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 shell, a motor and a pump body assembly; the distance H1 between the shell opening end and the first end face, the distance H2 between the second end face and the installation plane, the distance H3 between the inner end face and the shell opening end, the inner diameter R5 of the connecting end of the main shell and the first end shell, the inner diameter R7 of the other end, the inner diameter R6 of the first end shell, the height h1, the outer diameter R1 and the inner diameter R2 of the end portion of the first winding, and the height h2, the outer diameter R3 and the inner diameter R4 of the end portion of the second winding are defined, the exhaust oscillation noise of the compressor can be reduced.

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 through the top, it generates axial oscillation impact, causing vibration noise and resulting in an increase in the amount of oil discharged by the compressor. Summary of the Invention

[0003] The main objective of this invention is to provide a compressor and refrigeration equipment that can reduce exhaust oscillation noise and reduce oil discharge while ensuring a small compressor size.

[0004] To achieve the above objectives, the compressor proposed in this invention includes: The housing includes a main housing and a first end housing located at one end of the main housing; An electric motor is disposed within the housing. The motor includes a stator, which comprises a stator core and a coil winding. The coil winding has a first winding end and a second winding end respectively disposed at both ends of the stator core. The first end shell has an inner end face opposite to the first winding end and a shell opening circumferentially disposed around the first winding end. The stator core has a first end face facing the inner end face and a second end face facing away from the inner end face. A pump body assembly is disposed within the housing. The pump body assembly includes a compression component located at the end of the second winding away from the stator core. The compression component has a mounting plane facing the second end face. Along the stator axis, the distance between the shell opening end and the first end face is defined as H1, the distance between the second end face and the mounting plane is defined as H2, the distance between the inner end face and the shell opening end is defined as H3, the inner radius of the end of the main shell connected to the first end shell is R5, the inner radius of the first end shell is R6, the inner radius of the end of the main shell near the end of the second winding is R7, the height of the end of the first winding is h1, the outer radius of the end of the first winding is R1, the inner radius of the end of the first winding is R2, the height of the end of the second winding is h2, the outer radius of the end of the second winding is R3, and the inner radius of the end of the second winding is R4, satisfying: .

[0005] In one embodiment, the first winding end and the second winding end satisfy the following: [h1*(R1 2 -R22 )] and [h2*(R3 2 -R4 2 The ratio of )] is not less than 1.2.

[0006] In one embodiment, a first cavity is formed between the inner end face and the first end face, the first cavity having an axial height of H4; a second cavity is formed between the second end face and the pump body assembly mounting plane, the second cavity having a height of H2; satisfying: The ratio of the axial height h1 at the end of the first winding to the axial height H4 of the first cavity is not less than 0.4 and not greater than 0.6. And / or, the ratio of the axial height h2 at the end of the second winding to the axial height H2 of the second cavity is not less than 0.6 and not greater than 0.9.

[0007] In one embodiment, the ratio of the outer radius R1 of the first winding end to the inner radius R6 of the first end shell is not less than 0.8 and not greater than 0.95. And / or, the ratio of the outer radius R2 of the end of the second winding to the inner radius R7 of the main housing near the end of the second winding is not less than 0.8 and not greater than 0.95.

[0008] In one embodiment, the main housing includes a main body and a connecting portion connected to the first end shell, the connecting portion being flared toward the first end shell.

[0009] In one embodiment, the connecting portion includes a first sub-segment and a second sub-segment, the first sub-segment connecting the main body and the second sub-segment, the first sub-segment being gradually widened toward the first end shell, and the inner side of the second sub-segment connecting to the outer surface of the first end shell.

[0010] In one embodiment, the main body is provided with a uniform inner diameter along the axial direction. The inner radius of the main body is the inner radius R7 of the end of the main housing near the end of the second winding. The maximum inner radius of the second sub-segment is the inner radius R5 of the end of the main housing connected to the first end shell. The ratio of R5 to R7 is not less than 1.05 and not greater than 1.2.

[0011] In one embodiment, the motor further includes a rotor that passes through the stator axially; The pump assembly includes a muffler and a crankshaft connected to the rotor. The compression component and the muffler are sleeved around the crankshaft. The muffler is located on the side of the compression component facing the rotor and has an exhaust port.

[0012] 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, and 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.

