Compressor and refrigeration equipment

Abstract

The invention discloses a compressor and refrigeration equipment, and relates to the technical field of compressors, the compressor comprises: a motor comprising a rotor and a stator; the pump body assembly comprises a crankshaft, a compression part and a silencer, and the silencer is located on the side, close to the rotor, of the compression part; the silencer comprises a bottom cover and a silencing cover, and the silencing cover is provided with an exhaust hole; the exhaust holes comprise a first exhaust hole, the first exhaust hole is provided with an exhaust plane intersecting with the circumferential direction of the silencing cover, the normal of the exhaust plane and the exhaust plane intersect at a point A, the projection circle center formed by the silencer on the axial projection plane of the silencer is a point O, an included angle alpha is formed between a straight line OA and the normal of the exhaust plane, and the included angle alpha is larger than 0 degree and smaller than 180 degrees; the radius of the outer circle of the silencing cover is R0, the maximum size of the first exhaust hole in the radial direction of the silencer is d0, and the outer diameter of a rotor iron core of the rotor is R1; the following is satisfied. According to the technical scheme, efficient noise reduction and performance optimization can be achieved on the premise that the height of the whole machine is guaranteed.

Description

Technical Field

[0001] This invention relates to the field of compressor technology, and in particular to a compressor and refrigeration equipment. Background Technology

[0002] Currently, constant speed mufflers mainly adopt a top exhaust strategy. Although this solution can meet basic exhaust requirements, it conflicts with the modern compressor's low-profile integrated design concept. Specifically, the concentrated airflow formed when the high-pressure refrigerant is exhausted through the top will directly impact the rotor, causing axial oscillation of the shaft system and dynamic load fluctuations, which in turn leads to deterioration of shaft noise and affects the compressor's performance. Summary of the Invention

[0003] The main objective of this invention is to propose a compressor and refrigeration equipment that can achieve efficient noise reduction and performance optimization while maintaining a low overall height.

[0004] To achieve the above objectives, the compressor proposed in this invention comprises: An electric motor, comprising a rotor and a stator disposed around the rotor; and The pump body assembly includes a crankshaft connected to the rotor, a compression component and a muffler sleeved around the crankshaft, the muffler being located on the side of the compression component closer to the rotor; the muffler includes a bottom cover that abuts against the compression component, and a muffler cover located on the side of the bottom cover closer to the rotor, the muffler cover having an exhaust port; The exhaust port includes a first exhaust port, which has an exhaust plane that intersects the circumferential direction of the muffler. The normal of the exhaust plane intersects the exhaust plane at point A. The center of the projection of the muffler on its axial projection plane is point O. The line connecting point O and point A is a straight line OA. The straight line OA forms an angle α with the normal of the exhaust plane. The angle α is greater than 0 degrees and less than 180 degrees. The outer radius of the muffler is R0, the maximum radial dimension of the first exhaust port in the muffler is d0, and the outer diameter of the rotor core is R1; satisfying: .

[0005] In one embodiment, the stator includes a stator core and a coil winding wound around the stator core. The coil winding has a first winding end and a second winding end located at the stator core. The second winding end is located at the end of the stator core closer to the muffler, and the outer radius of the second winding end is R3; satisfying: .

[0006] In one embodiment, the inner radius of the end of the second winding is R4; satisfying: .

[0007] In one embodiment, the muffler has a plurality of protrusions spaced apart circumferentially, wherein at least one of the protrusions is provided with the first exhaust port.

[0008] In one embodiment, at least two of the protrusions are provided with the first exhaust hole, and the exhaust direction of each first exhaust hole is tangent to the circumferential direction of the muffler.

[0009] In one embodiment, at least two of the first vent holes on the convex bulges are opened toward the same side in the circumferential direction of the muffler.

[0010] In one embodiment, at least one of the protrusions has a first protrusion and a second protrusion disposed adjacent to each other, wherein the height of the first protrusion is greater than the height of the second protrusion in the axial direction of the crankshaft, and the first vent is disposed on the side of the first protrusion facing the second protrusion and located on the top of the second protrusion.

[0011] In one embodiment, the vent further includes a second vent, and at least one of the second bosses of the bulge is provided with the second vent.

[0012] In one embodiment, the compression component includes a first bearing, a cylinder, and a second bearing arranged sequentially along the axial direction of the crankshaft. The muffler is located on the side of the first bearing away from the cylinder. The first bearing has a vent hole with an opening area of ​​S0, and the total opening area of ​​the exhaust holes is S; satisfying: The ratio of S to S0 is not less than 0.5 and not greater than 2.5.

[0013] The present invention also proposes a refrigeration device, including the compressor described above.

[0014] The technical solution of this invention, through dual optimization of both structure and airflow path, effectively improves the direct impact force of high-pressure refrigerant airflow on the rotor, reduces the axial pulsation excitation borne by the rotor shaft system, and also avoids oil leakage deterioration. On one hand, a first exhaust port is opened on the muffler's shroud, and the exhaust plane of the first exhaust port intersects the circumferential direction of the shroud. The angle between the normal of the exhaust plane of the first exhaust port and the line connecting the center of the muffler (i.e., the straight line OA) is 0° < α < 180°. This allows the normal of the exhaust plane of the first exhaust port (i.e., the exhaust direction of the first exhaust port) to be tangent or substantially tangent to the circumferential direction of the shroud. This allows the airflow discharged from the first exhaust port to be discharged along a tangential direction tangent or substantially tangent to the circumferential direction of the shroud, achieving tangential side exhaust of the shroud. Thus, without increasing the overall height of the unit, it avoids the high-pressure refrigerant from being directly discharged from the top of the shroud and directly impacting the rotor, reducing the axial impact force on the rotor. On the other hand, by limiting... Further constraining the safe distance between the exhaust outlet of the first exhaust port and the outer diameter of the rotor ensures a suitable radial distance between the exhaust outlet of the first exhaust port and the compressor rotor. This effectively reduces the direct impact force of the high-pressure refrigerant on the rotor, decreases the axial pulsation excitation on the rotor shaft system, resulting in a smaller rotor vibration amplitude and ensuring the compressor's oil discharge rate is close to the acceptable level, preventing further deterioration of oil discharge performance. Thus, efficient noise reduction and performance optimization can be achieved while maintaining a low overall height. Attached Figure Description

[0015] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on the structures shown in these drawings without creative effort.

