Compressor and refrigeration apparatus

Abstract

The utility model provides a kind of compressor and refrigeration equipment, compressor: including static disc, exhaust hole is provided on static disc;Cover, it is installed in the side of static disc, and it is enclosed with static disc and is held cavity, exhaust hole is communicated with holding cavity;Wherein, at least one outlet gas oil filter groove is provided on the surface of static disc close to cover, outlet gas oil filter groove is communicated with the space outside cover of holding cavity.This scheme constructs a two-stage separation system of "holding cavity primary separation+outlet gas oil filter groove secondary separation" by outlet gas oil filter groove, so as to significantly improve the capture efficiency of fine oil droplets of compressor, reduce the oil discharge of compressor, improve the energy efficiency and reliability of entire refrigeration system.

Description

Technical Field

[0001] This utility model relates to the field of household appliance technology, and more specifically, to a compressor and a refrigeration device. Background Technology

[0002] Scroll compressors are widely used due to their high efficiency and low noise. Their working principle is that a moving disc and a stationary disc mesh to form a compression chamber. The refrigerant is compressed from the outside to the center by the translational motion (revolution) of the moving disc, and finally discharged through the exhaust port in the center of the stationary disc. To lubricate the moving and stationary discs, refrigerant oil is present in the compression chamber, resulting in a high-pressure oil-gas mixture being discharged. If excessive refrigerant oil (i.e., high oil discharge) enters the refrigeration system along with the refrigerant, it will adhere to the heat exchanger walls, forming an oil film that severely degrades heat exchange efficiency, leading to decreased system performance, increased energy consumption, and, in the long run, affects the system's operational reliability.

[0003] Although various methods for increasing oil-gas separation efficiency have been proposed in the relevant schemes, these methods often have limited separation efficiency, are not effective at capturing fine oil droplets, and are difficult to stably control the oil output at an ideal level.

[0004] Therefore, how to more effectively reduce the amount of oil discharged from the compressor remains an urgent problem to be solved. Utility Model Content

[0005] The present invention aims to solve at least one of the technical problems existing in the prior art or related technologies.

[0006] Therefore, the first aspect of this utility model provides a compressor.

[0007] The second aspect of this utility model provides a refrigeration device.

[0008] In view of this, the first aspect of the present invention provides a compressor, comprising: a stationary plate having an exhaust port; a cover mounted on one side of the stationary plate, forming a receiving cavity with the stationary plate, the exhaust port communicating with the receiving cavity; wherein, at least one air outlet oil filter groove is provided on the surface of the stationary plate near the cover, the air outlet oil filter groove communicating with the space outside the receiving cavity and the cover.

[0009] The compressor according to an embodiment of this application includes a stationary disc and a housing. The stationary disc cooperates with a moving disc to compress refrigerant gas. The stationary disc has an exhaust port; during operation, the compressed high-pressure oil-gas mixture is discharged from the exhaust port at the center of the stationary disc. At least one exhaust oil filter groove is machined on the end face of the stationary disc facing the housing (the upper surface of the stationary disc). The housing is fixedly installed on one side (generally the top) of the stationary disc, and the two are tightly joined to form a receiving cavity. The outlet of the exhaust port leads directly to the receiving cavity. The receiving cavity is the main space for initial oil-gas separation, and the exhaust oil filter groove is the final exhaust channel of the receiving cavity; that is, the exhaust oil filter groove connects the receiving cavity and the space outside the housing. When the compressor is operating, the high-pressure oil-gas mixture first enters the receiving cavity from the exhaust port of the stationary plate. Within the cavity, initial oil-gas separation occurs due to spatial expansion and airflow impacting the inner wall of the casing. Subsequently, the gas separated in the initial stage gathers and enters the outlet oil filter. As the gas passes through the outlet oil filter, it is accelerated and guided, forming a directional jet. This jet, after exiting the outlet oil filter, impacts a specific external structure located on the outlet path of the outlet oil filter within the compressor, achieving secondary oil-gas separation through this impact. This design, through the outlet oil filter, constructs a two-stage separation system of "initial separation in the receiving cavity + secondary separation in the outlet oil filter," significantly improving the compressor's efficiency in capturing fine oil droplets, reducing the compressor's oil discharge, and enhancing the energy efficiency and reliability of the entire refrigeration system.