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

[0014] The technical solution of this invention defines the distance between the shell opening end and the first end face as H1, the distance between the second end face and the mounting plane as H2, the distance between the inner end face and the shell opening end as H3, the inner radius of the main shell at the end connecting to the first end shell as R5, the inner radius of the first end shell as R6, the inner radius of the main shell at the end near the second winding end as R7, the height of the first winding end as h1, the outer radius of the first winding end as R1, the inner radius of the first winding end as R2, the height of the second winding end as h2, the outer radius of the second winding end as R3, and the inner radius of the second winding end as R4. Calculate the actual volume of the upper chamber exhaust space by... Calculate the volume at the end of the first winding, by... Calculate the actual volume of the lower chamber exhaust space by... The volume of the second winding end is calculated so that the ratio of the difference between the actual volume of the upper exhaust space and the volume of the first winding end to the difference between the actual volume of the lower exhaust space and the volume of the second winding end is between 2.0 and 2.5. This makes the exhaust volume of the upper exhaust space smaller than that of the lower exhaust space, creating a larger buffer space. When the high-pressure gas is discharged from the pump assembly, it first enters the lower exhaust space. The smaller exhaust volume of the lower exhaust space allows for rapid establishment of the initial exhaust pressure, avoiding diffusion turbulence of the airflow under low pressure. Subsequently, the airflow enters the larger upper exhaust space, where the expansion of space reduces the flow velocity, minimizing the oscillation impact of the high-speed airflow on the housing and the end of the first winding, preventing airflow congestion caused by narrow space, and reducing pressure fluctuations and pulsating noise. Furthermore, the larger actual exhaust volume of the upper exhaust space allows for sufficient space to gradually reduce the flow velocity during the upward movement of the airflow. The lubricating oil mixed in the gaseous refrigerant settles due to gravity, reducing the amount of oil entering the exhaust pipe with the airflow, thereby reducing the amount of oil discharged. 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 schematic diagram of the structure of an embodiment of the compressor provided by the present invention; Figure 2 for Figure 1 A magnified view of a section at point A in the middle; Figure 3 for Figure 1 Schematic diagram of the dimensional relationships of the centerline winding; Figure 4 for Figure 1 A schematic diagram showing the dimensional relationship between the first and second cavities. Figure 5 for Figure 1 A schematic diagram of the structure of the muffler.

[0017] Explanation of icon numbers: 100. Compressor; 10. Housing; 1011. First cavity; 1012. Second cavity; 102. Exhaust end; 11. Main housing; 111. Main body; 112. Connecting part; 1121. First sub-section; 1122. Second sub-section; 12. First end shell; 121. Inner end face; 122. Shell port end; 20. Pump body assembly; 21. Compression component; 21a. Mounting plane; 211. First bearing; 212. Cylinder; 213. Second bearing; 22. Silencer; 221. Exhaust port; 23. Crankshaft; 30. Motor; 31. Stator; 311. Stator core; 3111. First end face; 3112. Second end face; 312. Wire winding; 3121. First winding end; 3122. Second winding end; 32. Rotor; 40. Liquid reservoir.

[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 through the top, it generates axial oscillation impact, causing vibration noise and resulting in an increase in the amount of oil discharged by the compressor.

[0023] This invention proposes a compressor 100.

[0024] Please see Figures 1 to 5 In one embodiment of the present invention, the compressor 100 includes a housing 10, a motor 30, and a pump assembly 20; 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 30 is disposed within the housing 10, and the motor 30 includes a stator 31, the stator 31 including a stator core 311 and a coil winding 312, the coil winding 312 having a first winding end 3121 and a second winding end 3122 respectively disposed at both ends of the stator core 311, and the first end shell 12 having a connection with the first winding end 312. The stator core 311 has an inner end face 121 opposite to the inner end face 121 and a shell end 122 surrounding the first winding end 3121. The stator core 311 has a first end face 3111 facing the inner end face 121 and a second end face 3112 away from the inner end face 121. The pump body assembly 20 is disposed in the housing 10. The pump body assembly 20 includes a compression component 21. The compression component 21 is located on the side of the second winding end 3122 away from the stator core 311. The compression component 21 has a mounting plane 21a facing the second end face 3112. Along the axial direction of the stator 31, the distance between the shell end 122 and the first end face 3111 is defined as H1, the distance between the second end face 3112 and the mounting plane 21a is defined as H2, the distance between the inner end face 121 and the shell end 122 is defined as H3, the inner radius of the end of the main shell 11 connected to the first end shell 12 is R5, the inner radius of the first end shell 12 is R6, the inner radius of the end of the main shell 11 near the second winding end 3122 is R7, the height of the first winding end 3121 is h1, the outer radius of the first winding end 3121 is R1, the inner radius of the first winding end 3121 is R2, the height of the second winding end 3122 is h2, the outer radius of the second winding end 3122 is R3, and the inner radius of the second winding end 3122 is R4, satisfying: .

