific order or sequence. It should be understood that the terms used in this way can be interchanged where appropriate for the disclosed embodiments described herein. In addition, the terms "including" and "having" and any variations thereof are intended to cover non-exclusive inclusions.

[0040] In the embodiments of the present disclosure, the terms "upper", "lower", "inside", "middle", "outside", "front", "back" and the like indicate directions or positional relationships based on the directions or positional relationships shown in the accompanying drawings. These terms are mainly intended to better describe the embodiments of the present disclosure and their embodiments, and are not intended to limit the indicated devices, elements or components to have a specific direction, or to be constructed and operated in a specific direction. Moreover, in addition to being used to indicate directions or positional relationships, some of the above terms may also be used to indicate other meanings. For example, the term "upper" may also be used to indicate a certain dependency or connection relationship in certain circumstances. For those of ordinary skill in the art, the specific meanings of these terms in the embodiments of the present disclosure can be understood according to specific circumstances.

[0041] In addition, the terms "disposed", "connected", and "fixed" should be understood in a broad sense. For example, "connected" 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, elements, or components. For those of ordinary skill in the art, the specific meanings of the above terms in the embodiments of the present disclosure can be understood according to specific circumstances.

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

[0043] In the embodiment of the present disclosure, the character " / " indicates that the preceding and following objects are in an "or" relationship. For example, A / B indicates: A or B.

[0044] The term "and / or" is a description of the association relationship 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, in the absence of conflict, the embodiments and features in the embodiments of the present disclosure may be combined with each other.

[0046] Usually the compressor is placed vertically, and the compressor refrigerant oil is at the bottom of the compressor housing 10. Since the compressor needs to lubricate each friction pair in the pump body assembly, the refrigerant oil in the oil pool at the bottom of the compressor is pumped into each friction pair of the pump body under the action of the oil guide plate of the crankshaft and the center oil hole. The refrigerant oil in the friction pair will reach the cylinder compression chamber or above the main bearing through the gap and fully contact with the compressed or discharged refrigerant gas. The refrigerant oil will be brought into the refrigerant gas in the form of tiny oil droplets, reach the upper space of the motor through the flow air gap of the motor assembly, and then be discharged from the exhaust pipe of the compressor.

[0047] like Figure 1As shown, currently, the conventional exhaust pipe 101 generally used in the compressor of the prior art has a shorter length extending into the accommodating space of the compressor housing 100, and the air inlet end of the conventional exhaust pipe 101 is closer to the housing top wall 103. In the compressor using the conventional exhaust pipe 101, the flow direction of the refrigerant gas is as follows: 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 refrigerant oil droplets carried in the refrigerant gas will be discharged from the conventional exhaust pipe 101 along with the refrigerant gas, and the oil discharge rate of the compressor is relatively large.

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

[0049] The shell 10 encloses an internal space 11, including a shell top cover 12 arranged at the end; the rotor assembly 20 is arranged in the internal space 11; the exhaust pipe 30 is passed through the shell top cover 12, including a first open end 31 arranged outside the shell 10 and a second open end 32 arranged in the internal space 11, and the second open end 32 extends linearly 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 is linearly lengthened.

[0050] The compressor provided in the present application is suitable for compressors of the type such as high-speed twin-cylinder rotor compressors.

[0051] The length of the exhaust pipe 30 extending into the internal space 11 will affect the oil-gas separation effect between the refrigerant gas and the refrigeration oil liquid. Figure 3 As shown in H, the distance from the inner surface of the housing top cover 12 to the top 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 the oil retaining cap 22 and the balancing weight, Figure 3-4 As shown, the topmost position of the rotor assembly 20 refers to the position of the rotor assembly 20 that is closest to the housing top cover 12 , and in the embodiment disclosed herein, refers to the topmost position of the oil deflector cap 22 .