[0016] Figure 1 This is a cross-sectional structural schematic diagram of an embodiment of the compressor provided by the present invention; Figure 2 for Figure 1 A schematic diagram of the assembly structure of the motor and pump body components of the medium compressor; Figure 3 for Figure 2 A schematic diagram of the cross-sectional structure of the middle stator; Figure 4 for Figure 2 A schematic diagram of the rotor core of the intermediate rotor; Figure 5 A schematic diagram of a compressor muffler according to one embodiment; Figure 6 for Figure 5 Side view of the muffler in the middle; Figure 7 for Figure 5 Top view of the muffler in the middle; Figure 8 A schematic diagram of another embodiment of the compressor's muffler; Figure 9 A schematic diagram of a structure of an embodiment of the first bearing of the compressor; Figure 10 for The relationship between the rotor's axial vibration amplitude and the compressor's oil discharge rate is shown in the graph.

[0017] Explanation of icon numbers: 100. Compressor; 10. Housing; 11. Main housing; 12. First end housing; 13. Second end housing; 20. Motor; 21. Rotor; 211. Rotor core; 22. Stator; 221. Stator core; 222. Wire winding; 2221. First winding end; 2222. Second winding end; 30. Pump body assembly; 31. Crankshaft; 32. Compression component; 321. First bearing; 3211. Vent hole; 322. Cylinder; 323. Second bearing; 33. Silencer; 331. Bottom cover; 332. Silencer cover; 3321. First exhaust port; 3322. Protrusion; 33221. First boss; 33222. Second boss; 3323. Second exhaust port.

[0018] The realization of the objective, functional features and advantages of the present invention will be further explained in conjunction with the embodiments and with reference to the accompanying drawings. Detailed Implementation

[0019] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of the present invention.

[0020] It should be noted that if the embodiments of the present invention involve directional indicators (such as up, down, left, right, front, back, etc.), the directional indicators are only used to explain the relative positional relationship and movement of the components in a specific posture. If the specific posture changes, the directional indicators will also change accordingly.

[0021] Furthermore, if the embodiments of this invention involve descriptions such as "first" or "second," these descriptions are for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined with "first" or "second" may explicitly or implicitly include at least one of those features. Additionally, the use of "and / or" or "and / or" throughout the text includes three parallel solutions. For example, "A and / or B" includes solution A, solution B, or a solution where both A and B are satisfied simultaneously. Furthermore, the technical solutions of the various embodiments can be combined with each other, but this must be based on the ability of those skilled in the art to implement them. When the combination of technical solutions is contradictory or impossible to implement, it should be considered that such a combination of technical solutions does not exist and is not within the scope of protection claimed by this invention.

[0022] Currently, constant speed mufflers mainly adopt a top exhaust strategy. Although this solution can meet basic exhaust requirements, it conflicts with the modern compressor's low-profile integrated design concept. Specifically, the concentrated airflow formed when the high-pressure refrigerant is exhausted through the top will directly impact the rotor, causing axial oscillation of the shaft system and dynamic load fluctuations, which in turn leads to deterioration of shaft noise and affects the compressor's performance.

[0023] Based on this, the present invention proposes a compressor 100.

[0024] Please see Figure 1 , Figures 4 to 7 In one embodiment of the present invention, the compressor 100 includes a motor 20 and a pump assembly 30. The motor 20 includes a rotor 21 and a stator 22 disposed around the rotor 21. The pump assembly 30 includes a crankshaft 31 connected to the rotor 21, and a compression component 32 and a muffler 33 sleeved around the crankshaft 31. The muffler 33 is located on the side of the compression component 32 near the rotor 21. The muffler 33 includes a bottom cover 331 that abuts against the compression component 32, and a muffler shroud 332 disposed on the side of the bottom cover 331 near the rotor 21. The muffler shroud 332 has an exhaust port. The exhaust port includes a first... The exhaust port 3321 has an exhaust plane that intersects the circumferential direction of the muffler 332. The normal of the exhaust plane intersects the exhaust plane at point A. The center of the projection of the muffler 33 onto its axial projection plane is point O. The line connecting point O and point A is a straight line OA. The straight line OA forms an angle α with the normal of the exhaust plane. The angle α is greater than 0 degrees and less than 180 degrees. The outer radius of the muffler 332 is R0. The maximum radial dimension of the first exhaust port 3321 in the muffler 33 is d0. The outer diameter of the rotor core 211 of the rotor 21 is R1. The following conditions are met: .