[0025] In this invention, the compressor 100 can be a vertical compressor 100 or a horizontal compressor 100. The compressor 100 includes a housing 10 and a motor 30 and a pump assembly 20 disposed within the housing 10. A liquid receiver 40 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 at the same time, the housing 10 and the internal components together define 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 respectively disposed at the two open ends of the main housing 11. The first end shell 12 and the second end shell 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 the exhaust pipe. The motor 30 and the pump body assembly 20 are located inside the housing 10. The motor 30 is used to drive the pump body assembly 20 to move, compress the refrigerant through the pump body assembly 20, 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. The first end shell 12 and the second end shell are respectively fixed to the axial ends of the main housing 11. The first end shell 12 is the upper end shell of the housing 10, and the second end shell is the lower end shell of the housing 10. The first end shell 12 has an exhaust end 102, which is used to connect to the exhaust pipe of the compressor 100. The motor 30 includes a rotor 32 and a stator 31. The stator 31 is fixed inside the main housing 11 and sleeved around the rotor 32. The rotor 32 is sleeved around the crankshaft 23 of the pump body assembly 20. The rotor 32 includes a rotor core and a magnet disposed on the rotor core. The stator 31 includes a stator core 311 and a coil winding 312 wound around the stator core 311. The coil winding 312 is used to connect to the power supply circuit. When the motor 30 is working, it generates an induced magnetic field under the synergistic effect of the stator 31 and the rotor 32, causing the rotor 32 to rotate relative to the stator 31, thereby driving the crankshaft 23 to rotate. The coil winding 312 includes a first winding end 3121 and a second winding end 3122 located at both ends of the stator core 311. The first winding end 3121 (i.e., the positive side of the end of the coil winding 312) is located at the upper end of the stator core 311, and the second winding end 3122 (i.e., the opposite side of the end of the coil winding 312) is located at the lower end of the stator core 311. The first winding end 3121 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 20 includes a crankshaft 23 connected to the rotor 32, and a compression component 21 and a muffler 22 sleeved around the crankshaft 23. The compression component 21 has an intake passage for refrigerant to enter and an exhaust passage for high-pressure refrigerant to exit. The muffler 22 has a muffler cavity communicating with the exhaust passage and an exhaust port 221 communicating with the muffler cavity.

[0027] After the refrigerant in the external circulation system enters the compression component 21 through the intake channel, the refrigerant is compressed by the compression component 21 to perform work. The resulting high-pressure refrigerant is discharged from the exhaust channel into the silencing chamber. After being silencing and reducing noise in the silencing chamber, it is discharged from the exhaust port 221 into the gap between the housing 10 and the second winding end 3122. It passes through the gap between the housing 10 and the second winding end 3122, the gap between the housing 10, the stator core 311 and the rotor 32, and the gap between the housing 10 and the first winding end 3121 in sequence, and is discharged from the exhaust end 102 on the first end shell 12 into the external refrigerant circulation system.

[0028] Of course, in other embodiments, the compressor 100 may also be a multi-cylinder 212 rotary compressor 100, with at least two cylinders 212 provided and a partition provided between two adjacent cylinders 212.

[0029] It is understandable that when exhausting gas inside the compressor 100, the space between the stator 31 and the pump assembly 20 is roughly the lower exhaust space inside the compressor 100, which can be defined as the second cavity 1012. The space between the stator 31 and the first end shell 12 is roughly the upper exhaust space inside the compressor 100, which can be defined as the first cavity 1011. In the inner cavity of the compressor 100, the exhaust flow path is from the exhaust port 221 of the muffler 22 to the exhaust end 102 of the first end shell 12. When the pump assembly 20 is venting gas, the high-pressure gaseous refrigerant will first pass through the second cavity 1012, then through the gap between the stator 31 and the housing 10 into the first cavity 1011, then from the first cavity 1011 into the exhaust end 102, and finally be discharged from the compressor 100.

[0030] The plane defined by the connection point between the compression component 21 and the main housing 11 is the mounting plane 21a. For example, the compression component 21 of the pump body assembly 20 is generally welded to the main housing 11. 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 21a of the compression component 21. The shell opening end 122 surrounding the first winding end 3121 can be the opening end of the first end shell 12 facing the main housing 11. The first winding end 3121 can be partially located in the first end shell or entirely located in the main housing 11. No limitation is made here.

[0031] It is understandable that the actual volume of the first cavity 1011 is the space between the inner end face 121 of the first end shell 12 and the first end face 3111 of the stator core 311. The volume available for refrigerant flow must be reduced by the volume of the first winding end 3121 and the volume of the rotor 32 in the first cavity 1011. Similarly, the actual volume of the second cavity 1012 is the space between the mounting plane 21a of the compression component 21 and the second end face 3112 of the stator core 311. The actual volume available for refrigerant flow must be reduced by the volume of the second winding end 3122 and the volume of the rotor 32 in the second cavity 1012. With the rotor 32 volume remaining constant, the relationship between the size of the first winding end 3121 and the volume of the first cavity 1011 determines the volume of the first cavity 1011 available for refrigerant flow, and the relationship between the size of the second winding end 3122 and the volume of the second cavity 1012 determines the volume of the second cavity 1012 available for refrigerant flow.