[0053] The exhaust pipe 30 is extended in a straight line. When the length of the exhaust pipe 30 extending into the internal space 11 reaches a preset value, the flow direction of the refrigerant gas can be changed to prevent the refrigerant gas with oil flowing out of the air gap of the motor structure from flowing out directly through the exhaust pipe 30, but to flow to the inner surface of the housing top cover 12 and reflux 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 with refrigeration oil droplets swirls multiple times in the internal space 11 between the rotor assembly 20 and the shell top cover 12, and is in full contact with the inner surface of the shell top cover 12 and the inner surface of the side wall of the shell 10, so that the oil carried in the refrigerant gas adheres to the inner surface of the shell 10, and then flows back to the bottom of the compressor along the inner surface of the shell 10, completing the oil and gas separation, and the refrigerant gas is discharged from the exhaust pipe 30, thereby effectively reducing the oil discharge rate.

[0054] The air conditioning compressor needs to compress the low-temperature and low-pressure refrigerant into high-temperature and high-pressure refrigerant. Therefore, the refrigerant gas needs to be at a higher pressure when it is discharged from the compressor.

[0055] Combination Figure 1-3 As shown, with the compressor provided by the embodiment of the present disclosure, the second open end 32 of the exhaust pipe 30 is arranged in the internal space 11 and is linearly extended toward the rotor assembly 20 until the length of the exhaust pipe 30 extending into the internal space 11 reaches a preset value, which can linearly extend the length of the exhaust pipe 30 extending into the internal space 11 on the basis of the conventional exhaust pipe 101, and make the gaseous refrigerant flow into the exhaust pipe 30 extending in a linear manner, and flow out from the exhaust pipe 30 along a straight path, with small flow resistance, which can ensure that the refrigerant gas is discharged at a higher pressure, and maintain the flow rate stability of the refrigerant on the basis of reducing the oil discharge rate, thereby improving the efficiency of the compressor. At the same time, compared with the design of the curved pipe section of the exhaust pipe in the related art, the exhaust pipe 30 of the embodiment of the present disclosure adopts a linear extension and lengthening setting, which can also reduce 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 shown.

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

[0059] Using the compressor provided by the embodiment of the present disclosure, the relationship between the H / C ratio and the oil discharge rate was tested under the conditions that the operating frequency of the compressor was 60 Hz, the distance between the first end face 41 and the inner surface of the housing top cover 12 was 82 mm, and the distance between the second end face 42 and the third end face 511 was 25 mm. The specific test data are shown in the following table.

[0060]

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

[0062] The compressor provided by the embodiment of the present disclosure can significantly reduce the oil discharge rate when H / C ≥ 0.2, avoid the refrigerant oil in the compressor from being discharged from the exhaust pipe 30, reduce the oil content of the refrigerant, and ensure the lubrication requirements of the friction pair. At the same time, the refrigerant gas flowing out of the linear exhaust pipe 30 can also reduce the collision with the inner wall of the exhaust pipe during the flow process, reducing the vibration and noise level.

[0063] It can be understood 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 also satisfies H / C<1. That is, when 0.2≤H / C<1, the oil discharge rate can be significantly reduced.

[0064] It is understood that the H / C ratio can be any value in 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 lengthening of the exhaust pipe 30 extending into the internal space 11 is conducive to the refrigerant gas carrying the refrigeration oil droplets flowing to the inner surface of the shell top cover 12 for reflux. At the same time, a gap needs to be left between the second open end 32 of the exhaust pipe 30 and the top of the rotor assembly 20 for the refrigerant gas to flow in, and to prevent the rotor assembly 20 from directly contacting the exhaust pipe 30 during high-speed rotation, causing 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 shell 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 shell 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, while maintaining an appropriate gap between the exhaust pipe 30 and the top of the rotor assembly 20 for the refrigerant gas to flow, the stability and reliability of the rotor assembly 20 during operation can also be ensured.

[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 length of the exhaust pipe 30 extending into the interior of the housing 10 is greater than or equal to 15 mm, which can optimize the flow path of the refrigerant gas carrying the refrigeration oil droplets in the internal space 11 and improve the oil-liquid separation effect. It can also provide a longer refrigerant gas circulation channel to reduce the resistance of the refrigerant gas during the discharge process, thereby improving the exhaust efficiency of the compressor and helping to ensure that the compressor can still maintain stable performance under high load or high speed. At the same time, the longer exhaust pipe 30 can play a certain buffering role and reduce the generation of airflow pulsation and noise.