[0025] The compressor 100 can be a vertical compressor or a horizontal compressor. The compressor 100 includes a housing 10 and a motor 20 and a pump assembly 30 housed within the housing 10. A liquid receiver communicating with the suction pipe of the compressor 100 may also be provided outside the housing 10. The housing 10 serves to support and protect the internal components, and together with the internal components, defines a passage for the flow of high-pressure refrigerant. The housing 10 includes a main housing 11 with open ends, and a first end shell 12 and a second end shell 13 located at the two open ends of the main housing 11. The first end shell 12 and the second end shell 13 can be welded and fixed to the main housing 11 to ensure that the entire housing 10 can withstand high pressure. The first end shell 12 is used to connect to the exhaust pipe. The motor 20 and the pump body assembly 30 are located inside the housing 10. The motor 20 is used to drive the pump body assembly 30 to move, compress the refrigerant through the pump body assembly 30, and discharge the compressed high-pressure refrigerant into the housing 10. Finally, it is discharged from the exhaust pipe of the first end shell 12 into the external refrigerant circulation system.

[0026] like Figures 1 to 3As shown, a vertical rotary compressor 100 is used as an example. The housing 10 is generally a vertically extending cylinder, with a first end shell 12 and a second end shell 13 fixed to the axial ends of the main housing 11, respectively. The first end shell 12 is the upper end shell of the housing 10, and the second end shell 13 is the lower end shell of the housing 10. The first end shell 12 is used to connect the exhaust pipe of the compressor 100. The motor 20 includes a rotor 21 and a stator 22. The stator 22 is fixed inside the main housing 11 and sleeved around the rotor 21. The rotor 21 is sleeved around the crankshaft 31 of the pump body assembly 30. The rotor 21 includes a rotor core 211 and a magnet disposed on the rotor core 211. The stator 22 includes a stator core 221 and a coil winding 222 wound around the stator core 221. The coil winding 222 is used to connect to the power supply circuit. When the motor 20 is working, it generates an induced magnetic field under the synergistic effect of the stator 22 and the rotor 21, causing the rotor 21 to rotate relative to the stator 22, thereby driving the crankshaft 31 to rotate. The coil winding 222 includes a first winding end 2221 and a second winding end 2222 located at both ends of the stator core 221. The first winding end 2221 (i.e., the positive side of the coil winding end) is located at the upper end of the stator core 221, and the second winding end 2222 (i.e., the negative side of the coil winding end) is located at the lower end of the stator core 221. The first winding end 2221 is located close to the first end shell 12 and forms a certain gap with the top wall of the first end shell 12. The pump body assembly 30 includes a crankshaft 31 connected to the rotor 21, and a compression component 32 and a muffler 33 sleeved around the crankshaft 31. The compression component 32 has an intake passage for refrigerant to enter and an exhaust passage for high-pressure refrigerant to exit. The muffler 33 has a muffler chamber communicating with the exhaust passage and an exhaust port communicating with the muffler chamber. The refrigerant in the external circulation system enters the compression component 32 through the intake passage, and the compression component 32 compresses the refrigerant to perform work. The resulting high-pressure refrigerant is discharged from the exhaust passage into the muffler chamber, where it is silenced and reduced in noise before being discharged from the exhaust port.

[0027] like Figure 5 As shown, the muffler 33 includes a bottom cover 331 and a muffler hood 332. The bottom cover 331 includes a first side and a second side facing each other. The muffler hood 332 is disposed on the first side of the bottom cover 331. The second side of the bottom cover 331 abuts against the first bearing 321 of the compression member 32, thereby connecting the muffler hood 332 to the compression member 32. The muffler hood 332 protrudes from the bottom cover 331 toward the side away from the compression member 32 to form a boss structure. The side of the muffler hood 332 away from the bottom cover 331 has an opening for the shaft sleeve of the first bearing 321 to pass through. Optionally, the bottom cover 331 and the muffler hood 332 are integrally formed.

[0028] The muffler 332 is provided with exhaust ports. The exhaust ports include a first exhaust port 3321, which can be circular, elliptical, square, crescent-shaped, or other irregularly shaped. The number of first exhaust ports 3321 can be designed as one, two, or more, depending on actual needs. The first exhaust port 3321 has an exhaust plane that intersects the muffler 332 circumferentially. The normal to the exhaust plane intersects the exhaust plane at point A. The center of the projection of the muffler 33 onto its axial projection plane is point O. The line connecting point O and point A is a straight line OA. The straight line OA forms an angle α with the normal to the exhaust plane, where α is greater than 0 degrees and less than 180 degrees. The exhaust plane of the first exhaust port 3321 refers to the plane where the outlet of the first exhaust port 3321 is located. The exhaust plane of the first exhaust port 3321 intersects the circumferential direction of the muffler 332, and the angle between the normal of the exhaust plane of the first exhaust port 3321 and the line connecting the center of the muffler 33 (i.e., the straight line OA) is 0° < α < 180°. In this way, the normal of the exhaust plane of the first exhaust port 3321 (i.e. the exhaust direction of the first exhaust port 3321) can be tangent or substantially tangent to the circumferential direction of the muffler 332, so that the airflow discharged from the first exhaust port 3321 can be discharged along the tangential direction that is tangent or substantially tangent to the circumferential direction of the muffler 332, thereby realizing the tangential side exhaust of the muffler 332. Compared to the traditional solution of directly opening an exhaust port on the top of the muffler for axial exhaust, this solution uses the first exhaust port 3321 of the muffler 332 for tangential exhaust. In this way, without increasing the overall height of the machine, by changing the exhaust direction, the high-pressure refrigerant discharged from the first exhaust port 3321 is controlled to be discharged along the tangential direction of the muffler 332, forming a vortex along the outer wall of the muffler 332, and then flowing to the area where the rotor 21 is located, instead of being discharged directly along the axial direction of the muffler 332 and blowing directly onto the end face of the rotor 21. This reduces the axial impact force on the rotor 21.

