Compressor and refrigeration equipment

Abstract

The invention discloses a compressor and refrigeration equipment, and relates to the technical field of compressors, and the compressor comprises a shell which comprises a main shell and a first end shell; the motor comprises a rotor and a stator, the stator comprises a stator iron core and a coil winding, and the coil winding is provided with a first winding end part and a second winding end part which are arranged at the two ends of the stator iron core; the pump body assembly comprises a crankshaft connected with the rotor, a compression component arranged on the crankshaft in a sleeving mode and a silencer, the silencer is located on the side, facing the rotor, of the compression component, and the silencer is provided with an exhaust hole; the total opening area of the exhaust holes is S1, the total area of the trimming gap between the stator and the shell is S2, the radius of the outer circle of the rotor is r1, and the radius of the inner circle of the end part of the second winding is R4; the ratio of S1 to S2 is not less than 0.05 and less than 0.12; the ratio of S1 to S1 is not less than 2 and not more than 3. According to the scheme, high-efficiency noise reduction and performance optimization can be realized on the premise of ensuring the short height of the whole machine.

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] In recent years, driven by the demand in the portable terminal market, the design of compressors towards shorter height and smaller size has become a major trend. However, the miniaturization of compressors has led to a reduction in the internal cavity volume of the compressor. When the high-pressure refrigerant is discharged from the top, the concentrated airflow formed will directly impact the rotor, causing axial oscillation of the shaft system and dynamic load fluctuations, which in turn leads to the deterioration of shaft noise and affects the performance of the compressor. 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: The housing includes a main housing and a first end housing disposed at one end of the main housing; An electric motor, disposed within the housing, includes a rotor and a stator disposed around the rotor. The stator includes a stator core and a coil winding. The coil winding has a first winding end and a second winding end located at opposite ends of the stator core, the first winding end being located at the end of the stator core facing the first end housing. A pump body assembly is disposed within the housing. 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 facing the rotor, and the muffler having an exhaust port. The total opening area of ​​the exhaust port is S1, the total area of ​​the tangential gap formed between the stator and the housing is S2, the outer radius of the rotor is r1, the inner radius of the end of the second winding is R4, and the product of the square difference between R4 and r1 and π is... ;satisfy: The ratio of S1 to S2 is not less than 0.05 and less than 0.12; The S1 and The ratio is not less than 2 and not greater than 3.

[0005] In one embodiment, the outer radius of the first winding end is R1, the inner radius of the first winding end is R2, the outer radius of the second winding end is R3, and the inner radius of the second winding end is R4; satisfying: The ratio of r1 to R1 is not less than 0.2 and less than 0.27; The ratio of r1 to R2 is not less than 0.35 and less than 0.45; The ratio of r1 to R3 is greater than 0.25 and less than 0.27; The ratio of r1 to R4 is greater than 0.44 and less than 0.46.

[0006] In one embodiment, the stator core has a first end face facing the first end shell and a second end face away from the first end shell. A first cavity is formed between the end of the first end shell near the first end face and the first end face. A second cavity is formed between the second end face and the mounting plane of the pump assembly. In the axial direction of the crankshaft, the height of the second winding end is h2, the height of the second cavity is H2, the inner radius of the main housing is R5, the displacement of the pump assembly is P, and the difference between the volume of the second cavity and the volume of the second winding end is [value missing]. ;satisfy: The S1 and The product of the ratio multiplied by 1000 is no less than 0.15 and no greater than 0.35; The P and The ratio is not less than 0.5 and not greater than 1.

[0007] In one embodiment, the stator core has a first end face facing the first end shell and a second end face away from the first end shell. A first cavity is formed between the end of the first end shell near the first end face and the first end face. A second cavity is formed between the second end face and the mounting plane of the pump body assembly. Along the axial direction of the crankshaft, the height of the first cavity is H1, the height of the second cavity is H2, the height of the first end shell is H3, the height of the first winding end is h1, and the height of the second winding end is h2, satisfying: The ratio of h1 to (H1+H3) is not less than 0.4 and not greater than 0.6; And / or, the ratio of h2 to H2 is not less than 0.6 and not greater than 0.9.

[0008] In one embodiment, the outer radius of the first winding end is R1, the outer radius of the second winding end is R3, the inner radius of the main housing is R5, and the inner radius of the first end shell is R6; satisfying: The ratio of R1 to R6 is not less than 0.8 and not greater than 0.95; And / or, the ratio of R3 to R5 is not less than 0.8 and not greater than 0.95.

[0009] In one embodiment, r1 is no greater than 30 mm.

[0010] In one embodiment, the compressor is configured as a vertical rotary compressor, the first end shell is configured as the upper end shell of the housing, the compression component includes a first bearing, a cylinder and a second bearing arranged sequentially from the side near the rotor toward the direction away from the first end shell, and the muffler is disposed on the side of the first bearing away from the cylinder.

[0011] In one embodiment, the muffler includes a bottom cover and a muffler hood disposed on one side of the bottom cover. The side of the bottom cover away from the muffler hood abuts against the compression component. The muffler hood and the compression component enclose a muffler cavity. The compression component has an exhaust passage communicating with the muffler cavity. An exhaust port is disposed on the muffler hood and communicates with the muffler cavity. The exhaust direction of the exhaust port is tangent to the circumferential direction of the muffler hood.

[0012] In one embodiment, the muffler has a plurality of protrusions spaced apart circumferentially, wherein at least one of the protrusions has a first boss and a second boss disposed adjacent to each other, wherein the height of the first boss is greater than the height of the second boss in the axial direction of the crankshaft, and the exhaust port is located on the side of the first boss facing the second boss.