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

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

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

[0072] It can be understood that the distance from the inner surface of the housing top cover 12 to the topmost end of the rotor assembly 20 can be 50 mm, 51 mm, 53 mm, 55 mm, 60 mm, 65 mm, and so on.

[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 more effectively reduced and the flow rate stability of the refrigerant can be maintained. The maximum value 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 value C from the inner surface of the shell top cover 12 to the top of the rotor assembly 20 and the compressor displacement value Q satisfy: (E×C) / Q≥0.042.

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

[0076] After the refrigerant gas flows out of the air gap such as the flow hole in the rotor assembly 20, it flows into the internal space 11 between the rotor assembly 20 and the shell top cover 12, and then is discharged through the exhaust pipe 30. The inner diameter cross-sectional area of ​​the exhaust pipe 30 also has a great influence on the pressure loss of the fluid. The increase in the inner diameter cross-sectional area of ​​the exhaust pipe 30 will reduce the flow rate of the gas in the pipeline, reduce the gas pressure, thereby reducing the resistance loss, and also reduce the possibility of oil spitting. 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 a gap for the flow of refrigerant gas, the distance from the inner surface of the shell 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 when extending into the internal space 11. In the embodiment of the present disclosure, the product (E×C) between the minimum cross-sectional area value E of the inner diameter of the exhaust pipe 30 and the distance value C from the inner surface of the shell top cover 12 to the top of the rotor assembly 20 represents the volume inside the exhaust pipe 30, which 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 compression chamber of the compressor pump body. Within a certain range, the increase in the internal volume of the exhaust pipe 30 can reduce the airflow pressure in the exhaust pipe 30, so that the refrigerant gas can flow from the higher pressure space in the compressor pump body into the relatively low pressure space in the exhaust pipe 30, improving the smoothness of fluid flow. When (E×C) / Q≥0.042, the pressure loss of the refrigerant fluid can be reduced, the oil discharge rate can be reduced, and the efficiency of the compressor can be improved and the power consumption can be reduced.

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

[0078] The product of the minimum cross-sectional area value E of the inner diameter of the exhaust pipe 30 and the distance value C from the inner surface of the housing top cover 12 to the top of the rotor assembly 20 also needs to be controlled within a certain range to avoid the exhaust pipe 30 inner diameter being too large to affect the gas flow rate in 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 reduced while ensuring the normal flow of the refrigerant gas.

[0079] It will be appreciated that the ratio of (E×C) / Q may be 0.042, 0.053, 0.065, 0.072, 0.084, and so on.

[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 arranged in the internal space 11 and is 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 arranged opposite to each other. The first end face 41 is arranged toward the shell top cover 12, and the second end face 42 is arranged away from the shell top cover 12; the main bearing base 51 is arranged in the internal space 11, located on the second end face 42 side of the stator core 40, extending along the radial direction of the shell 10, and has a third end face 511 arranged toward the second end face 42; wherein, the distance value A between the first end face 41 and the inner surface of the shell top cover 12, the distance value B between the second end face 42 and the third end face 511, and the compressor displacement value Q satisfy: A / B / Q≥0.11.

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

[0082] The stator core 40 and the rotor assembly 20 belong to the motor assembly of the compressor, and the main bearing 50 belongs to the pump assembly of the compressor. The compressor is usually placed vertically, and the pump assembly, the motor assembly, and the housing top cover 12 are arranged in sequence from bottom to top, and there is space between the three.

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

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

[0085] After being discharged from the pump body assembly, the refrigerant gas first flows into the space with a distance value of B between the second end face 42 and the third end face 511, and then passes through the air gap of the motor assembly and flows into the space with a distance value of A between the first end face 41 on the upper part of the motor assembly and the inner surface of the shell top cover 12. The volume sizes of these two spaces will affect the circulation 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 value A between the first end face 41 and the inner surface of the housing top cover 12 and the distance value 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 smaller the gas pressure. The ratio of A and B can be used to measure the pressure ratio of the gas flow paths in the two spaces, thereby measuring the smoothness of the fluid flow in the space. In order to make the gas flow smoother, A is made greater than B, so that the gas flows from the lower space of the motor assembly into the air gap of the motor assembly, and then flows into the upper space of the motor assembly, which is equivalent to enlarging the gas flow space, enabling the gas to flow from high pressure to low pressure, reducing flow resistance and improving flow smoothness.