[0029] like Figure 6 and Figure 7 As shown, the outer radius R0 of the muffler 332 refers to the maximum outer radius of the projection formed by the muffler 332 on the axial projection plane perpendicular to the crankshaft 31. For example, the muffler 332 typically includes multiple circumferentially spaced protrusions 3322, presenting an overall petal shape. The outer edge projection lines of the multiple protrusions 3322 lie on the same circumference, and the radius of this circumference is the outer radius R0 of the muffler 332. The maximum radial dimension of the first exhaust port 3321 in the muffler 33 is d0, and the outer diameter of the rotor core 211 of the rotor 21 is R1; satisfying: .

[0030] in, The exhaust outlet of the first exhaust port 3321 is limited to a safe radial distance from the rotor 21 of the compressor 100.

[0031] For example, The value can be 0.9, 1.0, 1.1, 1.2, or any other value in the range [0.9, 1.2].

[0032] Combination Figure 10 It can be seen that when When the value is less than 0.9, it indicates that the radial distance between the exhaust outlet of the first exhaust port 3321 and the rotor 21 is less than the safe distance. Within this range, the high-pressure refrigerant discharged from the first exhaust port 3321 will have a large axial impact on the rotor 21, resulting in a large axial vibration amplitude of the rotor 21. When the value is greater than 1.2, it indicates that the radial distance between the exhaust outlet of the first exhaust port 3321 and the rotor 21 is greater than the safe distance. Within this range, although the axial vibration amplitude of the rotor 21 is small, it will lead to a significant increase in the oil discharge rate of the compressor 100, resulting in a deterioration of the oil discharge of the compressor 100. When the value is in the range of [0.9, 1.2], the distance between the exhaust outlet of the first exhaust port 3321 and the radial distance between the compressor 100 rotor 21 is within a safe distance range. This can effectively improve the direct impact force of the high-pressure refrigerant on the rotor 21, reduce the axial pulsation excitation borne by the rotor 21 shaft system, make the vibration amplitude of the rotor 21 smaller, and make the oil discharge rate of the compressor 100 close to the qualified oil discharge rate line, so as not to cause the oil discharge to deteriorate.

[0033] The technical solution of the present invention can effectively improve the direct impact force of high-pressure refrigerant airflow on rotor 21 by optimizing both the structure and the airflow path, reduce the axial pulsation excitation of rotor 21 shaft system, and also avoid oil discharge deterioration. On the one hand, a first exhaust port 3321 is opened on the muffler cover 332 of the muffler 33, and the exhaust plane of the first exhaust port 3321 intersects the circumferential direction of the muffler cover 332. The angle between the normal of the exhaust plane of the first exhaust port 3321 and the line connecting the center of the muffler 33 (i.e., the straight line OA) is 0° < α < 180°. This allows the normal of the exhaust plane of the first exhaust port 3321 (i.e., the exhaust direction of the first exhaust port 3321) to be tangent or substantially tangent to the circumferential direction of the muffler cover 332. This allows the airflow discharged from the first exhaust port 3321 to be discharged along the tangential direction that is tangent or substantially tangent to the circumferential direction of the muffler cover 332, achieving tangential side exhaust of the muffler cover 332. In this way, without increasing the overall height of the unit, it is possible to prevent the high-pressure refrigerant from being directly discharged from the top of the muffler cover 332 and directly impacting the rotor 21, thereby reducing the axial impact force on the rotor 21. On the other hand, by limiting... Further constraining the safe distance between the exhaust outlet of the first exhaust port 3321 and the outer diameter of the rotor 21 ensures that the radial safe distance between the exhaust outlet of the first exhaust port 3321 and the rotor 21 of the compressor 100 is moderate. This effectively reduces the direct impact force of the high-pressure refrigerant on the rotor 21, reduces the axial pulsation excitation borne by the rotor 21 shaft system, resulting in a smaller vibration amplitude of the rotor 21, and keeps the oil discharge rate of the compressor 100 close to the qualified oil discharge rate line, preventing oil discharge deterioration. In this way, efficient noise reduction and performance optimization can be achieved while maintaining a low overall height.

[0034] like Figure 1 and Figure 2 As shown, when the high-pressure refrigerant in the muffler 33 is discharged through the first exhaust port 3321, it first passes through the second winding end 2222 of the coil winding 222, then through the gap between the rotor core 211 and the stator core 221, flows to the first winding end 2221 of the coil winding 222, and finally is discharged from the exhaust pipe of the first end shell 12 of the compressor 100 to the external refrigerant circulation system. Therefore, the safe distance between the inner and outer radial dimensions of the second winding end 2222 and the first exhaust port 3321 will affect the exhaust flow path of the first exhaust port 3321, which in turn will affect the impact of the high-pressure refrigerant on the rotor 21 and the compressor 100 housing 10, and will also affect the oil discharge rate and performance of the compressor 100.

[0035] To further reduce the noise of compressor 100 and improve the oil discharge and performance of compressor 100. For example... Figure 2 and Figure 3 As shown, in one embodiment, the stator 22 includes a stator core 221 and a coil winding 222 wound around the stator core 221. The coil winding 222 has a first winding end 2221 and a second winding end 2222 located at the stator core 221. The second winding end 2222 is located at the end of the stator core 221 near the muffler 33, and the outer radius of the second winding end 2222 is R3; satisfying: .

[0036] The outer radius R3 of the second winding end refers to the maximum outer radius of the projection formed by the second winding end on the projection plane perpendicular to the rotor 21 axis.

[0037] A radial safety distance is defined between the exhaust outlet of the first exhaust port 3321 and the outer circle of the second winding end 2222. For example, The value can be 0.6, 0.7, 0.8, 0.9, 1.0, 1.1, 1.2, or any other value in the range [0.6, 1.2].