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

[0014] The technical solution of this invention limits the relationship between multiple parameters, such as the total opening area S1 of the exhaust port, the total area S2 of the tangential gap, the outer radius r1 of the rotor, and the inner radius R4 of the end of the second winding, to satisfy the following conditions: the ratio of S1 to S2 is not less than 0.05 and less than 0.12, and S1 and... The ratio of S1 to S2 is not less than 2 and not greater than 3. In this way, without changing the compressor cavity height, by limiting the range of the flow area ratio of the main passages in the exhaust path, the change in the main energy flow path of the high-pressure refrigerant can be controlled. This allows most of the high-pressure refrigerant to flow towards the tangential gap between the stator and the casing, and controls a small portion of the high-pressure refrigerant to flow towards the area between the rotor and the winding coil. This achieves controllable distribution of the high-pressure refrigerant flow, effectively reducing the energy distribution in the rotor impact area, preventing direct impact of the high-pressure refrigerant on the rotor, reducing rotor axial vibration, and improving noise and vibration. Furthermore, by further limiting S1 to S2... The ratio of refrigerant flow to the rotor is not less than 2 and not greater than 3, which further controls the refrigerant flow to the rotor, ensuring it passes through the gap between the rotor and the coil winding as much as possible. This further reduces the axial impact on the rotor, decreases the axial vibration amplitude, and lowers vibration noise. It also controls a small portion of the high-pressure refrigerant flow to the core area of ​​the motor (i.e., the stator, rotor, and coil winding). The coil winding then acts as a filter for the high-pressure refrigerant, preventing it from carrying excessive lubricating oil out of the compressor, thus reducing the compressor's oil discharge rate. Furthermore, the passage of some high-pressure refrigerant through the core area of ​​the motor facilitates heat dissipation, contributing to motor cooling. In this way, 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 cross-sectional schematic diagram of the assembly structure of the stator and housing of the compressor. Figure 3 for Figure 1 A schematic diagram of a cross-section of the compressor perpendicular to its axial direction; Figure 4 A schematic diagram of the rotor of a compressor according to one embodiment; Figure 5 This is a schematic diagram of the assembly structure of the rotor and pump body assembly in one embodiment; Figure 6 for Figure 5 A cross-sectional schematic diagram of the assembly structure of the rotor and pump body components; Figure 7 This is a schematic cross-sectional view of the stator in one embodiment; Figure 8 This is a schematic diagram of the muffler in one embodiment; Figure 9 For S1 / The curve showing the relationship between the amplitude of the rotor's axial vibration and the amplitude of the rotor's axial vibration.

[0017] Explanation of icon numbers: 100. Compressor; 10. Housing; 11. Main housing; 12. First end housing; 13. Second end housing; 20. Motor; 21. Rotor; 22. Stator; 221. Stator core; 221a. First end face; 221b. Second end face; 222. Wire coil winding; 2221. First winding end; 2222. Second winding end; 30. Pump body assembly; 31. Crankshaft; 32. Compression component; 3 21. First bearing; 322. Cylinder; 323. Second bearing; 324. Piston; 325. Sliding vane; 33. Muffler; 331. Bottom cover; 332. Muffler cover; 3321. Exhaust port; 3322. Protrusion; 33221. First boss; 33222. Second boss; 101. Cutting edge clearance; 102. First cavity; 103. Second cavity; 104. Mounting plane of pump body assembly.

[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] In recent years, driven by the demand in the portable terminal market, the design of compressors towards shorter height and smaller size has become a major trend. However, the miniaturization of compressors has led to a reduction in the internal cavity volume of the compressor. When the high-pressure refrigerant is discharged from the top, the concentrated airflow formed will directly impact the rotor, causing axial oscillation of the shaft system and dynamic load fluctuations, which in turn leads to the deterioration of shaft noise and affects the performance of the compressor.

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

[0024] Please see Figures 1 to 4 ,as well as Figure 7 and Figure 8 In one embodiment of the present invention, the compressor 100 includes a housing 10, and a motor 20 and a pump assembly 30 disposed within the housing 10. The housing 10 includes a main housing 11 and a first end shell 12 disposed at one end of the main housing 11. The motor 20 includes a rotor 21 and a stator 22 disposed around the rotor 21. The stator 22 includes a stator core 221 and a coil winding 222. The coil winding 222 has a first winding end 2221 and a second winding end 2222 respectively disposed at both ends of the stator core 221. The first winding end 2221 is located at the end of the stator core 221 facing the first end shell 12. 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 facing the rotor 21. The muffler 33 has an exhaust port 3321. The total opening area of ​​the exhaust port 3321 is S1, the total area of ​​the tangential gap 101 formed between the stator 22 and the housing 10 is S2, the outer radius of the rotor 21 is r1, the inner radius of the second winding end 2222 is R4, and the product of the square difference between R4 and r1 and π is... The following conditions must be met: the ratio of S1 to S2 is not less than 0.05 and less than 0.12; S1 and... The ratio is not less than 2 and not greater than 3.

[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 Figure 1As 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 and magnets disposed on the rotor core. 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 end of the coil winding 222) is located at the upper end of the stator core 221, and the second winding end 2222 (i.e., the opposite side of the end of the coil winding 222) 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 cavity communicating with the exhaust passage and an exhaust port 3321 communicating with the muffler cavity. 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 cavity, where it is silenced and reduced in noise before being discharged from the exhaust port 3321.

[0027] Please combine Figure 1 , Figure 5 and Figure 6Taking 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 324, and a sliding vane 325. The cylinder 322 has a working chamber and a sliding vane groove communicating with the working chamber. The piston 324 is eccentrically rotatably disposed in the working chamber of the cylinder 322. The sliding vane 325 is slidably disposed in the sliding vane groove along the radial direction of the cylinder 322. One end of the sliding vane 325 abuts against or is hinged to the piston 324. The crankshaft 31 has an eccentric portion. The piston 324 is sleeved around the eccentric portion of the crankshaft 31. By rotating the crankshaft 31, the piston 324 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. In the vertical compressor 100, 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). To allow the high-pressure refrigerant in the compression component 32 to be discharged, the first bearing 321 is also provided with a vent hole for connecting the working chamber and the silencer chamber. The high-pressure refrigerant enters the silencer chamber through the vent hole of the first bearing 321, and then is discharged into the cavity of the housing 10 through the exhaust hole 3321. 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, in which at least two cylinders 322 are provided, and a partition is provided between two adjacent cylinders 322.