[0032] Through formula Calculate the actual volume of the first cavity 1011. Where H1 is the distance between the shell opening 122 and the first end face 3111, H3 is the distance between the inner end face 121 and the shell opening 122, and the sum of these two is the height of the first cavity 1011. R5 is the inner radius of the end where the main shell 11 connects to the first end shell 12. R6 is the volume of the first cavity 1011 from the shell opening end 122 to the first end face 3111, and R6 is the inner radius of the first end shell 12. The volume of the first cavity 1011 from the inner end face 121 to the shell opening end 122.

[0033] Through formula Calculate the volume occupied by the first winding end 3121 within the first cavity 1011. Where R1 is the outer radius of the first winding end 3121, R2 is the inner radius of the first winding end 3121, and the difference of the squares of the two, multiplied by π and the height h1 of the first winding end 3121, is the volume occupied by the first winding end 3121 within the first cavity 1011.

[0034] Through formula Calculate the volume of the second cavity 1012. Where H2 is the distance between the second end face 3112 and the mounting plane 21a, which is the height of the second cavity 1012, and R7 is the inner radius of the main housing 11 near the end of the second winding 3122.

[0035] Calculated using formula Calculate the volume occupied by the second winding end 3122 within the second cavity 1012. Here, R3 is the outer radius of the second winding end 3122, R4 is the inner radius of the second winding end 3122, and the difference of their squares multiplied by π and the height h2 of the second winding end 3122 equals the volume occupied by the second winding end 3122 within the second cavity 1012.

[0036] With the rotor volume remaining constant, the ratio of the difference between the actual volume of the first cavity 1011 and the volume of the first winding end 3121 to the difference between the actual volume of the second cavity 1012 and the volume of the second winding end 3122 is defined to be between 2.0 and 2.5, i.e., satisfying the condition... .

[0037] This makes the exhaust volume of the first chamber 1011 smaller than that of the second chamber 1012, creating a larger buffer space. When the high-pressure gas is discharged from the pump body, it first enters the second chamber 1012. The smaller volume of the second chamber 1012 can quickly establish the initial exhaust pressure, avoiding diffusion turbulence of the airflow under low pressure. Subsequently, the airflow enters the larger volume of the first chamber 1011, where the flow velocity is reduced by expanding the space, reducing the impact of high-speed airflow on the housing 10 and the end of the first winding 3121, while avoiding airflow congestion caused by narrow space, thereby reducing pressure fluctuations and pulsating noise.

[0038] The first chamber 1011 serves as the main exhaust channel. Its large volume allows for sufficient space to gradually reduce the flow rate of the airflow as it rises. The lubricating oil mixed in the gaseous refrigerant settles due to gravity, reducing the amount of oil entering the exhaust pipe with the airflow, thereby reducing the amount of oil discharged.

[0039] For example, the ratio of the difference between the actual volume of the first cavity 1011 and the volume of the first winding end 3121 to the difference between the actual volume of the second cavity 1012 and the volume of the second winding end 3122 can be 2.0, 2.1, 2.2, 2.3, 2.4, 2.5, and any point value within the interval [2.0, 2.5].

[0040] The technical solution of this invention defines the distance between the shell end 122 and the first end face 3111 as H1, the distance between the second end face 3112 and the mounting plane 21a as H2, the distance between the inner end face 121 and the shell end 122 as H3, the inner radius of the end connecting the main shell 11 and the first end shell 12 as R5, the inner radius of the first end shell 12 as R6, the inner radius of the end of the main shell 11 near the second winding end 3122 as R7, the height of the first winding end 3121 as h1, the outer radius of the first winding end 3121 as R1, the inner radius of the first winding end 3121 as R2, the height of the second winding end 3122 as h2, the outer radius of the second winding end 3122 as R3, and the inner radius of the second winding end 3122 as R4. Calculate the actual volume of the upper chamber exhaust space by... Calculate the volume of the first winding end 3121 by... Calculate the actual volume of the lower chamber exhaust space by... Calculate the volume of the second winding end 3122, so that the ratio of the difference between the actual volume of the upper cavity exhaust space and the volume of the first winding end 3121 to the difference between the actual volume of the lower cavity exhaust space and the volume of the second winding end 3122 is between 2.0 and 2.5, so that the exhaust volume of the upper cavity exhaust space is smaller than that of the lower cavity exhaust space, and the upper cavity exhaust space forms a larger buffer space. After the high-pressure gas is discharged from the pump body assembly 20, it first enters the lower exhaust space. The smaller exhaust volume of the lower exhaust space can quickly establish the initial exhaust pressure, avoiding the diffusion turbulence of the airflow under low pressure. Subsequently, the airflow enters the larger upper exhaust space. The flow velocity is reduced by the expansion of the space, which reduces the oscillation impact of the high-speed airflow on the housing 10 and the end of the first winding 3121, avoids the airflow blockage caused by the narrow space, and reduces pressure fluctuations and pulsating noise. In addition, the larger actual exhaust volume of the upper exhaust space can reserve enough space to allow the flow velocity to gradually decrease during the upward process. The lubricating oil mixed in the gaseous refrigerant settles due to gravity, reducing the amount of oil entering the exhaust pipe with the airflow, thereby reducing the amount of oil discharged.