[0010] In any of the above technical solutions, optionally, there are multiple air outlet oil filter grooves, which are distributed on the same half of the circumference of the exhaust hole along the circumference of the exhaust hole on the cover.

[0011] In this technical solution, the multiple exhaust oil filter slots are not randomly or symmetrically distributed around the exhaust port, but are all concentrated on the same side of the exhaust port (i.e., the multiple exhaust oil filter slots are located on the same half-circumference of the cover). For example, all the exhaust oil filter slots can be arranged on the left or right side of the exhaust port. This concentrated arrangement ensures that the airflow discharged from each exhaust oil filter slot has approximately the same directionality. These airflows will collectively impact a certain area, which helps the discharged airflow to form a uniform flow field, avoiding the collision and energy cancellation of airflows ejected from different directions. This enhances the oil-gas separation effect and improves the efficiency and stability of oil-gas separation.

[0012] In any of the above technical solutions, optionally, along the radial direction of the stationary disc, the air outlet oil filter groove includes an inner end and an outer end, and along the circumferential direction of the stationary disc, the inner end is offset relative to the outer end.

[0013] In this technical solution, each outlet oil filter groove has an inner end near the center of the stationary disc and an outer end away from the center. The inner and outer ends are not aligned circumferentially with the stationary disc, meaning there is a circumferential offset. This implies that the outlet oil filter groove is not a straight groove along the radial direction, but rather an inclined groove with a specific orientation. When the airflow exits from this inclined outlet oil filter groove, its flow direction is no longer purely radial, but acquires a tangential velocity component. This tangential velocity drives the airflow to continue flowing tangentially after exiting the filter. Thus, by imparting a tangential velocity to the airflow, secondary separation of oil and gas is achieved using centrifugal force, improving the ability to separate fine oil droplets.

[0014] In any of the above technical solutions, optionally, there are multiple air outlet oil filter grooves, and along the circumference of the stationary disc, the outer ends of the multiple air outlet oil filter grooves deviate from the inner ends in the same direction.

[0015] In this technical solution, when multiple inclined air outlet filter grooves are provided on the stationary disc, the inclination direction of all air outlet filter grooves is consistent. For example, looking outward from the center of the stationary disc, the outer ends of all air outlet filter grooves are offset clockwise relative to their inner ends, or they are all offset counterclockwise. This consistency ensures that the airflow discharged from each air outlet filter groove generates the same tangential velocity direction. The superposition of all airflows in the same direction will form a stronger and more uniformly oriented rotating flow field (vortex) in the outlet region of the air outlet filter groove. The uniform vortex field avoids turbulence and energy loss caused by inconsistent directions, thus enhancing the strength and stability of the centrifugal force field and improving the effect and efficiency of centrifugal separation.

[0016] In any of the above technical solutions, optionally, the outer end of the air outlet oil filter groove extends to the edge of the static disc near the surface of the cover.

[0017] In this technical solution, the outlet of the exhaust oil filter groove is located at the outermost circumference of the upper surface of the stationary disc. With this configuration, the exhaust oil filter groove, as the final exhaust channel of the receiving cavity, has its length maximized, ensuring a complete and smooth flow path for the airflow from the inner end to the outer end of the groove. After the gas completes its initial separation within the receiving cavity, it enters the exhaust oil filter groove and flows along its guide. Because the outer end reaches the edge of the stationary disc, the airflow can more directly and concentratedly impact the inner wall of the compressor housing or other specially designed baffle structures upon discharge. This avoids premature diffusion or energy attenuation of the airflow before discharge due to insufficient groove length, thereby enhancing the impact separation force. In contrast, if the outer end of the exhaust oil filter groove terminates at the middle of the stationary disc surface, the airflow may not effectively reach the external impact point, and the secondary separation effect will be significantly reduced.

[0018] In any of the above technical solutions, the compressor may optionally include: a moving disc, disposed on the side of the stationary disc away from the cover, forming a compression chamber with the stationary disc, wherein the rotation direction of the moving disc is consistent with the deviation direction of the outer end of the outlet oil filter groove relative to the inner end.