[0028] The muffler 33 has an exhaust port 3321, which can be located at the top of the muffler 33 for top exhaust, or at the side of the muffler 33 for side exhaust. The shape of the exhaust port 3321 can be circular, elliptical, square, crescent-shaped, or other irregular shapes. The number of exhaust ports 3321 can be designed as one, two, or more, depending on actual needs. When there is only one exhaust port 3321, the total opening area S1 of the exhaust port 3321 is the opening area of ​​that single exhaust port 3321. When there are multiple exhaust ports 3321, the total opening area S1 of the exhaust ports 3321 is the sum of the opening areas of the multiple exhaust ports 3321. The outer periphery of the stator core 221 of the stator 22 is generally not a regular circle, but has a stator tangent. This ensures that after the stator 22 is assembled with the housing 10, a certain tangent gap 101 is formed between the outer wall of the stator 22 and the inner wall of the housing 10. This tangent gap 101 facilitates the flow of high-pressure refrigerant and also allows the refrigerant oil at the top of the motor 20 to flow back to the lower part of the compressor 100 via the tangent gap 101. When there is only one stator tangent, a single tangent gap 101 is formed between the stator 22 and the housing 10, and the total area S2 of the tangent gap 101 is the area of ​​that single tangent gap 101. When there are multiple stator tangents, multiple tangent gaps 101 are formed between the stator 22 and the housing 10, and the total area S2 of the tangent gaps 101 is the sum of the areas of the multiple tangent gaps 101. The maximum outer radius of the projection of rotor 21 onto a projection plane perpendicular to its axial direction is the outer radius r1 of rotor 21, and the inner radius of the part of rotor 21 that mates with crankshaft 31 is r0. The minimum inner radius of the projection of the end of second winding 2222 onto a projection plane perpendicular to the axial direction of rotor 21 is the inner radius R4 of end of second winding 2222.

[0029] Understandably, when the high-pressure refrigerant is discharged from the exhaust port 3321 of the muffler 33, a portion of the high-pressure refrigerant will flow into the cavity formed by the end 2222 of the second winding, and then flow through the gap between the rotor 21 and the stator 22 toward the first end shell 12. Another portion of the high-pressure refrigerant will flow from the tangential gap 101 between the stator 22 and the housing 10 toward the first end shell 12. In the existing design, due to the unreasonable flow distribution design of the exhaust path of the high-pressure refrigerant, the high-pressure refrigerant is usually discharged through the exhaust port 3321 and directly rushes toward the rotor 21. The high-pressure exhaust refrigerant flow is concentrated on the lower surface of the rotor 21, which leads to the deterioration of the axial vibration of the rotor 21 or even axial movement, generating resonance noise or abnormal sounds.

[0030] To mitigate the impact of high-pressure refrigerant on rotor 21, this embodiment defines the relationships between several parameters, including the total opening area S1 of exhaust port 3321, the total area S2 of tangential clearance 101, the outer radius r1 of rotor 21, and the inner radius R4 of the second winding end 2222, satisfying that the ratio of S1 to S2 is not less than 0.05 and less than 0.12, i.e. S1 and The ratio is not less than 2 and not greater than 3, that is... .

[0031] For example, the ratio of S1 to S2 can be 0.05, 0.06, 0.07, 0.08, 0.09, 0.10, 0.11, and any other value within the interval [0.05, 0.12). The ratio can be 2, 2.1, 2.2, 2.3, 2.4, 2.5, 2.6, 2.7, 2.8, 2.9, 3, or any other point value in the interval [2, 3].

[0032] After the high-pressure refrigerant is discharged through the exhaust port 3321, there are two main flow paths. One flow path is the tangential gap 101 between the stator 22 and the housing 10. The other flow path is to first enter the cavity formed by the end of the second winding 2222, and then enter the annular gap between the rotor 21 and the stator 22.

[0033] From a macro perspective, by limiting the ratio of S1 to S2 to be no less than 0.05 and no less than 0.12, S1 and... The ratio is not less than 2 and not greater than 3; thus, the total area of ​​the tangential gap 101 is much larger than the total area of ​​the exhaust port 3321, and the area of ​​the exhaust port 3321 is larger than the area of ​​the annular gap between the second winding end 2222 and the rotor 21. This results in relatively low fluid resistance at the tangential gap 101, while the fluid resistance at the annular gap between the second winding end 2222 and the rotor 21 is relatively greater. Since the airflow tends to flow towards the area with lower resistance, most of the high-pressure refrigerant discharged from the exhaust port 3321 and its kinetic energy will flow through the tangential gap 101, while a small portion of the high-pressure refrigerant will first enter the cavity formed by the second winding end 2222, and then enter the annular gap between the rotor 21 and the stator 22, thus entering the core area of ​​the motor 20. In this way, macroscopically, the high-pressure refrigerant can be diverted to reduce the refrigerant flow to the rotor 21 area, thereby reducing the axial impact force on the rotor 21.

[0034] From a micro perspective, such as Figure 9 As shown, when S1 and When the ratio of S1 to S2 is less than 2, the axial vibration amplitude of rotor 21 tends to increase slightly as the ratio decreases; when S1 and S2 are less than 2, the axial vibration amplitude of rotor 21 tends to increase slightly as the ratio decreases. When the ratio of S1 to S2 is greater than 3, the axial vibration amplitude of rotor 21 increases significantly with the increase of the ratio; when S1 and S2 are greater than 3, the axial vibration amplitude of rotor 21 increases significantly with the increase of the ratio. When the ratio of S1 to S2 is within the range of [2, 3], the axial vibration amplitude of the rotor is in a relatively low range and is generally stable. That is, by limiting S1 to S2... The ratio of S1 to S2 is not less than 2 and not greater than 3, which can further control the refrigerant flowing to the rotor 21 to pass through the gap area between the rotor 21 and the coil winding 222 as much as possible, so as to further reduce the axial impact on the rotor 21, reduce the axial vibration amplitude of the rotor 21, and reduce vibration noise. In addition, by limiting the ratio of S1 to S2 to not less than 0.05 and less than 0.12, the ratio of the total opening area S1 of the exhaust port 3321 to the total area S2 of the tangential gap 101 is moderate. This ensures that the high-pressure refrigerant discharged from the exhaust port 3321 can flow smoothly towards the first end shell 12 through the tangential gap 101; at the same time, it can also avoid the tangential gap 101 being too large, which would lead to an excessively large radial dimension of the shell 10, which is beneficial to the miniaturization of the compressor 100.