[0041] Optionally, the first winding end 3121 and the second winding end 3122 satisfy the following: [h1*(R1 2 -R2 2 )] and [h2*(R3 2 -R4 2 The ratio of )] is not less than 1.2.

[0042] Among them, R1 2 -R2 2 R1 is the difference of the squares of the outer radius R1 and the inner radius R2 of the first winding end 3121, h1 is the height of the first winding end 3121, and R3 is the height of the first winding end 3121. 2 -R4 2 Let R1 be the square difference between the outer radius R3 and the inner radius R4 of the second winding end 3122, and h2 be the height of the second winding end 3122. [h1*(R4)] 2 -R2 2 )] and [h2*(R3 2 -R4 2 The ratio of 1.2 to the actual volume of the end of the first winding 3121 is not less than 1.2.

[0043] That is, the actual volume of the first winding end 3121 is at least 1.2 times that of the second winding end 3122. This design is consistent with... The spatial arrangement creates synergy. The larger volume of the first winding end 3121 can match the larger exhaust volume of the first cavity 1011, avoiding wasted space in the first cavity 1011 due to the small coil volume, avoiding increased resistance caused by airflow diffusion, and achieving spatial balance between the volume of the first winding end 3121 and the volume of the first cavity 1011.

[0044] Optionally, such as Figure 3 , Figure 4 As shown, a first cavity 1011 is formed between the inner end face 121 and the first end face 3111, and the axial height of the first cavity 1011 is H4. A second cavity 1012 is formed between the second end face 3112 and the mounting plane 21a of the pump body assembly 20, and the height of the second cavity 1012 is H2; satisfying: The ratio of the axial height h1 of the first winding end 3121 to the axial height H4 of the first cavity 1011 is not less than 0.4 and not greater than 0.6. And / or, the ratio of the axial height h2 of the second winding end 3122 to the axial height H2 of the second cavity 1012 is not less than 0.6 and not greater than 0.9.

[0045] Wherein, the axial height H4 of the first cavity 1011 is the sum of the distance H1 between the shell opening end 122 and the first end face 3111 and the distance H3 between the inner end face 121 and the shell opening end 122. The height H2 of the second cavity 1012 is the distance between the second end face 3112 and the mounting plane 21a.

[0046] Understandably, when the ratio of h1 to H4 is not less than 0.4, it ensures that the height of the first winding end 3121 is sufficient to accommodate a sufficient number of winding turns or thicker wires, thereby increasing the electromagnetic induction intensity, reducing copper losses, and supporting efficient electromagnetic conversion. If the ratio is too small, insufficient coil volume will lead to a decrease in electromagnetic efficiency. When the ratio of h1 to H4 is not greater than 0.6, it ensures that the first cavity 1011 reserves at least 40% of the space as an exhaust channel. When the ratio of the difference between the actual volume of the first cavity 1011 and the volume of the first winding end 3121 to the difference between the actual volume of the second cavity 1012 and the volume of the second winding end 3122 is between 2.0 and 2.5, sufficient buffer space is provided for high-pressure exhaust, so that the airflow velocity decreases after entering the first cavity 1011, reducing the impact of high-speed airflow on the housing and the first winding end 3121, thereby reducing pulsating noise. Furthermore, the lower flow velocity allows the lubricating oil to settle due to gravity, reducing the amount of oil carried out with the exhaust.

[0047] For example, the ratio of h1 to H4 can be 0.4, 0.45, 0.5, 0.55, 0.6, or any point value within the interval [0.4, 0.6].

[0048] Understandably, when the ratio of h2 to H2 is not less than 0.6, the height of the second winding end 3122 can account for more than 60% of the height of the second cavity 1012, resulting in a more compact coil structure. When the ratio of the difference between the actual volume of the first cavity 1011 and the volume of the first winding end 3121 to the difference between the actual volume of the second cavity 1012 and the volume of the second winding end 3122 is between 2.0 and 2.5, airflow diffusion in the small-volume second cavity 1012 can be avoided. During exhaust, the pump assembly 20 can quickly establish exhaust pressure within the second cavity 1012, reducing airflow turning resistance and improving exhaust efficiency. When h2 / H2 ≤ 0.9, an excessively large height of the second winding end 3122 can be avoided, preventing the forced increase in the height H2 of the second cavity 1012 and thus increasing the overall size of the compressor 100. By compressing the redundant space between the end 3122 of the second winding and the second cavity 1012, the axial dimension of the second cavity 1012 is minimized while satisfying electromagnetic efficiency, making the compressor 100 smaller and facilitating miniaturization.