[0019] In this technical solution, the moving disc is the core moving component of the scroll compressor. It is located on the side of the stationary disc away from the casing; specifically, in a typical vertical compressor, the moving disc is located below the stationary disc. The scroll profiles of the moving disc and the stationary disc mesh with each other, forming a series of crescent-shaped compression chambers. When the motor drives the moving disc, it does not rotate on its own axis, but rather performs an orbital motion around the center of the stationary disc, called "revolution" or "translation." The direction of revolution is fixed, for example, clockwise. In this embodiment, the circumferential deviation direction of the outer end of the outlet oil filter groove relative to the inner end is set to be consistent with the revolution direction of the moving disc. This means that if the moving disc revolves clockwise, then the tilt direction of all outlet oil filter grooves is also designed to guide the airflow to generate a clockwise tangential velocity. This design ensures that the airflow ejected from the outlet oil filter groove for secondary separation moves in a direction that matches the natural rotational tendency of the airflow within the containment chamber, dominated by the revolution of the moving disc. This directional consistency reduces energy loss caused by drastic changes in airflow direction, making gas flow smoother and enabling more effective use of the initial kinetic energy imparted by the revolution of the moving disk. This creates a stronger and more stable swirling field within the containment cavity, thereby improving the effect of the initial separation and providing more ideal airflow conditions for subsequent secondary separation.

[0020] Along the height direction of the compressor, the moving plate is located below the stationary plate, and the cover is located above the stationary plate.

[0021] In any of the above technical solutions, optionally, the exhaust oil filter groove extends in a straight line from the inner end to the outer end, and the extension direction of the exhaust oil filter groove forms an angle with the radial direction of the stationary disc.

[0022] In this technical solution, the exhaust oil filter groove is specifically designed as a straight or near-straight inclined groove, with the centerline of the exhaust oil filter groove forming a fixed angle with the radial line of the stationary disc. This simple straight structure first brings significant advantages in processing technology, allowing the exhaust oil filter groove to be easily formed using conventional processes such as milling, while easily ensuring dimensional accuracy. Simultaneously, compared to curved grooves that may cause continuous changes in flow direction, the straight inclined groove provides a flow path with less resistance and a more stable direction for the airflow, effectively avoiding the generation of additional eddies. Thus, when the gas exits from the straight inclined groove, it can form a concentrated jet with a clearly defined direction and height. Therefore, the straight inclined groove structure achieves the required tangential velocity while balancing ease of processing and smooth flow.

[0023] In any of the above technical solutions, optionally, the included angles of the multiple air outlet oil filter grooves are equal.

[0024] In this technical solution, regardless of whether there are two or more outlet oil filter slots, the acute angle formed by the extension direction of the centerline of multiple outlet oil filter slots and the radial direction of the stationary disc is the same. For example, the included angle of all outlet oil filter slots can be uniformly 15°, instead of some being 10° and others being 20°. This design ensures that the tangential velocity component of the gas ejected from each outlet oil filter slot is uniform. These airflows with the same tangential velocity can form a stable and uniform rotating flow field, avoiding uneven airflow velocity, mutual interference, or even local turbulence caused by angular differences.

[0025] In any of the above technical solutions, optionally, the included angle is greater than or equal to 10° and less than or equal to 20°.

[0026] In this technical solution, if the included angle is too small (e.g., less than 10°), the outlet oil filter groove will be close to the radial groove, resulting in insufficient tangential velocity component and significantly reduced centrifugal separation effect. If the included angle is too large (e.g., greater than 20°), although the tangential velocity component will increase, the effective radial discharge path of the airflow will become longer, potentially leading to increased flow resistance and even affecting the compressor's exhaust efficiency. Setting the included angle in the range of 10° to 20° ensures sufficient centrifugal force for effective oil droplet separation while controlling the exhaust flow resistance within a reasonable range, achieving a balance between separation performance and energy consumption.

[0027] In any of the above technical solutions, optionally, the guiding area of ​​the exhaust port is S1, and the total flow cross-sectional area of ​​at least one exhaust oil filter groove is S2, where S2 is greater than S1.

[0028] In any of the above technical solutions, optionally, the guiding area S1 of the exhaust port reflects the flow capacity of the exhaust channel, and the sum of the cross-sectional areas of all the outlet oil filter grooves is the total flow cross-sectional area S2, representing the total flow capacity of the secondary exhaust channel. After the high-pressure oil-gas mixture is discharged from the compression chamber through the exhaust port into the receiving chamber for initial separation, the gas needs to be discharged. Since S2 is greater than S1, the outlet oil filter groove provides a channel with lower resistance than the exhaust port, which helps to guide more gas through the outlet oil filter groove for discharge, thereby making fuller use of the guiding effect of these grooves for secondary separation. If S2 is less than or equal to S1, the outlet oil filter groove will increase the system resistance and weaken the separation effect. Therefore, S2 being greater than S1 can ensure smooth exhaust while achieving efficient oil-gas separation, maintaining the overall performance and efficiency of the compressor, and avoiding the negative impact of reduced oil output.