[0035] The technical solution of this invention limits the relationship between multiple parameters, such as the total opening area S1 of the exhaust hole 3321, the total area S2 of the tangential gap 101, the outer radius r1 of the rotor 21, and the inner radius R4 of the second winding end 2222, satisfying that: the ratio of S1 to S2 is not less than 0.05 and less than 0.12, and S1 and... The ratio is not less than 2 and not greater than 3. Thus, without changing the height of the compressor 100 cavity, by limiting the range of the flow area ratio of the main passage of the exhaust path, the change in the main energy flow path of the high-pressure refrigerant can be controlled. This allows most of the high-pressure refrigerant to flow to the tangential gap 101 between the stator 22 and the housing 10, while controlling a small portion of the high-pressure refrigerant to flow to the area between the rotor 21 and the coil winding 222. This achieves controllable distribution of the high-pressure refrigerant flow, effectively reducing the energy distribution in the rotor 21 region, preventing direct impact of the high-pressure refrigerant on the rotor 21, reducing axial vibration of the rotor 21, and improving noise and vibration. Furthermore, by further limiting S1 and... The ratio of the refrigerant flow rate to the rotor 21 is not less than 2 and not greater than 3, which further controls the refrigerant flow to the rotor 21 to pass through the gap area between the rotor 21 and the coil winding 222 as much as possible. This further reduces the axial impact on the rotor 21, decreases the axial vibration amplitude of the rotor 21, and reduces vibration noise. In addition, the coil winding 222 can filter the high-pressure refrigerant to prevent it from carrying too much lubricating oil out of the compressor 100, thereby reducing the oil discharge rate of the compressor 100. It also helps to dissipate heat from the core area of ​​the motor 20, which is beneficial to the cooling of the motor 20. In this way, high-efficiency noise reduction and performance optimization can be achieved while maintaining a low overall height.

[0036] After the high-pressure refrigerant is discharged from the exhaust port 3321, it flows sequentially through the inner and outer sides of the second winding end 2222, the gap between the rotor 21 and the stator 22, and the inner and outer sides of the first winding end 2221 as it flows toward the first end shell 12. Therefore, the dimensions of the two ends of the coil winding 222 and the dimensions of the rotor 21 will affect the flow path of the high-pressure refrigerant.

[0037] To further optimize the discharge path of the high-pressure refrigerant and effectively improve the axial vibration problem caused by the direct blowing of high-pressure exhaust refrigerant from the compressor 100 onto the rotor 21, thereby reducing noise and vibration, in one embodiment, the outer radius of the first winding end 2221 is R1, the inner radius of the first winding end 2221 is R2, the outer radius of the second winding end 2222 is R3, and the inner radius of the second winding end 2222 is R4; satisfying the following conditions: the ratio of r1 to R1 is not less than 0.2 and less than 0.27; the ratio of r1 to R2 is not less than 0.35 and less than 0.45; the ratio of r1 to R3 is greater than 0.25 and less than 0.27; and the ratio of r1 to R4 is greater than 0.44 and less than 0.46.

[0038] Wherein, the maximum outer radius of the projection formed by the first winding end 2221 on the projection plane perpendicular to the axial direction of the rotor 21 is the outer radius R1 of the first winding end 2221; the minimum inner radius of the projection formed by the first winding end 2221 on the projection plane perpendicular to the axial direction of the rotor 21 is the inner radius R2 of the first winding end 2221; the maximum outer radius of the projection formed by the second winding end 2222 on the projection plane perpendicular to the axial direction of the rotor 21 is the outer radius R3 of the second winding end 2222; and the minimum inner radius of the projection formed by the second winding end 2222 on the projection plane perpendicular to the axial direction of the rotor 21 is the inner radius R4 of the second winding end 2222.

[0039] In this embodiment, the ratio of r1 to R1 is not less than 0.2 and less than 0.27; that is, 0.2 ≤ r1 / R1 < 0.27. For example, the ratio of r1 to R1 can be 0.2, 0.21, 0.22, 0.23, 0.24, 0.25, 0.26, or any other value within the interval [0.2, 0.27). The ratio of r1 to R2 is not less than 0.35 and less than 0.45; that is, 0.35 ≤ r1 / R2 < 0.45. For example, the ratio of r1 to R2 can be 0.35, 0.36, 0.37, 0.38, 0.39, 0.40, 0.41, 0.42, 0.43, 0.44, or any other value within the interval [0.35, 0.45). The ratio of r1 to R3 is greater than 0.25 and less than 0.27; that is, 0.25 < r1 / R3 < 0.27. For example, the ratio of r1 to R3 can be 0.251, 0.255, 0.26, 0.265, 0.269, or any other value within the interval (0.25, 0.27). The ratio of r1 to R4 is greater than 0.44 and less than 0.46; that is, 0.44 < r1 / R4 < 0.46. For example, the ratio of r1 to R4 can be 0.441, 0.445, 0.45, 0.455, 0.459, or any other value within the interval (0.44, 0.46).

[0040] By confining the parameters r1 / R1, r1 / R2, r1 / R3, and r1 / R4, the flow cross-section of the refrigerant's flow path is essentially constrained. Specifically, the ratio of the outer and inner radii of the second winding end 2222 to the outer diameter of the rotor 21 constrains the flow space of the high-pressure refrigerant at the lower end of the stator 22, while the ratio of the outer and inner radii of the first winding end 2221 to the outer diameter of the rotor 21 constrains the flow space of the high-pressure refrigerant at the upper end of the stator 22. By limiting the values ​​to 0.2≤r1 / R1<0.27, 0.2≤r1 / R1<0.27, 0.25<r1 / R3<0.27, and 0.44<r1 / R4<0.46, the size ratio of the coil winding 222 and the rotor 21 is made suitable. The first winding end 2221 and the second winding end 2222 of the coil winding 222 can form a suitable flow gap with the rotor 21, which is conducive to the smooth flow of high-pressure refrigerant through the flow gap and avoids the high-pressure refrigerant directly hitting the end face of the rotor 21. This can effectively improve the axial vibration problem caused by the high-pressure exhaust refrigerant of the compressor 100 directly blowing into the rotor 21 and reduce noise vibration. If the flow gap between the coil winding 222 and the rotor 21 is too small, it will generate excessive resistance to the refrigerant, causing the refrigerant to be unable to pass through the flow gap smoothly and instead rush directly to the rotor 21. This will result in the high-pressure exhaust refrigerant flow being more concentrated on the lower surface of the rotor 21, leading to worsened axial vibration of the rotor 21 or even axial movement, generating resonance noise or abnormal sounds. If the flow gap between the coil winding 222 and the rotor 21 is too large, it will result in an excessively large distance between the rotor 21 and the stator 22, affecting the performance of the motor 20. It will also increase the overall radial dimension of the motor 20, which is not conducive to the miniaturization of the compressor 100.