[0087] The displacement value Q of the compressor can be used to represent the volume of the compression chamber of the pump assembly, and A / B / Q can be used to measure the volume ratio of the key space through which the entire refrigerant gas flows. Within a certain range, the larger the ratio of A / B / Q, the smaller the fluid resistance loss, the smaller the loss, and the higher the energy efficiency of the compressor.

[0088] When A / B / Q≥0.11, the distance value A between the first end face 41 and the inner surface of the shell top cover 12 is relatively large. The distance between the first end face 41 and the inner surface of the shell top cover 12 increases, which can increase the inner surface area of ​​the shell 10 between the two, so that the refrigerant is in full contact with the inner surface of the shell 10, and more refrigerant oil droplets are attached to the inner surface of the shell 10. While improving the gas flow effect, it can also improve the oil-gas separation effect and reduce the oil discharge rate of the compressor.

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

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

[0091] It will be appreciated that the ratio of A / B / Q may be 0.11, 0.15, 0.18, 0.20, 0.22, and so on.

[0092] Optionally, the distance value A between the first end face 41 and the inner surface of the shell top cover 12, the distance value B between the second end face 42 and the third end face 511, and the compressor displacement value Q also satisfy: 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 more effectively reduced, so that the oil discharge rate of the compressor is minimized.

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

[0095] The disclosed embodiment eliminates the external balancing block, and forms a built-in counterweight balancing part by eccentrically setting a groove 211 on one side of the axial end face of the rotor core 21, which is equivalent to embedding the balancing block in the rotor core 21, so as to avoid the collision of the balancing block with the refrigerant and the refrigeration oil droplets, reduce the stirring effect of the balancing block on the refrigeration oil droplets, and thus reduce the oil discharge rate. At this time, there is no balancing block to interfere with the flow field between the oil deflector cap 22 and the rotor core 21, and the gap is radially symmetrical along the oil deflector cap 22, so that after the oil droplets flow through the flow holes of the rotor core 21, they are evenly and smoothly thrown out to the inner surface of the side wall of the shell 10 under the action of centrifugal force, and then flow into the bottom of the compressor, reducing the oil discharge rate.

[0096] It can be understood that the groove 211 can be provided on one axial end surface of the rotor core 21 , or the groove 211 can be provided on both axial end surfaces of the rotor core 21 .

[0097] Optionally, combined Figure 3-4 and Figure 8 As shown, the rotor assembly 20 further includes an oil deflector cap 22 , which is disposed on the side of the rotor core 21 facing the housing top cover 12 , with a gap between the rotor core 21 and the oil deflector cap 22 , and the gap is radially symmetrical along the oil deflector cap 22 .

[0098] It is mentioned in the above embodiments that 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. On this basis, 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 so that the frozen oil droplets do not rush out directly, but flow out from the side through the gap between the oil baffle cap 22 and the rotor core 21. Under the guidance of the oil baffle cap 22, the frozen oil droplets are refluxed, thereby reducing the loss of oil and improving the oil return effect. The gap between the oil baffle cap 22 and the rotor core 21 is arranged radially symmetrically along the oil baffle cap 22, so that the flow resistance can be reduced when the oil flows out from the side.

[0099] Specifically, the oil deflector cap 22 is provided with a plurality of positioning posts 23 extending toward the rotor core 21, and the plurality of positioning posts 23 are arranged symmetrically along the circumference of the oil deflector cap 22; the rotor core 21 is correspondingly provided with a plurality of positioning holes along the circumference, and the rivets penetrate the positioning posts 23 and match with the positioning holes, so that the oil deflector cap 22 can be fixed to the end face of the rotor core 21. The obstruction of the external balancing block between the oil deflector cap 22 and the rotor core 21 is eliminated, and the plurality of positioning posts 23 are arranged symmetrically along the circumference of the oil deflector cap 22, so that the gap between the oil deflector cap 22 and the end face of the rotor core 21 can be divided into a plurality of symmetrical gaps.