[0029] In any of the above technical solutions, optionally, 1.2S1≤S2≤1.5S1.

[0030] In this technical solution, the exhaust oil filter tank ensures that while providing a low-resistance auxiliary exhaust path, the gas flow rate is maintained within an ideal range, thereby optimizing the oil-gas separation process. This balances separation efficiency and flow performance without excessively increasing system complexity, effectively reducing the amount of oil discharged.

[0031] According to a second aspect of the present invention, a refrigeration device is also provided, comprising: a compressor as described in any of the above embodiments.

[0032] The refrigeration equipment provided in the second aspect of this utility model, since it includes the compressor proposed in any of the above embodiments, has all the beneficial effects of the compressor.

[0033] Refrigeration equipment can include air conditioners, refrigerators, etc. One of the core components of refrigeration equipment is the compressor. Using a compressor with a lower oil discharge rate means that the amount of refrigerant oil entering the heat exchanger with the refrigerant circulation will be significantly reduced. The oil film formed by refrigerant oil adhering to the inner wall of the heat exchanger tubes severely hinders heat exchange. With a reduced oil discharge rate, the heat exchanger can maintain higher heat exchange efficiency. This improves the overall energy efficiency ratio of the refrigeration equipment, making it more energy-efficient, while also reducing the risk of malfunctions due to oil circuit problems, thus helping to extend the service life and reliability of the refrigeration equipment.

[0034] Additional aspects and advantages of this invention will become apparent in the description that follows, or may be learned by practice of this invention. Attached Figure Description

[0035] The above and / or additional aspects and advantages of this utility model will become apparent and readily understood from the description of the embodiments taken in conjunction with the following drawings, in which:

[0036] Figure 1 A schematic diagram of the compressor in one embodiment of the present invention is shown;

[0037] Figure 2 A schematic diagram of the static plate and cover of the compressor in one embodiment of the present invention is shown;

[0038] Figure 3 One of the structural schematic diagrams of the stationary disc of the compressor in one embodiment of the present invention is shown;

[0039] Figure 4 A schematic diagram of the compressor housing in one embodiment of the present invention is shown;

[0040] Figure 5 This is a second schematic diagram of the static plate of the compressor in one embodiment of the present invention;

[0041] Figure 6A schematic diagram of the stationary disc of a compressor according to another embodiment of the present invention is shown.

[0042] in, Figures 1 to 6 The correspondence between the reference numerals and component names in the attached drawings is as follows:

[0043] 1. Static plate, 12. Exhaust port, 14. Air outlet oil filter groove, 142. Inner end, 144. Outer end, 2. Cover, 3. Receiving cavity, 4. Moving plate, 5. Compression cavity. Detailed Implementation

[0044] To better understand the above-mentioned objectives, features, and advantages of this utility model, the present utility model will be further described in detail below with reference to the accompanying drawings and specific embodiments. It should be noted that, unless otherwise specified, the embodiments and features described in these embodiments can be combined with each other.

[0045] Many specific details are set forth in the following description in order to provide a full understanding of the present invention. However, the present invention may also be implemented in other ways different from those described herein. Therefore, the scope of protection of the present invention is not limited to the specific embodiments disclosed below.

[0046] The compressor and refrigeration equipment in this embodiment will be further described below with reference to the accompanying drawings.