[0049] For example, the ratio of h2 to H2 can be 0.6, 0.7, 0.8, 0.9, or any point value within the interval [0.6, 0.9].

[0050] The above design for the first winding end 3121 and the second winding end 3122 can satisfy either one or both, and no specific limitation is made here.

[0051] like Figure 3 , Figure 4 As shown, optionally, the ratio of the outer radius R1 of the first winding end 3121 to the inner radius R6 of the first end shell 12 is not less than 0.8 and not greater than 0.95.

[0052] And / or, the ratio of the outer radius R2 of the second winding end 3122 to the inner radius R7 of the main housing 11 near the end of the second winding end 3122 is not less than 0.8 and not greater than 0.95.

[0053] It is understandable that a first channel gap for refrigerant flow is formed between the outer peripheral surface of the first winding end 3121 and the inner peripheral surface of the first end shell 12. If the ratio of R1 to R6 is too small, the first channel gap between the first winding end 3121 and the inner diameter R6 of the first end shell 12 will be too wide. After the high-pressure exhaust enters the first cavity 1011, it is easy to form a diffusion flow field, resulting in uneven flow velocity distribution and increased local turbulence, which in turn causes airflow impact noise and secondary entrainment of lubricating oil mist. If the ratio of R1 to R6 is too large, the gap will be too narrow, which will cause the airflow velocity to increase sharply. The high-speed airflow will easily carry lubricating oil and impact the shell, resulting in increased oil discharge and increased pulsating noise. When the ratio of R1 to R6 is between 0.8 and 0.95, and the ratio of the difference between the actual volume of the first cavity 1011 and the volume of the first winding end 3121 to the difference between the actual volume of the second cavity 1012 and the volume of the second winding end 3122 is between 2.0 and 2.5, the gap control of 0.8 to 0.95 can make the first cavity 1011 form a "stable flow channel" on the basis of a large volume. The airflow flows uniformly along the outer periphery of the coil, reducing local eddies. It can also be combined with the ratio of the height H1 of the first cavity 1011 to the height h1 of the first winding end 3121 (0.4≤h1 / H1≤0.6) to achieve dual optimization of low flow velocity and stable flow field.

[0054] 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].

[0055] A second channel gap for refrigerant flow is formed between the outer peripheral surface of the second winding end 3122 and the inner peripheral surface of the main housing 11. By setting the ratio of the outer radius R2 of the second winding end 3122 to the inner radius R7 of the main housing 11 near the second winding end 3122 to be between 0.8 and 0.95, a narrower second channel gap can be ensured. This allows airflow to quickly pass through the second cavity 1012 and establish stable pressure when the ratio of the difference between the actual volume of the first cavity 1011 and the volume of the first winding end 3121 to the difference between the actual volume of the second cavity 1012 and the volume of the second winding end 3122 is between 2.0 and 2.5. This reduces airflow diffusion resistance caused by an excessively wide gap or pressure loss caused by an excessively narrow gap.

[0056] For example, the ratio of R3 to R5 can be 0.8, 0.85, 0.9, 0.95, or any point value within the interval [0.8, 0.95].

[0057] When both of the above conditions are met, that is, R1 / R6 and R3 / R5 are both controlled between 0.8 and 0.95, the radial gap of the exhaust path formed by the first cavity 1011 and the second cavity 1012 forms a "smooth transition", avoiding the generation of local vortices when the airflow turns due to excessive difference in the upper and lower gaps.

[0058] like Figure 1 , Figure 2 As shown, in one embodiment, the main housing 11 includes a main body 111 and a connecting portion 112 connected to the first end housing 12, the connecting portion 112 being flared toward the first end housing 12.

[0059] It is understandable that the volume of the first cavity 1011 is determined by its axial height and radial width. When the connecting portion 112 is flared towards the first end shell 12, the main shell 11 has a non-uniform diameter configuration, with the inner diameter of the main shell 11 on the side of the connecting portion 112 being larger than the inner diameter of the side of the main shell 11 away from the first end shell 12. This increases the width of the first cavity 1011 within the connecting portion 112, allowing for a reduction in the overall height of the first cavity 1011 while maintaining its volume. This, in turn, reduces the overall height of the compressor 100, thus facilitating its miniaturization. Furthermore, the flared connecting portion 112 increases the distance between the inner side of the main shell 11 and the first winding end 3121, preventing high-temperature welding damage to the first winding end 3121 during welding of the connecting portion 112 to the first end shell 12.