[0041] Furthermore, by combining the limitations on parameters such as the total opening area S1 of the exhaust port 3321, the total area S2 of the tangential gap 101, the outer radius r1 of the rotor 21, and the inner radius R4 of the second winding end 222 in the aforementioned embodiments, the optimal design can be achieved in multiple dimensions based on the exhaust process of the compressor 100. This is achieved by sequentially constraining the exhaust area of ​​the muffler 33, the size of the motor 20 winding coil, and the distribution relationship of the stator tangential flow area. This improves exhaust flow and reduces response, effectively mitigating the axial vibration problem caused by the direct blowing of high-pressure exhaust refrigerant from the compressor 100 onto the rotor 21, and reducing noise vibration. This high-rigidity shaft compressor effectively improves noise in the 500~3150Hz frequency band, with an overall noise OA value improvement of more than 3dB.

[0042] When the pump body assembly 30 and the motor 20 are assembled into the housing 10, they will divide the inner cavity of the housing 10 into some cavity structures. These cavity structures also constitute part of the refrigerant exhaust path. After the high-pressure refrigerant is discharged through the exhaust port 3321, it enters the relatively large cavity structure. The cavity structure can buffer and dissipate the pressure pulsation of the high-pressure refrigerant.

[0043] In order to fully dissipate the pulsating excitation of the high-pressure exhaust refrigerant, effectively improve the direct impact force of the high-pressure refrigerant airflow on rotor 21, and reduce the axial pulsating excitation borne by the rotor 21 shaft system, such as... Figure 2 and Figure 7 As shown, in one embodiment, the stator core 221 has a first end face 221a facing the first end shell 12 and a second end face 221b away from the first end shell 12. A first cavity 102 is formed between the end of the first end shell 12 near the first end face 221a and the first end face 221a. A second cavity 103 is formed between the second end face 221b and the mounting plane 104 of the pump body assembly 30. In the axial direction of the crankshaft 31, the height of the second winding end 2222 is h2, the height of the second cavity 103 is H2, the inner radius of the main housing 11 is R5, the displacement of the pump body assembly 30 is P, and the difference between the volume of the second cavity 103 and the volume of the second winding end 2222 is [value missing]. Satisfy: S1 and The product of the ratio of and multiplied by 1000 is no less than 0.15 and no greater than 0.35; P and The ratio is not less than 0.5 and not greater than 1.

[0044] Taking a vertical rotary compressor 100 as an example, the upper end face of the stator core 221 is the first end face 221a, and the lower end face of the stator core 221 is the second end face 221b. The bottom surface of the first end shell 12 (i.e., the upper end shell of the housing 10) and the first end face 221a define a first cavity 102 (i.e., the upper cavity), and the vertical distance between the bottom surface of the first end shell 12 and the first end face 221a is the height H1 of the first cavity 102. The pump body assembly 30 is installed inside the main housing 11, and the plane defined by the connection point between the pump body assembly 30 and the main housing 11 is the mounting plane 104 of the pump body assembly 30. For example, the pump body assembly 30 is generally welded inside the main housing 11, and the inner peripheral wall of the main housing 11 is generally provided with multiple welding points at intervals. The plane defined by the multiple welding points is the mounting plane 104 of the pump body assembly 30. The second end face 221b and the mounting plane of the pump body define a second cavity 103 (i.e., the lower cavity). The vertical distance between the second end face 221b and the mounting plane of the pump body is the height H2 of the second cavity 103. The first winding end 2221 protrudes from the first end face 221a of the stator core 221. The vertical distance from the topmost side of the first winding end 2221 to the first end face 221a is the height h1 of the first winding end 2221. The second winding end 2222 protrudes from the second end face 221b of the stator core 221. The vertical distance from the second end face 221b to the bottommost side of the second winding end 2222 is the height h2 of the second winding end 2222. The main housing 11 is cylindrical, and the radius of the inner cavity section of the main housing 11 is the inner radius R5 of the main housing 11. The compressor 100 can compress refrigerant and provide refrigeration cycle function for the refrigeration system. Its motor 20 drives the pump body assembly 30 to periodically discharge gas. The volume of gas that can be discharged per unit time is defined as the displacement P of the pump body assembly 30.

[0045] In this embodiment, The volume of the second cavity 103 minus the volume of the second winding end 2222 represents the effective buffer volume of the high-pressure refrigerant gas entering the second cavity 103 after being discharged from the exhaust port 3321. Wherein, S1 and... The product of the ratio multiplied by 1000 is no less than 0.15 and no greater than 0.35; that is... For example, S1 and The product of the ratio of and 1000 can be 0.15, 0.20, 0.25, 0.30, 0.35, or any other value within the interval [0.15, 0.35]. P and The ratio is not less than 0.5 and not greater than 1; that is... For example, P and The ratio can be 0.5, 0.6, 0.7, 0.8, 0.9, 1, or any other point value within the interval [0.5, 1].

[0046] It is understandable that the larger the total opening area S1 of the exhaust port 3321, the more pulse energy of the refrigerant injected into the second cavity 103 per unit time; the effective buffer dissipation volume of the second cavity 103... The larger the ratio, the stronger the pulse dissipation capability for high-pressure refrigerant. If the ratio of the total opening area of ​​the exhaust port 3321 to the effective buffer volume of the second cavity 103 is too large, the refrigerant pulse energy injected into the second cavity 103 per unit time by the exhaust port 3321 will be excessive. The effective buffer volume of the second cavity 103 will not match the exhaust area of ​​the exhaust port 3321, and the refrigerant pulse energy will not be effectively dissipated in time. As a result, some refrigerant pulse energy will still directly impact the rotor 21, causing a large pulse excitation to the rotor 21, leading to deterioration of the axial excitation of the rotor 21 and generating resonance noise or abnormal sound problems. If the ratio of the total opening area of ​​the exhaust port 3321 to the effective buffer volume of the second cavity 103 is too small, although the pulse energy dissipation effect is good, it may excessively limit the exhaust efficiency of the exhaust port 3321, increase the exhaust back pressure, and reduce the exhaust efficiency of the compressor 100. Furthermore, the ratio of the pump body assembly 30's displacement to the effective buffer volume of the second chamber 103 must be rationally designed to ensure that the effective buffer volume of the second chamber 103 can effectively dissipate the pulse energy of the high-pressure refrigerant discharged per unit time. If the ratio of the pump body assembly 30's displacement to the effective buffer volume of the second chamber 103 is too large, it indicates that the effective buffer volume of the second chamber 103 is smaller than the pump body assembly 30's displacement. This means that the pulse energy of the high-pressure refrigerant discharged by the pump body assembly 30 per unit time cannot be completely dissipated by the effective buffer volume of the second chamber 103. A portion of the refrigerant pulse energy will still directly impact the rotor 21, causing significant pulse excitation to the rotor 21. This leads to deterioration of the rotor 21's axial excitation, resulting in resonance noise or abnormal sound problems. If the ratio of the effective buffer dissipation volume of the pump body assembly 30 to that of the second cavity 103 is too small, it indicates that the effective buffer dissipation volume of the second cavity 103 is much larger than the displacement of the pump body assembly 30. Although it can fully dissipate the high-pressure refrigerant pulse energy discharged by the pump body assembly 30 per unit time, the volume of the second cavity 103 is too large, which is not conducive to the miniaturization of the overall volume of the compressor 100.