[0047] like Figure 1 , Figure 2 , Figure 3 and Figure 4As shown, the first aspect of this utility model discloses a compressor, including a stationary disc 1 and a housing 2. The stationary disc 1 is used to cooperate with a moving disc 4 to compress refrigerant gas. An exhaust port 12 is provided on the stationary disc 1; during operation, the compressed high-pressure oil-gas mixture is discharged from the exhaust port 12 at the center of the stationary disc 1. At least one exhaust oil filter groove 14 is machined on the end face of the stationary disc 1 facing the housing 2 (the upper surface of the stationary disc 1). The housing 2 is fixedly installed on one side (generally the top) of the stationary disc 1, and the two are tightly joined to form a receiving cavity 3. The outlet of the exhaust port 12 directly leads to the receiving cavity 3. The receiving cavity 3 is the main space for initial oil-gas separation, and the exhaust oil filter groove 14 is the final exhaust channel of the receiving cavity 3, which connects the receiving cavity 3 and the space outside the housing 2 to separate the high-pressure oil-gas mixture in the receiving cavity 3 and discharge it to the outside of the housing 2. When the compressor is working, the high-pressure oil-gas mixture first enters the receiving cavity 3 from the exhaust port 12 of the stationary plate 1. Within the receiving cavity 3, initial oil-gas separation occurs due to spatial expansion and airflow impacting the inner wall of the casing 2. Subsequently, the gas separated by the initial separation gathers and enters the outlet oil filter 14. As the gas passes through the outlet oil filter 14, it is accelerated and guided, forming a directional jet. This jet, after exiting the outlet oil filter 14, impacts a specific external structure located on the outlet path of the outlet oil filter 14 within the compressor, achieving secondary oil-gas separation through this impact. This design, through the outlet oil filter 14, constructs a two-stage separation system of "initial separation in the receiving cavity 3 + secondary separation in the outlet oil filter 14," significantly improving the compressor's efficiency in capturing fine oil droplets, reducing the compressor's oil discharge, and enhancing the energy efficiency and reliability of the entire refrigeration system.

[0048] For example, the compressor is a scroll compressor.

[0049] In any of the above embodiments, optionally, as Figure 2 and Figure 3 As shown, the multiple exhaust oil filter grooves 14 are not randomly or symmetrically distributed around the exhaust port 12, but are all concentrated on the same side of the exhaust port 12 (i.e., the multiple exhaust oil filter grooves 14 are located on the same half-circumference area of ​​the cover). For example, all the exhaust oil filter grooves 14 can be arranged on the left or right side of the exhaust port 12. This concentrated arrangement makes the airflow discharged from each exhaust oil filter groove 14 have approximately the same directionality. These airflows will jointly impact a certain area, which is conducive to the exhaust airflow forming a uniform flow field, avoiding the collision and energy cancellation of airflows when they are ejected from different directions. This enhances the oil-gas separation effect and improves the efficiency and stability of oil-gas separation.

[0050] In any of the above embodiments, optionally, as Figure 2 and Figure 3As shown, each outlet oil filter groove 14 has an inner end 142 near the center of the stationary disk 1 and an outer end 144 away from the center. The inner end 142 and the outer end 144 are not aligned circumferentially on the stationary disk 1; that is, there is a circumferential offset. This means that the outlet oil filter groove 14 is not a straight groove along the radial direction, but an inclined groove with a specific orientation. When the airflow exits from this inclined outlet oil filter groove 14, its flow direction is no longer purely radial, but acquires a tangential velocity component. This tangential velocity drives the airflow to continue flowing tangentially after exiting. Thus, by imparting a tangential velocity to the airflow, secondary separation of oil and gas is achieved using centrifugal force, improving the separation capability for fine oil droplets.

[0051] In any of the above embodiments, optionally, as Figure 2 and Figure 3 As shown, when multiple inclined air outlet filter grooves 14 are provided on the stationary disk 1, the inclination direction of all air outlet filter grooves 14 is consistent. For example, looking outward from the center of the stationary disk 1, the outer ends 144 of all air outlet filter grooves 14 are offset clockwise relative to their inner ends 142, or they are all offset counterclockwise. This consistency ensures that the airflow discharged from each air outlet filter groove 14 generates the same tangential velocity direction. The superposition of all airflows in the same direction will form a stronger and more uniformly oriented rotating flow field (vortex) in the outlet region of the air outlet filter groove 14. The uniform vortex field avoids turbulence and energy loss caused by inconsistent directions, thus enhancing the strength and stability of the centrifugal force field and improving the effect and efficiency of centrifugal separation.

[0052] In any of the above embodiments, optionally, as Figure 2 and Figure 3 As shown, the outer end 144 of the air outlet oil filter groove 14 extends to the edge of the surface of the stationary disc 1 near the cover 2.