[0038] like If the value is less than 0.6, it indicates that the radial distance between the exhaust outlet of the first exhaust port 3321 and the outer circle of the second winding end 2222 is less than the safe distance. Within this range, most of the high-pressure refrigerant discharged from the first exhaust port 3321 flows to the side of the second winding end 2222 closer to the rotor 21, which will generate a large impact force on the rotor 21, causing axial vibration and noise in the rotor 21. If the value is greater than 1.2, it indicates that the radial distance between the exhaust outlet of the first exhaust port 3321 and the outer circle of the second winding end 2222 is greater than the safe distance. Within this range, most of the high-pressure refrigerant discharged from the first exhaust port 3321 flows to the side of the second winding end closer to the housing 10, which may cause secondary noise problems caused by the high-pressure refrigerant directly hitting the housing 10. Furthermore, the high-pressure refrigerant directly impacts the oil surface on the outer edge of the housing 10, which will cause the high-pressure refrigerant to carry more lubricating oil out of the compressor 100, resulting in an increased oil discharge rate of the compressor 100, and deterioration of the compressor 100's oil discharge and performance.

[0039] In this embodiment, by limiting The radial safety distance between the exhaust outlet of the first exhaust port 3321 and the outer circle of the second winding end 2222 is further constrained. This ensures that the high-pressure refrigerant discharged from the first exhaust port 3321 can avoid the area where the rotor 21 and the housing 10 are located as much as possible, ensuring that most of the high-pressure refrigerant can pass through the area where the second winding end 2222 is located. In this way, the direct impact force of the high-pressure refrigerant on the rotor 21 can be effectively reduced, the axial pulsation excitation borne by the rotor 21 shaft system can be reduced, the axial vibration and noise of the rotor 21 can be reduced, and the smoothness of the rotor 21 rotation can be ensured; it can also prevent the high-pressure refrigerant from directly hitting the housing 10 and generating secondary noise. Furthermore, by controlling most of the high-pressure refrigerant to blow towards the area of ​​the coil winding 222, the high-pressure exhaust refrigerant can be prevented from directly impacting the oil surface on the outer edge of the housing 10. Moreover, the coil winding 222 can also filter the lubricating oil in the high-pressure refrigerant, preventing the high-pressure refrigerant from carrying too much lubricating oil out of the compressor 100, thereby reducing the oil discharge of the compressor 100 and improving the oil discharge and performance of the compressor 100. In addition, the high-pressure refrigerant passing through the coil winding 222 area also helps to dissipate heat from the coil winding 222, thereby improving the heat dissipation efficiency of the motor 20 and increasing energy efficiency.

[0040] Furthermore, the inner radius R4 of the second winding end 2222 satisfies: .

[0041] Wherein, the inner circle radius R4 of the second winding end 2222 refers to the minimum inner circle radius of the projection formed by the second winding end 2222 on the projection plane perpendicular to the axial direction of the rotor 21.

[0042] A radial safety distance is defined between the exhaust outlet of the first exhaust port 3321 and the inner circle of the second winding end 2222. For example, The value can be 1.0, 1.1, 1.2, 1.3, 1.4, 1.5, or any other value within the range [1.0, 1.5].

[0043] like If the value is less than 1, it indicates that the radial distance between the exhaust outlet of the first exhaust port 3321 and the inner circle of the second winding end 2222 is less than the safety distance. In this case, the high-pressure refrigerant discharged from the exhaust outlet of the first exhaust port 3321 is closer to the rotor 21 area, which will generate a large impact force on the rotor 21, causing axial vibration and noise of the rotor 21. If the value is greater than 1.5, more refrigerant will flow to the side of the second winding end 2222 closer to the housing 10, which will cause secondary noise problems caused by the high-pressure refrigerant rushing directly to the housing 10.

[0044] In this embodiment, by limiting The radial safety distance between the exhaust outlet of the first exhaust port 3321 and the inner circle of the second winding end 2222 is further constrained, ensuring that the high-pressure refrigerant discharged from the first exhaust port 3321 can avoid the area where the rotor 21 and the housing 10 are located as much as possible, and that most of the high-pressure refrigerant can pass through the area where the second winding end 2222 is located. This effectively reduces the direct impact force of the high-pressure refrigerant on the rotor 21, reduces the axial pulsation excitation borne by the rotor 21 shaft system, reduces the axial vibration and noise of the rotor 21, and ensures the smooth rotation of the rotor 21; it also prevents the high-pressure refrigerant from directly impacting the housing 10 and generating secondary noise. Furthermore, by controlling most of the high-pressure refrigerant to be blown towards the area of ​​the coil winding 222, the high-pressure exhaust refrigerant can be prevented from directly impacting the oil surface on the outer edge of the housing 10. Moreover, the coil winding 222 can also filter the lubricating oil in the high-pressure refrigerant, preventing the high-pressure refrigerant from carrying excessive lubricating oil out of the compressor 100, thus reducing the oil discharge of the compressor 100 and improving the oil discharge and performance of the compressor 100. In addition, the high-pressure refrigerant passing through the coil winding 222 area also helps to dissipate heat from the coil winding 222, thereby improving the heat dissipation efficiency of the motor 20 and increasing energy efficiency.