[0047] In this embodiment, by reasonably constraining multiple dimensions such as the total exhaust area of ​​the exhaust port 3321, the displacement of the pump assembly 30, and the effective buffer volume of the second chamber 103, the limitations are achieved. , In this way, after the high-pressure refrigerant discharged through the exhaust port 3321 enters the second chamber 103, the buffering effect of the second chamber 103 allows the pulse energy of the high-pressure refrigerant to be fully dissipated. This allows the high-temperature refrigerant to flow more smoothly over the rotor 21 region, thereby reducing the pulse excitation of the high-pressure refrigerant on the end face of the rotor 21. This makes the pulsating excitation blowing onto the surface of the rotor 21 gentler, reduces the direct impact force of the high-pressure refrigerant airflow on the rotor 21, reduces the axial pulsating excitation borne by the rotor 21 shaft system, reduces the vibration noise of the rotor 21, and makes the rotation of the rotor 21 more stable. Moreover, while ensuring that the pulse energy of the high-pressure refrigerant discharged by the pump assembly 30 per unit time is fully dissipated, the exhaust efficiency of the exhaust port 3321 can be guaranteed, and the volume of the second chamber 103 can be kept from being too large, which is conducive to the miniaturization of the overall size of the compressor 100.

[0048] Please refer to Figure 2 and Figure 7 In one embodiment, the stator core 221 has a first end face 221a facing the first end shell 12 and a second end face 221b away from the first end shell 12. A first cavity 102 is formed between the end of the first end shell 12 near the first end face 221a and the first end face 221a. A second cavity 103 is formed between the second end face 221b and the mounting plane 104 of the pump body assembly 30. In the axial direction of the crankshaft 31, the height of the first cavity 102 is H1, the height of the second cavity 103 is H2, the height of the first end shell 12 is H3, the height of the first winding end 2221 is h1, and the height of the second winding end 2222 is h2, satisfying that: the ratio of h1 to (H1+H3) is not less than 0.4 and not greater than 0.6; and / or, the ratio of h2 to H2 is not less than 0.6 and not greater than 0.9.

[0049] The definitions of the height H1 of the first cavity 102, the height H2 of the second cavity 103, the height h1 of the first winding end 2221, and the height h2 of the second winding end 2222 can be referred to the explanation in the foregoing embodiments, and will not be repeated here.

[0050] It is understandable that (H1+H3) represents the total height between the first end face 221a of the stator core 221 and the inner side of the top wall of the first end shell 12 (that is, the total height of the top cavity of the stator core 221). If the value of h1 / (H1+H3) is too small (for example, less than 0.4) when the height h1 of the first winding end 2221 remains unchanged, it indicates that the total height (H1+H3) of the top cavity of the stator core 221 is large. At this time, although a large space can be reserved between the top surface of the first winding end 2221 and the inner side of the top wall of the first end shell 12 for the high-pressure refrigerant to flow, it will also lead to the overall height of the housing 10 being too high, which is not conducive to the miniaturization of the compressor 100. If the value of h1 / (H1+H3) is too large when the height h1 of the first winding end 2221 remains unchanged, it indicates that the total height (H1+H3) of the top cavity of the stator core 221 is small. At this time, the distance between the top surface of the first winding end 2221 and the inner side of the top wall of the first end shell 12 is small, which will generate greater resistance to the flow of refrigerant and is not conducive to the discharge of refrigerant.

[0051] By limiting the ratio of h1 to (H1+H3) to be no less than 0.4 and no greater than 0.6; that is... This ensures that the ratio of h1 to (H1+H3) is appropriate, providing sufficient space between the top surface of the first winding end 2221 and the inner side of the top wall of the first end shell 12 for the high-pressure refrigerant to flow and ensure smooth refrigerant discharge, while also preventing the overall height of the casing 10 from being too high, which is beneficial for miniaturizing the compressor 100. For example, the ratio of h1 to (H1+H3) can be 0.4, 0.45, 0.5, 0.55, 0.6, or any other value within the range [0.4, 0.6].

[0052] Understandably, if the height h2 at the end of the second winding 2222 remains constant, and the value of h2 / H2 is too small (e.g., less than 0.6), it indicates that the height H2 of the second cavity 103 is large. In this case, the second cavity 103 has a large volume. Although it can fully dissipate the high-pressure refrigerant pulse energy, the large volume of the second cavity 103 is not conducive to the miniaturization of the overall size of the compressor 100. If the height h2 at the end of the second winding 2222 remains constant, and the value of h2 / H2 is too large (e.g., greater than 0.9), it indicates that the height H2 of the second cavity 103 is small. In this case, the end of the second winding 2222 occupies most of the space inside the second cavity 103, making the effective buffer dissipation volume of the second cavity 103 for the high-pressure refrigerant small. This results in the high-pressure refrigerant pulse energy not being fully dissipated, which will generate a large axial impact force on the rotor 21, leading to noise degradation.