[0060] like Figure 1 , Figure 2As shown, in one embodiment, the connecting portion 112 includes a first sub-segment 1121 and a second sub-segment 1122. The first sub-segment 1121 connects the main body portion 111 and the second sub-segment 1122. The first sub-segment 1121 is gradually widened toward the first end shell 12, and the inner side of the second sub-segment 1122 is connected to the outer surface of the first end shell 12.

[0061] This configuration increases the local inner diameter of the first cavity 1011 by gradually widening the first segment 1121, thus increasing the strength of the connection between the first segment 1121 and the main body 111. To facilitate the connection between the connecting part 112 and the first end shell 12, the connecting part 112 further includes a second segment 1122, with its inner surface connected to the outer surface of the first end shell 12. The second segment 1122 serves to connect and mate with the first end shell 12, and its inner surface adapts to the shape of the outer surface of the first end shell 12, facilitating a tight weld between the first end shell 12 and the connecting part 112. This reduces the overall height of the first cavity 1011 while further increasing the tightness of the connection between the main body 11 and the first end shell 12.

[0062] Optionally, the main body 111 is provided with a uniform inner diameter along the axial direction. The inner radius of the main body 111 is the inner radius R7 of the end of the main housing 11 near the second winding end 3122. The maximum inner radius of the second sub-segment 1122 is the inner radius R5 of the end of the main housing 11 connected to the first end shell 12. The ratio of R5 to R7 is not less than 1.05 and not greater than 1.2.

[0063] R7 is the inner radius of the main body 111, and the inner radius of the end where the main housing 11 connects to the first end housing 12. It is also the maximum inner radius of the second sub-segment 1122. Since the actual volume of the first cavity 1011 is larger than that of the second cavity 1012, when the maximum inner diameter of the first cavity 1011 is made larger through the gradual expansion of the connecting part 112, a larger radial space can be provided for the first cavity 1011. Under the premise of miniaturizing the compressor 100, that is, the height of the first cavity 1011 cannot be too high, it is easy to achieve the design target that the ratio of the difference between the actual volume of the first cavity 1011 and the volume of the first winding end 3121 to the difference between the actual volume of the second cavity 1012 and the volume of the second winding end 3122 is between 2.0 and 2.5.

[0064] In addition, if the ratio of R5 to R7 is too large, the difference between the inner diameters of the upper and lower ends will be too large, causing the airflow to turn sharply when it enters the first cavity 1011 from the lower cavity, forming a local vortex zone, which increases exhaust resistance and pressure loss.

[0065] like Figure 1 , Figure 3 As shown, the motor 30 also includes a rotor 32, which passes through the stator 31 axially; The pump body assembly 20 includes a muffler 22 and a crankshaft 23. The crankshaft 23 is connected to the rotor 32. The compression component 21 and the muffler 22 are sleeved around the crankshaft 23. The muffler 22 is located on the side of the compression component 21 facing the rotor 32. The muffler 22 has an exhaust port 221.

[0066] The stator 31 is fixed inside the main housing 11 and sleeved around the rotor. The rotor is sleeved around the crankshaft 23 of the pump body assembly 20. The rotor includes a rotor core and a magnet disposed on the rotor core. When the motor is working, an induced magnetic field is generated under the synergistic effect of the stator 31 and the rotor, so that the rotor can rotate relative to the stator 31, thereby driving the crankshaft 23 to rotate.

[0067] The pump assembly 20 includes a crankshaft 23 connected to a rotor, and a compression component 21 and a muffler 22 sleeved around the crankshaft 23. The compression component 21 has an intake passage for refrigerant and an exhaust passage for high-pressure refrigerant. The muffler 22 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 21 through the intake passage, and is compressed by the compression component 21 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 into the second chamber 1012.