[0045] The above embodiment addresses the technical pain points of compressor 100 through dual optimization of both structure and airflow path: Specifically, the airflow direction of muffler 33 is optimized to a tangential direction, further constraining the safe distance between the exhaust direction of muffler 33 and the outer diameter of rotor 21, thereby effectively reducing the direct impact force of high-pressure refrigerant airflow on rotor 21 and reducing the axial pulsation excitation borne by rotor 21 shaft system. To further improve the oil discharge and performance of compressor 100, the safe distance between the exhaust direction of muffler 33 and the inner and outer diameters of the stator 22 reverse side coil is also constrained. This design scheme can achieve efficient noise reduction and performance optimization while ensuring cost. Through the above design, the noise of the compressor in the 500~3150Hz frequency band can be effectively improved, and the overall noise OA value can be improved by more than 3dB; the tangential exhaust of the silencer 33 can improve the impact force of the direct-blowing rotor 21, and the overall axial vibration is significantly improved; the refrigerant discharged by the silencer 33 is filtered by the coil winding 222 of the motor 20, which can improve the problem of refrigerant direct-blowing oil leakage; due to the change in the flow direction of the discharged refrigerant, the heat dissipation efficiency of the motor 20 is improved, and the energy efficiency is improved; compared with the conventional radial side exhaust, the silencer 33 can improve the secondary noise problem caused by the direct impact on the main housing 11, and reduce the secondary disturbance flow noise of the high-pressure exhaust refrigerant by the rotor 21 of the motor 20.

[0046] like Figure 5 As shown, in one embodiment, the muffler 332 has a plurality of protrusions 3322 spaced apart along the circumference, wherein at least one protrusion 3322 is provided with a first exhaust port 3321.

[0047] In this embodiment, the muffler 332 has a plurality of protrusions 3322 arranged circumferentially, such that the projection of the muffler 332 onto a plane perpendicular to its axial direction resembles a petal shape. For example, the number of protrusions 3322 can be two, three, four, five, or more. Exemplarily, the muffler 332 has five protrusions 3322 arranged circumferentially, with a recessed area formed between adjacent protrusions 3322. At least one protrusion 3322 is provided with a first vent 3321. For example, the first vent 3321 can be provided on only one of the protrusions 3322, and the number of first vents 3321 on that protrusion 3322 can be one, two, or more. Alternatively, the first vent 3321 can be provided on each of the plurality of protrusions 3322, and the number of first vents 3321 on each protrusion 3322 can also be one, two, or more. The number of first vents 3321 on each protrusion 3322 can be the same or different. The shapes of the various first exhaust ports 3321 can be the same or different. The orientations of the various first exhaust ports 3321 can be the same or different. No specific restrictions are imposed here.

[0048] like Figure 5 and Figure 7As shown, in one embodiment, at least two protrusions 3322 are provided with first exhaust holes 3321, and the exhaust direction of each first exhaust hole 3321 is tangent to the circumferential direction of the muffler 332.

[0049] In this embodiment, by providing first exhaust holes 3321 on at least two protrusions 3322, the total opening area of ​​the exhaust holes can be increased, improving exhaust efficiency. Furthermore, the first exhaust holes 3321 are distributed across at least two protrusions 3322, making the discharge path of the high-pressure refrigerant more dispersed, ensuring that the high-pressure refrigerant is discharged along different paths. This changes the impact direction of the airflow, effectively improving the direct impact force of the high-pressure refrigerant airflow on the rotor 21, reducing the axial pulsation excitation borne by the rotor 21 shaft system, and improving the operational stability and reliability of the compressor 100. The exhaust direction of each first exhaust hole 3321 is tangential to the circumferential direction of the muffler 332, enabling each first exhaust hole 3321 to exhaust in the tangential direction of the muffler 332, thereby further reducing the axial impact force on the rotor 21, reducing the axial pulsation excitation borne by the rotor 21 shaft system, and reducing vibration noise.

[0050] It is worth noting that the exhaust direction of each first exhaust port 3321 is tangent to the circumference of the muffler 332. This can be because the opening directions of multiple first exhaust ports 3321 are oriented towards the same side along a preset rotation direction in the circumference of the muffler 332. Alternatively, some first exhaust ports 3321 can be oriented towards a preset rotation direction (e.g., counterclockwise), while others can be oriented towards a direction opposite to the preset rotation direction (e.g., clockwise).

[0051] like Figure 5 As shown, optionally, in one embodiment, the first exhaust holes 3321 on at least two protrusions 3322 are opened towards the same side in the circumferential direction of the muffler 332. By restricting the opening direction of the first exhaust holes 3321 on the multiple protrusions 3322 to the same preset rotation direction, a consistent exhaust path can be formed, which helps to reduce the deflection and turbulence of the airflow during the exhaust process, reduce sound wave interference, and improve the noise reduction effect.

[0052] For example, the muffler 332 includes a plurality of protrusions 3322 arranged circumferentially, wherein two non-adjacent protrusions 3322 are respectively provided with a first exhaust hole 3321, and the two first exhaust holes 3321 are opened towards the same side in the same preset rotation direction.

[0053] like Figure 5As shown, in one embodiment, at least one protrusion 3322 has a first protrusion 33221 and a second protrusion 33222 disposed adjacently. In the axial direction of the crankshaft 31, the height of the first protrusion 33221 is greater than the height of the second protrusion 33222. The first exhaust port 3321 is disposed on the side of the first protrusion 33221 facing the second protrusion 33222 and is located on the top of the second protrusion 33222.