[0053] By limiting the ratio of h2 to H2 to be no less than 0.6 and no more than 0.9; that is... This ensures that the ratio of h2 to H2 is appropriate, guaranteeing that the second cavity 103 has sufficient effective buffer and dissipation volume to fully dissipate the high-pressure refrigerant discharged from the exhaust port 3321. This reduces the pulse excitation of the high-pressure refrigerant on the rotor 21 end face, making the pulsating excitation blowing onto the rotor 21 surface gentler, reducing the direct impact force of the high-pressure refrigerant airflow on the rotor 21, reducing the axial pulsating excitation borne by the rotor 21 shaft system, and reducing the vibration noise of the rotor 21. Furthermore, it ensures that the volume of the second cavity 103 is not excessively large, which is beneficial for the miniaturization of the overall compressor 100. For example, the ratio of h2 to H2 can be 0.6, 0.65, 0.7, 0.75, 0.8, 0.85, 0.9, or any other value within the range [0.6, 0.9].

[0054] Optionally, the ratio of h1 to (H1+H3) is not less than 0.4 and not greater than 0.6; the ratio of h2 to H2 is not less than 0.6 and not greater than 0.9. This ensures that the height ratio of the first cavity 102, the second cavity 103, the first winding end 2221, and the second winding end 2222 is moderate. This allows the high-pressure refrigerant discharged from the exhaust port 3321 to first enter the second cavity 103 while maintaining a relatively low overall height of the compressor 100. The second cavity 103 then fully dissipates the pulse energy of the high-pressure refrigerant, reducing the pulse excitation of the high-pressure refrigerant on the end face of the rotor 21, reducing the axial pulsation excitation borne by the rotor 21 shaft system, and reducing the vibration noise of the rotor 21. After passing through the area where the motor 20 is located, the high-pressure refrigerant enters the first cavity 102. The first cavity 102 can further buffer and reduce the noise of the high-pressure refrigerant. In addition, the first cavity 102 has low flow resistance to the high-pressure refrigerant, which is conducive to the high-pressure refrigerant being output from the exhaust pipe on the first end shell 12 to the external refrigerant circulation system.

[0055] In one embodiment, the outer radius of the first winding end 2221 is R1, the outer radius of the second winding end 2222 is R3, the inner radius of the main housing 11 is R5, and the inner radius of the first end housing 12 is R6; satisfying that: the ratio of R1 to R6 is not less than 0.8 and not greater than 0.95; and / or, the ratio of R3 to R5 is not less than 0.8 and not greater than 0.95.

[0056] A first channel gap for refrigerant flow is formed between the outer peripheral surface of the first winding end 2221 and the inner peripheral surface of the first end shell 12. If the first channel gap is too small, it will hinder the refrigerant from entering the first cavity 102; if the first channel gap is too large, it will result in an excessively large radial dimension of the first end shell 12, which will hinder the miniaturization of the compressor 100. By limiting the ratio of R1 to R6 to be no less than 0.8 and no more than 0.95, the width of the first channel gap is moderate, which is conducive to the flow of refrigerant, allowing the refrigerant to smoothly enter the first cavity 102 through the first channel gap, while ensuring that the radial dimension of the first end shell 12 is not too large, which is beneficial to the miniaturization of the compressor 100. For example, the ratio of R1 to R6 can be 0.8, 0.85, 0.9, 0.95, or any point value within the interval [0.8, 0.95].

[0057] A second channel gap for refrigerant flow is formed between the outer peripheral surface of the second winding end 2222 and the inner peripheral surface of the main housing 11. If the second channel gap is too small, it will hinder the refrigerant from entering the tangential gap 101 between the stator 22 and the main housing 11; if the second channel gap is too large, it will result in an excessively large radial dimension of the main housing 11, which is detrimental to the miniaturization of the compressor 100. By limiting the ratio of R3 to R5 to be no less than 0.8 and no more than 0.95, the width of the second channel gap is made moderate, which is conducive to the flow of refrigerant, allowing the refrigerant to smoothly enter the tangential gap 101 from the second channel gap, while ensuring that the radial dimension of the main housing 11 is not too large, which is beneficial to the miniaturization of the compressor 100. For example, the ratio of R3 to R5 can be 0.8, 0.85, 0.9, 0.95, or any point value within the range [0.8, 0.95].

[0058] Optionally, the ratio of R1 to R6 is not less than 0.8 and not greater than 0.95; the ratio of R3 to R5 is not less than 0.8 and not greater than 0.95. This makes the overall radial dimensions of the coil winding 222 and the housing 10 appropriately proportioned, which is beneficial for the flow of refrigerant and also for the miniaturization of the overall size of the compressor 100.

[0059] In one embodiment, the outer radius r1 of the rotor 21 is no greater than 30 mm. That is, r1 ≤ 30 mm. This makes the radial dimension of the rotor 21 relatively small, which is beneficial for reducing the radial dimensions of the motor 20 and the housing 10, and thus for miniaturizing the compressor 100. For example, the outer radius r1 of the rotor 21 can be 30 mm, 29 mm, 28 mm, 27 mm, 26 mm, 25 mm, 24 mm, 23 mm, 22 mm, 21 mm, 20 mm, etc.

[0060] like Figure 1 and Figure 5 As shown, in one embodiment, the compressor 100 is configured as a vertical rotary compressor 100, the first end shell 12 is configured as the upper end shell of the housing 10, and the compression component 32 includes a first bearing 321, a cylinder 322, and a second bearing 323 arranged sequentially from the side near the rotor 21 toward the direction away from the first end shell 12. The muffler 33 is located on the side of the first bearing 321 away from the cylinder 322. The specific structure and working process of the vertical rotary compressor 100 have been described above and will not be repeated here. Of course, in some embodiments, the compressor 100 can also be a horizontal rotary compressor 100, and the first end shell 12 can be configured as the left or right end shell of the housing 10.

[0061] To further reduce the impact of the high-pressure refrigerant on rotor 21, such as Figure 1 and Figure 8 As shown, in one embodiment, the muffler 33 includes a bottom cover 331 and a muffler hood 332 disposed on one side of the bottom cover 331. The side of the bottom cover 331 away from the muffler hood 332 abuts against the compression member 32. The muffler hood 332 and the compression member 32 surround each other to form a muffler cavity. The compression member 32 has an exhaust channel communicating with the muffler cavity. An exhaust port 3321 is disposed on the muffler hood 332 and communicates with the muffler cavity. The exhaust direction of the exhaust port 3321 is tangent to the circumferential direction of the muffler hood 332.