[0100] The linear extended exhaust pipe 30 provided in the present application, when the refrigerant comes out of the air gap of the motor assembly, first flows to the inner surface of the shell top cover 12, and then flows back to the second open end 32 of the exhaust pipe 30, forming a vortex in the internal space 11 between the motor assembly and the shell top cover 12, and most of the refrigerant oil droplets carried in the refrigerant adhere to the inner surface of the shell 10 through full contact with the inner surface of the shell 10, and flow down along the shell 10 into the oil pool at the bottom of the compressor. Another part of the refrigerant oil droplets directly drips on the oil deflector cap 22 during the downward flow from the inner surface of the shell top cover 12, and is again thrown to the inner surface of the shell 10 by the centrifugal force of the high-speed rotation of the oil deflector cap 22, and then flows down along the inner surface of the shell 10 back to the compressor oil pool, thereby effectively achieving gas-liquid separation and reducing the oil discharge rate of the compressor.

[0101] The oil discharge rates of the compressors using the conventional exhaust pipe 101 scheme in the prior art and the compressors using the exhaust pipe 30 lengthening scheme provided in the embodiment of the present disclosure were tested at different operating frequencies. The conventional exhaust pipe 101 scheme and the exhaust pipe 30 lengthening scheme use the same model of compressors and the same batch of installed machines for testing. Under the same other test conditions, the distance from the inner surface of the housing top cover to the top of the rotor assembly is 65 mm, the length of the conventional exhaust pipe 101 extending into the internal space 11 is 5 mm, and the length of the exhaust pipe 30 provided in the embodiment of the present disclosure extending into the internal space 11 is 35 mm.

[0102] The specific test data are shown in the following table.

[0103]

[0104] Comparison of the curve relationship between the oil discharge rate and the compressor operating frequency of the compressor in the prior art and the compressor provided by the embodiment of the present disclosure. Figure 6 As shown. Combined Figure 6 As shown in the data in the above table, at the same frequency, the oil discharge rate of the compressor using the extended exhaust pipe 30 is significantly reduced compared to the oil discharge rate of the compressor using the conventional exhaust pipe 101. As the operating frequency of the compressor increases, the oil discharge rate of the compressor using the conventional exhaust pipe 101 increases significantly, and the oil discharge rate of the compressor using the extended exhaust pipe 30 provided in the embodiment of the present disclosure increases but the increase is small. Moreover, under high-frequency operation, compared with the compressor using the conventional exhaust pipe 101 in the prior art, the oil discharge rate reduction effect of the compressor using the extended exhaust pipe 30 provided in the embodiment of the present disclosure is more obvious.

[0105] The above description and the accompanying drawings sufficiently illustrate the 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. Unless explicitly required, individual components and functions are optional, and the order of operations may vary. Portions and features of some embodiments may be included in or replace portions and features of other embodiments. The 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 the scope thereof. The scope of the present disclosure is limited only by the appended claims.

Claims

1. A compressor, characterized in that: include: A shell body encloses an internal space and includes a shell body top cover disposed at an end; A rotor assembly is disposed in the internal space; The exhaust pipe is passed through the top cover of the shell, and includes a first open end arranged outside the shell and a second open end arranged in the internal space. The second open end extends 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 lengthened.

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 15 mm.

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 value C from the inner surface of the shell top cover to the top of the rotor assembly and the compressor displacement value Q satisfy: (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 value C from the inner surface of the shell top cover to the top of the rotor assembly and the compressor displacement value Q also satisfy: (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 arranged in the internal space, sleeved on the outer side of the rotor assembly, and comprises a first end face and a second end face which are arranged opposite to each other, the first end face is arranged toward the housing top cover, and the second end face is arranged away from the housing top cover; A main bearing base is arranged in the internal space, located at the second end face side of the stator core, extending in the radial direction of the housing, and having a third end face arranged toward the second end face; Among them, the distance value A between the first end face of the stator core and the inner surface of the shell top cover, the distance value B between the second end face of the stator core and the third end face of the main bearing base, and the compressor displacement value Q satisfy: A / B / Q≥0.

11.

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

22.

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

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