[0054] In this embodiment, the muffler 332 has a plurality of protrusions 3322 arranged circumferentially, such that the projection of the muffler 332 on a plane perpendicular to its axis resembles a petal shape. At least one of the protrusions 3322 has a first protrusion 33221 and a second protrusion 33222 that are adjacent to each other and have different protrusion heights, such that there is a height difference between the first protrusion 33221 and the second protrusion 33222. The height of the first boss 33221 is greater than the height of the second boss 33222. In other words, the axial distance between the top surface of the first boss 33221 and the bottom cover 331 is greater than the axial distance between the top surface of the second boss 33222 and the bottom cover 331. This creates a stepped structure between the first boss 33221 and the second boss 33222. The first exhaust port 3321 is located at the junction of the first boss 33221 and the second boss 33222, with its opening facing the top of the second boss 33222. The airflow exiting from the first exhaust port 3321 flows towards the top of the second boss 33222, and is guided by the top of the second boss 33222 to exit along the tangential direction of the silencer 332. Thus, by utilizing the spatial arrangement of the bosses, the airflow can be guided tangentially, reducing the axial impact on the rotor 21 and lowering vibration noise.

[0055] like Figure 8 As shown, in one embodiment, the vent further includes a second vent 3323, and at least one second boss 33222 of the convex 3322 is provided with the second vent 3323.

[0056] The second vent 3323 can be circular, elliptical, square, crescent-shaped, or other irregularly shaped. The number of second vents 3323 can be one, two, or more, depending on actual needs. The number of first vents 3321 and second vents 3323 can be the same or different, and their opening directions can be the same or different. The first vent 3321 and second vent 3323 can be located on the same convex hull 3322 or on different convex hulls 3322.

[0057] In this embodiment, by providing a second exhaust port 3323 on the side wall of the lower of the first and second bosses 33221, the airflow is directed to the top and side wall of the lower boss by the first and second exhaust ports 3321 and 3323 respectively, ensuring that the airflow is discharged along different paths, reducing sound wave concentration, and changing the impact direction of the airflow. This effectively improves the direct impact force of the high-pressure refrigerant airflow on the rotor 21, reduces the axial pulsation excitation borne by the rotor 21 shaft system, and improves the operating stability and reliability of the compressor 100.

[0058] Optionally, the first exhaust port 3321 and the second exhaust port 3323 are disposed on the same protrusion 3322. For example, the first exhaust port 3321 is disposed on the side of the first protrusion 33221 near the second protrusion 33222 on the same protrusion 33222, and the second exhaust port 3323 is disposed on the side of the second protrusion 33222 away from the first protrusion 33221. In this way, the first exhaust port 3321 is located at the top of the second protrusion 33222, and the second exhaust port 3323 is located on the side of the second protrusion 33222, so that the airflow flows to the top and sidewall of the lower protrusion respectively. Furthermore, disposing of different exhaust ports (i.e., the first exhaust port 3321 and the second exhaust port 3323) on the same protrusion 3322 simplifies the structural layout, facilitates manufacturing and assembly, reduces structural complexity, improves production efficiency, reduces costs, and ensures the rationality and effectiveness of the exhaust path.

[0059] like Figure 2 and Figure 9 As shown, in one embodiment, the compression component 32 includes a first bearing 321, a cylinder 322, and a second bearing 323 arranged sequentially along the axial direction of the crankshaft 31. The muffler 33 is located on the side of the first bearing 321 away from the cylinder 322. The first bearing 321 has a vent hole 3211 with an opening area of ​​S0 and a total opening area of ​​S for the exhaust holes. The ratio of S to S0 is not less than 0.5 and not greater than 2.5.

[0060] In this embodiment, the compression component 32 is specifically the core component for compressing gas in the rotary compressor 100. Taking a single-cylinder rotary compressor 100 as an example, the compression component 32 includes a first bearing 321, a cylinder 322, a second bearing 323, a piston, and a sliding vane. The cylinder 322 has a working chamber and a sliding vane groove communicating with the working chamber. The piston is eccentrically rotatably disposed in the working chamber of the cylinder 322, and the sliding vane is slidably disposed in the sliding vane groove along the radial direction of the cylinder 322. One end of the sliding vane abuts against or is hinged to the piston. The crankshaft 31 has an eccentric portion, and the piston is sleeved around the eccentric portion of the crankshaft 31. By rotating the crankshaft 31, the piston can be driven to rotate eccentrically against the inner surface of the cylinder 322 to compress the gas in the working chamber and form a high-pressure refrigerant. The first bearing 321 and the second bearing 323 are respectively disposed on opposite sides of the cylinder 322 to seal both ends of the cylinder 322 and also to support the crankshaft 31. In this design, the first bearing 321 is located on the side of the cylinder 322 closer to the motor 20, and the second bearing 323 is located on the side of the cylinder 322 away from the motor 20. Taking a vertical compressor 100 as an example, the first bearing 321 is the upper bearing (i.e., the main bearing), and the second bearing 323 is the lower bearing (i.e., the auxiliary bearing). In order to discharge the high-pressure refrigerant in the compression component 32, the first bearing 321 is also provided with a vent 3211 for connecting the working chamber and the silencer chamber. The high-pressure refrigerant enters the silencer chamber through the vent 3211 of the first bearing 321, and then is discharged into the cavity of the housing 10 through the exhaust port. After passing through the gap between the housing 10 and the motor 20, and the internal gap of the motor 20, it is discharged into the external refrigerant circulation system through the exhaust pipe on the first end shell 12. Of course, in other embodiments, the compressor 100 can also be a multi-cylinder rotary compressor 100. Accordingly, at least two cylinders 322 are provided, and a partition is provided between two adjacent cylinders 322.