[0068] Taking a single-cylinder rotary compressor 100 as an example, the compression component 21 includes a first bearing 211, a cylinder 212, a second bearing 213, a piston, and a sliding vane. The cylinder 212 has a working chamber and a sliding vane groove communicating with the working chamber. The piston is eccentrically rotatably disposed within the working chamber of the cylinder 212, and the sliding vane is radially slidably disposed within the sliding vane groove of the cylinder 212. One end of the sliding vane abuts against or is hinged to the piston. The crankshaft 23 has an eccentric portion, and the piston is sleeved around the eccentric portion of the crankshaft 23. By rotating the crankshaft 23, the piston can be driven to rotate eccentrically against the inner surface of the cylinder 212 to compress the gas in the working chamber and form a high-pressure refrigerant. The first bearing 211 and the second bearing 213 are respectively disposed on opposite sides of the cylinder 212 to seal both ends of the cylinder 212 and also to support the crankshaft 23. In this design, the first bearing 211 is located on the side of the cylinder 212 closer to the motor 30, and the second bearing 213 is located on the side of the cylinder 212 away from the motor 30. In the vertical compressor 100, the first bearing 211 is the upper bearing (i.e., the main bearing), and the second bearing 213 is the lower bearing (i.e., the auxiliary bearing). To allow the high-pressure refrigerant in the compression component 21 to be discharged, the first bearing 211 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 211, and then is discharged into the cavity of the housing through the exhaust hole 221. After passing through the gap between the housing and the motor 30, as well as the internal gap of the motor 30, it is discharged into the external refrigerant circulation system through the exhaust pipe on the first end shell. Of course, in other embodiments, the compressor 100 can also be a multi-cylinder 212 rotary compressor 100, in which at least two cylinders 212 are provided, and a partition is provided between two adjacent cylinders 212.

[0069] like Figure 1 , Figure 3 , Figure 4 As shown, 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 21 includes a first bearing 211, a cylinder 212, and a second bearing 213 arranged sequentially from the side near the rotor toward the direction away from the first end shell 12. 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.

[0070] 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.

[0071] 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 located at one end of the main housing; An electric motor is disposed within the housing. The motor includes a stator, which comprises a stator core and a coil winding. The coil winding has a first winding end and a second winding end respectively disposed at both ends of the stator core. The first end shell has an inner end face opposite to the first winding end and a shell opening circumferentially disposed around the first winding end. The stator core has a first end face facing the inner end face and a second end face facing away from the inner end face. A pump body assembly is disposed within the housing. The pump body assembly includes a compression component located at the end of the second winding away from the stator core. The compression component has a mounting plane facing the second end face. Along the stator axis, the distance between the shell opening end and the first end face is defined as H1, the distance between the second end face and the mounting plane is defined as H2, the distance between the inner end face and the shell opening end is defined as H3, the inner radius of the end of the main shell connected to the first end shell is R5, the inner radius of the first end shell is R6, the inner radius of the end of the main shell near the end of the second winding is R7, the height of the end of the first winding is h1, the outer radius of the end of the first winding is R1, the inner radius of the end of the first winding is R2, the height of the end of the second winding is h2, the outer radius of the end of the second winding is R3, and the inner radius of the end of the second winding is R4, satisfying: 。 2. The compressor as described in claim 1, characterized in that, The following conditions must be met between the ends of the first winding and the ends of the second winding: [h1*(R1 2 -R2 2 )] and [h2*(R3 2 -R4 2 The ratio of )] is not less than 1.

2.

3. The compressor as described in claim 1, characterized in that, A first cavity is formed between the inner end face and the first end face, and the axial height of the first cavity is H4. A second cavity is formed between the second end face and the pump body assembly mounting plane, and the height of the second cavity is H2; satisfying: The ratio of the axial height h1 at the end of the first winding to the axial height H4 of the first cavity is not less than 0.4 and not greater than 0.

6. And / or, the ratio of the axial height h2 at the end of the second winding to the axial height H2 of the second cavity is not less than 0.6 and not greater than 0.

9.

4. The compressor as described in claim 1, characterized in that, The ratio of the outer radius R1 of the first winding end to the inner radius R6 of the first end shell is not less than 0.8 and not greater than 0.

95. And / or, the ratio of the outer radius R2 of the end of the second winding to the inner radius R7 of the main housing near the end of the second winding is not less than 0.8 and not greater than 0.

95.

5. The compressor as described in claim 1, characterized in that, The main housing includes a main body and a connecting part connected to the first end shell, the connecting part being flared toward the first end shell.

6. The compressor as described in claim 5, characterized in that, The connecting portion includes a first sub-segment and a second sub-segment. The first sub-segment connects the main body and the second sub-segment. The first sub-segment is gradually widened toward the first end shell, and the inner side of the second sub-segment is connected to the outer surface of the first end shell.

7. The compressor as described in claim 6, characterized in that, The main body is provided with a uniform inner diameter along the axial direction. The inner radius of the main body is the inner radius R7 of the end of the main housing near the end of the second winding. The maximum inner radius of the second sub-segment is the inner radius R5 of the end of the main housing connected to the first end shell. The ratio of R5 to R7 is not less than 1.05 and not greater than 1.

2.

8. The compressor as claimed in any one of claims 1 to 7, characterized in that, The motor also includes a rotor, which passes through the stator axially. The pump assembly includes a muffler and a crankshaft connected to the rotor. The compression component and the muffler are sleeved around the crankshaft. The muffler is located on the side of the compression component facing the rotor and has an exhaust port.

9. The compressor as claimed in claim 8, 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, and 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.

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

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