[0062] In this embodiment, the bottom cover 331 includes a first side and a second side facing each other. A silencer 332 is disposed on the first side of the bottom cover 331, and the second side of the bottom cover 331 abuts against the first bearing 321 of the compression component 32, thereby connecting the silencer 332 to the compression component 32. The silencer 332 protrudes from the bottom cover 331 towards the side away from the compression component 32, forming a boss structure. The side of the silencer 332 away from the bottom cover 331 has an opening through which the shaft of the first bearing 321 passes. When the compressor 100 is running, the refrigerant is compressed by the compression component 32 to form high-pressure refrigerant. The high-pressure refrigerant is discharged through the exhaust channel into the silencer chamber of the silencer 332, where the high-pressure refrigerant undergoes primary noise reduction. Then, the high-pressure refrigerant is discharged into the housing 10 through the exhaust port 3321 of the silencer 332. Since the exhaust direction of the exhaust port 3321 is tangent to the circumference of the muffler 332, the high-pressure refrigerant discharged from the exhaust port 3321 can be discharged along the tangential direction of the muffler 332. This avoids the high-pressure refrigerant being directly discharged upward and blown directly onto the rotor 21, thereby further reducing the impact force of the high-pressure refrigerant on the end face of the rotor 21, reducing the axial pulsation excitation on the rotor 21, making the operation of the rotor 21 more stable, and reducing the vibration noise of the rotor 21.

[0063] like Figure 8As shown, in one embodiment, the muffler 332 has a plurality of protrusions 3322 arranged circumferentially, wherein at least one protrusion 3322 has a first protrusion 33221 and a second protrusion 33222 arranged adjacent to each other. 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 exhaust port 3321 is provided on the side of the first protrusion 33221 facing the second protrusion 33222.

[0064] 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. That is, 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. In this way, the first boss 33221 and the second boss 33222 form a stepped structure. The exhaust port 3321 is located at the junction of the first boss 33221 and the second boss 33222. The opening of the exhaust port 3321 faces the top of the second boss 33222. In this way, by utilizing the spatial layout of the bosses, the airflow can be guided in a tangential direction, reducing the axial impact on the rotor and reducing vibration noise.

[0065] 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.

[0066] 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, characterized in that, include: The housing includes a main housing and a first end housing disposed at one end of the main housing; An electric motor, disposed within the housing, includes a rotor and a stator disposed around the rotor. The stator includes a stator core and a coil winding. The coil winding has a first winding end and a second winding end located at opposite ends of the stator core, the first winding end being located at the end of the stator core facing the first end housing. A pump body assembly is disposed within the housing. 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 facing the rotor, and the muffler having an exhaust port. The total opening area of ​​the exhaust port is S1, the total area of ​​the tangential gap formed between the stator and the housing is S2, the outer radius of the rotor is r1, the inner radius of the end of the second winding is R4, and the product of the square difference between R4 and r1 and π is... ; satisfy: The ratio of S1 to S2 is not less than 0.05 and less than 0.12; The S1 and The ratio is not less than 2 and not greater than 3.

2. The compressor as described in claim 1, characterized in that, The outer radius of the first winding end is R1, the inner radius of the first winding end is R2, the outer radius of the second winding end is R3, and the inner radius of the second winding end is R4; satisfying: The ratio of r1 to R1 is not less than 0.2 and less than 0.27; The ratio of r1 to R2 is not less than 0.35 and less than 0.45; The ratio of r1 to R3 is greater than 0.25 and less than 0.27; The ratio of r1 to R4 is greater than 0.44 and less than 0.

46.

3. The compressor as described in claim 2, characterized in that, The stator core has a first end face facing the first end shell and a second end face away from the first end shell. A first cavity is formed between the end of the first end shell near the first end face and the first end face. A second cavity is formed between the second end face and the mounting plane of the pump assembly. Along the axial direction of the crankshaft, the height of the second winding end is h2, the height of the second cavity is H2, the inner radius of the main housing is R5, the displacement of the pump assembly is P, and the difference between the volume of the second cavity and the volume of the second winding end is [value missing]. ; satisfy: The S1 and The product of the ratio multiplied by 1000 is no less than 0.15 and no greater than 0.35; The P and The ratio is not less than 0.5 and not greater than 1.

4. The compressor as described in claim 1, characterized in that, The stator core has a first end face facing the first end shell and a second end face away from the first end shell. A first cavity is formed between the end of the first end shell near the first end face and the first end face. A second cavity is formed between the second end face and the mounting plane of the pump body assembly. Along the axial direction of the crankshaft, the height of the first cavity is H1, the height of the second cavity is H2, the height of the first end shell is H3, the height of the first winding end is h1, and the height of the second winding end is h2, satisfying the following: The ratio of h1 to h2 is not less than 0.4 and not greater than 0.

6. And / or, the ratio of h2 to H2 is not less than 0.6 and not greater than 0.

9.

5. The compressor as described in claim 1, characterized in that, The outer radius of the first winding end is R1, the outer radius of the second winding end is R3, the inner radius of the main housing is R5, and the inner radius of the first end shell is R6; satisfying: The ratio of R1 to R6 is not less than 0.8 and not greater than 0.95; And / or, the ratio of R3 to R5 is not less than 0.8 and not greater than 0.

95.

6. The compressor as claimed in claim 1, characterized in that, The r1 is no greater than 30 mm.

7. The compressor as claimed in claim 1, characterized in that, The compressor is configured as a vertical rotary compressor, the first end shell is configured as the upper end shell of the housing, the compression component includes a first bearing, a cylinder and a second bearing arranged sequentially from the side near the rotor toward the direction away from the first end shell, and the muffler is located on the side of the first bearing away from the cylinder.

8. The compressor as claimed in any one of claims 1 to 7, characterized in that, The muffler includes a bottom cover and a muffler hood disposed on one side of the bottom cover. The side of the bottom cover away from the muffler hood abuts against the compression component. The muffler hood and the compression component enclose a muffler cavity. The compression component has an exhaust channel communicating with the muffler cavity. The exhaust port is disposed on the muffler hood and communicates with the muffler cavity. The exhaust direction of the exhaust port is tangent to the circumference of the muffler hood.

9. The compressor as claimed in claim 8, characterized in that, The muffler has a plurality of protrusions arranged circumferentially, wherein at least one of the protrusions has a first boss and a second boss arranged adjacent to each other. In the axial direction of the crankshaft, the height of the first boss is greater than the height of the second boss, and the exhaust port is located on the side of the first boss facing the second boss.

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

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