[0061] The total open area of ​​the exhaust port is S. For example, when there is only one exhaust port (e.g., only one first exhaust port 3321), the open area of ​​that single exhaust port (e.g., the open area of ​​a single first exhaust port 3321) is the total open area of ​​the exhaust port. When there are multiple exhaust ports (e.g., first exhaust port 3321 and second exhaust port 3323), the sum of the open areas of the multiple exhaust ports (e.g., the sum of the open areas of first exhaust port 3321 and second exhaust port 3323) is the total open area of ​​the exhaust port. The ratio S / S0 represents the relative size between the total open area of ​​the exhaust port and the open area of ​​the bearing vent 3211. If the S / S0 ratio is too small, less than 0.5, the total open area of ​​the exhaust port is too small, resulting in insufficient exhaust area, increased back pressure, and increased power consumption of compressor 100. If the S / S0 ratio is too large, greater than 2.5, the total opening area of ​​the exhaust port will be too large, leading to a decrease in flow velocity. Low flow velocity results in a thicker boundary layer, greater turbulence intensity, and increased pressure loss. By limiting the ratio of the total opening area of ​​the exhaust port to the opening area of ​​the vent 3211 to between 0.5 and 2.5 (i.e., 0.5 ≤ S / S0 ≤ 2.5), the balance between airflow distribution and system back pressure can be ensured. For example, the ratio of S to S0 can be 0.5, 0.6, 0.7, 0.8, 0.9, 1.0, 1.1, 1.2, 1.3, 1.4, 1.5, 1.6, 1.7, 1.8, 1.9, 2.0, 2.1, 2.2, 2.3, 2.4, 2.5, or any other value within the range [0.5, 2.5].

[0062] This invention also proposes a refrigeration device, which includes a compressor 100. The specific structure of the compressor 100 is as described in the above embodiments. Since this refrigeration device adopts all the technical solutions of all the above embodiments, it has at least all the beneficial effects brought about by the technical solutions of the above embodiments, which will not be described in detail here. The refrigeration device includes, but is not limited to, refrigerators, integrated air conditioners, split air conditioners, ducted air conditioners, window air conditioners, etc.

[0063] The above description is merely an exemplary embodiment of the present invention and does not limit the scope of protection of the present invention. Any equivalent structural transformations made based on the technical concept of the present invention and the contents of the specification and drawings of the present invention, or direct / indirect applications in other related technical fields, are included within the scope of protection of the present invention.

Claims

1. A compressor (100), characterized in that, include: The motor (20) includes a rotor (21) and a stator (22) disposed around the rotor (21); The pump body assembly (30) includes a crankshaft (31) connected to the rotor (21), a compression component (32) and a muffler (33) sleeved around the crankshaft (31), the muffler (33) being located on the side of the compression component (32) closer to the rotor (21); the muffler (33) includes a bottom cover (331) that abuts against the compression component (32), and a muffler cover (332) provided on the side of the bottom cover (331) closer to the rotor (21), the muffler cover (332) having an exhaust port; The exhaust port includes a first exhaust port (3321), which has an exhaust plane that intersects the circumferential direction of the muffler (332). The normal of the exhaust plane intersects the exhaust plane at point A. The center of the projection of the muffler (33) on its axial projection plane is point O. The line connecting point O and point A is a straight line OA. The straight line OA forms an angle α with the normal of the exhaust plane. The angle α is greater than 0 degrees and less than 180 degrees. The outer radius of the muffler (332) is R0, the maximum radial dimension of the first exhaust port (3321) in the muffler (33) is d0, and the outer diameter of the rotor core (211) of the rotor (21) is R1; satisfying: 。 2. The compressor (100) as described in claim 1, characterized in that, The stator (22) includes a stator core (221) and a coil winding (222) wound around the stator core (221). The coil winding (222) has a first winding end (2221) and a second winding end (2222) located on the stator core (221). The second winding end (2222) is located at the end of the stator core (221) near the muffler (33), and the outer radius of the second winding end (2222) is R3; satisfying: 。 3. The compressor (100) as described in claim 2, characterized in that, The inner radius of the end (2222) of the second winding is R4; satisfying: 。 4. The compressor (100) as claimed in claim 1, characterized in that, The muffler (332) has a plurality of protrusions (3322) spaced apart in the circumferential direction, wherein at least one of the protrusions (3322) is provided with the first exhaust port (3321).

5. The compressor (100) as described in claim 4, characterized in that, At least two of the protrusions (3322) are provided with the first exhaust hole (3321), and the exhaust direction of each first exhaust hole (3321) is tangent to the circumferential direction of the muffler (332).

6. The compressor (100) as described in claim 5, characterized in that, At least two of the first exhaust holes (3321) on the convex bulges (3322) are opened in the circumferential direction of the muffler (332) and face the same side.

7. The compressor (100) as claimed in claim 4, characterized in that, At least one of the convex bulges (3322) has a first convex bulge (33221) and a second convex bulge (33222) arranged adjacent to each other. In the axial direction of the crankshaft (31), the height of the first convex bulge (33221) is greater than the height of the second convex bulge (33222). The first exhaust hole (3321) is located on the side of the first convex bulge (33221) facing the second convex bulge (33222) and is located on the top of the second convex bulge (33222).

8. The compressor (100) as claimed in claim 7, characterized in that, The vent also includes a second vent (3323), and at least one of the second bosses (33222) of the bulge (3322) is provided with the second vent (3323).

9. The compressor (100) as claimed in any one of claims 1 to 8, characterized in that, The compression component (32) includes a first bearing (321), a cylinder (322), and a second bearing (323) arranged sequentially along the axial direction of the crankshaft (31). The muffler (33) is located on the side of the first bearing (321) away from the cylinder (322). The first bearing (321) has a vent hole (3211) with an opening area of ​​S0 and a total opening area of ​​S for the exhaust holes. satisfy: The ratio of S to S0 is not less than 0.5 and not greater than 2.

5.

10. A refrigeration device, characterized in that, Includes the compressor (100) as described in any one of claims 1 to 9.

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