[0053] In this embodiment, the outlet of the exhaust oil filter groove 14 is located at the outermost circumference of the upper surface of the stationary plate 1. With this configuration, the exhaust oil filter groove 14, serving as the final exhaust channel of the receiving cavity 3, has its length maximized, ensuring a complete and smooth flow path for the airflow from the inner end 142 to the outer end 144. After the gas completes its initial separation within the receiving cavity 3, it enters the exhaust oil filter groove 14 and flows along its guide. Because the outer end 144 reaches the edge of the stationary plate 1, the airflow can more directly and concentratedly impact the inner wall of the compressor housing or other specially designed baffle structures upon discharge. This avoids premature diffusion or energy attenuation of the airflow before discharge due to insufficient groove length, thereby enhancing the impact separation force. In contrast, if the outer end 144 of the exhaust oil filter groove 14 terminates at the middle of the surface of the stationary plate 1, the airflow may not effectively reach the external impact point, and the secondary separation effect will be significantly reduced.

[0054] In any of the above embodiments, optionally, as Figure 1 and Figure 2 As shown, the compressor also includes a moving plate 4, which is located on the side of the stationary plate 1 away from the cover 2, and together with the stationary plate 1, forms a compression chamber 5. The rotation direction of the moving plate 4 is consistent with the deviation direction of the outer end 144 of the outlet oil filter groove 14 relative to the inner end 142.

[0055] In this embodiment, the moving disk 4 is the core moving component of the scroll compressor. It is located on the side of the stationary disk 1 away from the housing 2. Specifically, in a typical vertical compressor, the moving disk 4 is located below the stationary disk 1. The scroll profiles of the moving disk 4 and the stationary disk 1 mesh with each other, forming a series of crescent-shaped compression chambers 5. When the motor drives the moving disk 4, the moving disk 4 does not rotate on its own axis, but rather performs an orbital motion around the center of the stationary disk 1, called "revolution" or "translation." The direction of revolution is fixed, for example, clockwise. In this embodiment, the circumferential deviation direction of the outer end 144 of the outlet oil filter groove 14 relative to the inner end 142 is set to be consistent with the revolution direction of the moving disk 4. This means that if the moving disk 4 revolves clockwise, then the tilt direction of all outlet oil filter grooves 14 is also designed to guide the airflow to generate a clockwise tangential velocity. This design ensures that the airflow ejected from the outlet oil filter trough 14 for secondary separation moves in a direction that aligns with the natural rotational trend of the airflow within the receiving cavity 3, dominated by the revolution of the moving disk 4. This directional consistency reduces energy loss caused by drastic changes in airflow direction, resulting in smoother gas flow. It also allows for more effective utilization of the initial kinetic energy imparted by the revolution of the moving disk 4, creating a stronger and more stable swirling field within the receiving cavity 3. This enhances the effectiveness of the initial separation and provides more ideal airflow conditions for subsequent secondary separation.

[0056] Along the height direction of the compressor, the moving plate 4 is located below the stationary plate 1, and the cover 2 is located above the stationary plate 1.

[0057] In any of the above embodiments, optionally, as Figure 2 , Figure 3 and Figure 5 As shown, the exhaust oil filter groove 14 is specifically designed as a straight or near-straight inclined groove, with the extension direction of the centerline of the exhaust oil filter groove 14 forming a fixed angle with the radial line of the stationary plate 1. This simple straight structure first brings significant advantages in processing technology, allowing the exhaust oil filter groove 14 to be easily formed by conventional processes such as milling, and easily ensuring dimensional accuracy. At the same time, compared with curved grooves that may cause continuous changes in flow direction, the straight inclined groove provides the airflow with a flow path with less resistance and more stable direction, effectively avoiding the generation of additional eddies. Thus, when the gas is discharged from the straight inclined groove, it can form a concentrated jet with a clear direction and height. Therefore, the straight inclined groove structure achieves the required tangential velocity while taking into account both processing convenience and smooth flow.

[0058] In any of the above embodiments, optionally, as Figure 2 , Figure 3 and Figure 5 As shown, regardless of whether there are two or more exhaust oil filter slots 14, the acute angle formed by the extension direction of the centerline of the multiple exhaust oil filter slots 14 and the radial direction of the stationary disk 1 is the same. For example, the included angle of all exhaust oil filter slots 14 can be uniformly 15°, instead of some being 10° and others being 20°. This design ensures that the tangential velocity component of the gas ejected from each exhaust oil filter slot 14 is uniform. These airflows with the same tangential velocity can form a stable and uniform rotating flow field, avoiding uneven airflow velocity, mutual interference, or even local turbulence caused by angular differences.

[0059] In any of the above embodiments, optionally, as Figure 2 , Figure 3 and Figure 5 As shown, the included angle is greater than or equal to 10° and less than or equal to 20°.

[0060] In this embodiment, if the included angle is too small (e.g., less than 10°), the outlet oil filter groove 14 will be close to the radial groove, resulting in insufficient tangential velocity component and significantly reduced centrifugal separation effect. If the included angle is too large (e.g., greater than 20°), although the tangential velocity component will increase, the effective radial discharge path of the airflow will become longer, which may lead to increased flow resistance and even affect the compressor's exhaust efficiency. Setting the included angle in the range of 10° to 20° ensures sufficient centrifugal force for effective oil droplet separation while controlling the exhaust flow resistance within a reasonable range, achieving a balance between separation performance and energy consumption.

[0061] In any of the above embodiments, optionally, the flow guiding area of ​​the exhaust port 12 is S1, and the total flow cross-sectional area of ​​at least one exhaust oil filter groove 14 is S2, where S2 is greater than S1.

[0062] In any of the above embodiments, optionally, the guiding area S1 of the exhaust port 12 reflects the flow capacity of the exhaust channel, and the sum of the cross-sectional areas of all the outlet oil filter grooves 14 is the total flow cross-sectional area S2, representing the total flow capacity of the secondary exhaust channel. After the high-pressure oil-gas mixture is discharged from the compression chamber 5 into the receiving chamber 3 through the exhaust port 12 for initial separation, the gas needs to be discharged. Since S2 is greater than S1, the outlet oil filter groove 14 provides a channel with lower resistance than the exhaust port 12, which helps to guide more gas through the outlet oil filter groove 14 for discharge, thereby making fuller use of the guiding effect of these grooves for secondary separation. If S2 is less than or equal to S1, the outlet oil filter groove 14 will increase the system resistance and weaken the separation effect. Therefore, S2 being greater than S1 can ensure smooth exhaust while achieving efficient oil-gas separation, maintaining the overall performance and efficiency of the compressor, and avoiding the negative impact of reduced oil discharge.

[0063] In any of the above embodiments, optionally, 1.2S1≤S2≤1.5S1.

[0064] In this embodiment, the exhaust oil filter tank 14 ensures that while providing a low-resistance auxiliary exhaust path, the gas flow rate is maintained within an ideal range, thereby optimizing the oil-gas separation process. This balances separation efficiency and flow performance without excessively increasing system complexity, effectively reducing the amount of oil discharged.

[0065] According to a second aspect of the present invention, a refrigeration device (not shown in the figure) is also provided, comprising: a compressor as described in any of the above embodiments.

[0066] The refrigeration equipment provided in the second aspect of this utility model, since it includes the compressor proposed in any of the above embodiments, has all the beneficial effects of the compressor.

[0067] Refrigeration equipment can include air conditioners, refrigerators, etc. One of the core components of refrigeration equipment is the compressor. Using a compressor with a lower oil discharge rate means that the amount of refrigerant oil entering the heat exchanger with the refrigerant circulation will be significantly reduced. The oil film formed by refrigerant oil adhering to the inner wall of the heat exchanger tubes severely hinders heat exchange. With a reduced oil discharge rate, the heat exchanger can maintain higher heat exchange efficiency. This improves the overall energy efficiency ratio of the refrigeration equipment, making it more energy-efficient, while also reducing the risk of malfunctions due to oil circuit problems, thus helping to extend the service life and reliability of the refrigeration equipment.

[0068] The following reference Figures 1 to 6 This describes a compressor proposed according to some embodiments of the present invention.

[0069] In a scroll compressor, the refrigerant is compressed by the moving plate 4 and the stationary plate 1, and then discharged through the exhaust port of the stationary plate 1. To lubricate the moving and stationary plates 1 and reduce wear, the compression chamber 5 is filled with refrigerant oil, resulting in the pump exhaust being an oil-gas mixture. If too much refrigerant oil enters the system with the refrigerant, it will affect the system's performance and lifespan. Therefore, it is of great importance to effectively retain the refrigerant oil inside the compressor to provide lubrication and to reduce the amount of oil discharged.

[0070] Based on this, this embodiment provides a compressor, which includes a stationary disc 1 and a housing 2.

[0071] In one specific embodiment, the structure of the static disk 1 is as follows: Figure 6 As shown.

[0072] In one specific embodiment, such as Figure 2 and Figure 3 As shown, the upper surface of the stationary disc 1 is provided with an exhaust oil filter structure. Exemplarily, the exhaust oil filter structure includes two exhaust oil filter grooves 14 located on the same side of the stationary disc 1. Viewed from above, both exhaust oil filter grooves 14 extend in a clockwise direction and form an angle Q with the radial direction. Figure 1 , Figure 2 and Figure 4 As shown, a cover 2 is installed on the upper surface of the stationary plate 1, and the cover 2 is in close contact with the surface of the stationary plate 1.

[0073] When the oil-gas mixture is discharged through the oil filter tank 14, it is blown toward the inner wall of the hood 2 and impacted within the space enclosed by the hood 2 and the stationary plate 1, thereby achieving oil-gas separation and reducing the amount of oil discharged.

[0074] For example, such as Figure 5 As shown, the angle Q between the air outlet oil filter groove 14 and the radial direction satisfies: 10°≤Q≤20°.

[0075] For example, the original exhaust port area on the stationary plate 1 is S1, the cross-sectional areas of the two exhaust oil filter grooves 14 are S21 and S22 respectively, and the total cross-sectional area of ​​the exhaust oil filter structure is S2=S21+S22, and satisfies 1.2S1≤S2≤1.5S1.

[0076] This embodiment, by setting an exhaust oil filter structure with a specific angle and area relationship, combined with the cover 2 to form an impact separation space, can effectively achieve oil-gas separation, reduce the amount of oil discharged by the compressor, and thus improve the reliability and life of the system.

[0077] In this utility model, the term "multiple" refers to two or more unless otherwise explicitly defined. The terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, "connection" can be a fixed connection, a detachable connection, or an integral connection; "linking" can be a direct connection or an indirect connection through an intermediate medium. Those skilled in the art can understand the specific meaning of the above terms in this utility model according to the specific circumstances.

[0078] In the description of this specification, the terms "one embodiment," "some embodiments," "specific embodiment," etc., refer to a specific feature, structure, material, or characteristic described in connection with that embodiment or example, which is included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0079] The above description is merely a preferred embodiment of this utility model and is not intended to limit the utility model. Various modifications and variations can be made to this utility model by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this utility model should be included within the protection scope of this utility model.

Claims

1. A compressor, characterized in that, include: A static plate, wherein the static plate is provided with an exhaust hole; The cover is installed on one side of the stationary plate, forming a receiving cavity with the stationary plate, and the exhaust hole communicates with the receiving cavity; The static plate has at least one air outlet oil filter groove on its surface near the cover, and the air outlet oil filter groove connects the receiving cavity and the space outside the cover.

2. The compressor according to claim 1, characterized in that, The number of the exhaust oil filter grooves is multiple, and the multiple exhaust oil filter grooves are distributed on the same half of the circumference of the exhaust hole along the circumference of the exhaust hole on the cover.

3. The compressor according to claim 1, characterized in that, Along the radial direction of the stationary disc, the outlet oil filter groove includes an inner end and an outer end, and along the circumference of the stationary disc, the inner end is offset relative to the outer end.

4. The compressor according to claim 3, characterized in that, The number of the air outlet oil filter grooves is multiple, and along the circumference of the stationary disc, the outer ends of the multiple air outlet oil filter grooves deviate from the inner ends in the same direction.

5. The compressor according to claim 2, characterized in that, The outer end of the air outlet oil filter groove extends to the edge of the static plate near the surface of the cover.

6. The compressor according to claim 3, characterized in that, The air outlet oil filter groove extends in a straight line from the inner end to the outer end, and the extension direction of the air outlet oil filter groove forms an angle with the radial direction of the stationary disc.

7. The compressor according to claim 6, characterized in that, The included angles of the plurality of said air outlet oil filter grooves are equal; and / or The included angle is greater than or equal to 10° and less than or equal to 20°.

8. The compressor according to any one of claims 1 to 7, characterized in that, The flow guiding area of ​​the exhaust port is S1, and the total flow cross-sectional area of ​​at least one of the exhaust oil filter grooves is S2, where S2 is greater than S1.

9. The compressor according to claim 8, characterized in that, 1.2S1≤S2≤1.5S1.

10. A refrigeration device, characterized in that, include: The compressor as described in any one of claims 1 to 9.

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