Compressor and refrigeration apparatus

Abstract

The application 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 a shell opening end and a first end surface, the distance H2 between a second end surface and a mounting plane, the distance H3 between an inner end surface and the shell opening end, the inner diameter R5 of a first end shell connecting end of a main shell, the inner diameter R7 of another end, the inner diameter R6 of the first end shell, the height h1 of a first winding end portion, the outer diameter R1, the inner diameter R2, the height h2 of a second winding end portion, the outer diameter R3 and the inner diameter R4 satisfy the following conditions: h1 < H1, H2 < H3, R5 < R6, R6 < R7, R1 < R2, R3 < R4 and R2 < R3. The application can reduce the exhaust oscillation noise of the compressor.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of compressors, in particular to a compressor and a refrigeration equipment. BACKGROUND

[0002] In recent years, driven by the demand of portable terminal market, the design of compressors towards low height and small volume has become a major trend. However, the miniaturization of compressors leads to the decrease of the cavity volume inside the compressor, and the axial oscillation impact of high-pressure refrigerant when discharging through the top causes vibration noise and increases the oil discharge amount of the compressor. SUMMARY

[0003] The main purpose of the present application is to provide a compressor and a refrigeration equipment, which can reduce the exhaust oscillation noise and reduce the oil discharge amount under the premise of small volume of the compressor.

[0004] To achieve the above-mentioned purpose, the compressor provided by the present application comprises:

[0005] A shell comprising a main shell and a first end shell arranged at one end of the main shell;

[0006] A motor arranged in the shell, the motor comprising a stator, the stator comprising a stator core and a wire-wound winding, the wire-wound winding having a first winding end portion and a second winding end portion arranged at two ends of the stator core respectively, the first end shell having an inner end face arranged opposite to the first winding end portion, and a shell mouth end arranged around the side of the first winding end portion, the stator core having a first end face facing the inner end face and a second end face facing away from the inner end face; and

[0007] A pump body assembly arranged in the shell, the pump body assembly comprising a compression component, the compression component being located on the side of the second winding end portion away from the stator core, the compression component having a mounting plane facing the second end face;

[0008] In the axial direction of the stator, the distance between the shell mouth 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 mouth end is defined as H3, the inner radius of the end connected with the first end shell of the main shell is defined as R5, the inner radius of the first end shell is defined as R6, the inner radius of the main shell close to the end of the second winding end portion is defined as R7, the height of the first winding end portion is defined as h1, the outer radius of the first winding end portion is defined as R1, the inner radius of the first winding end portion is defined as R2, the height of the second winding end portion is defined as h2, the outer radius of the second winding end portion is defined as R3, and the inner radius of the second winding end portion is defined as R4, which satisfy:

[0009] .

[0010] In one embodiment, the first winding end and the second winding end satisfy the following:

[0011] [h1*(R1 2 -R2 2 )] and [h2*(R3 2 -R4 2 The ratio of )] is not less than 1.2.

[0012] 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:

[0013] 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.

[0014] 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.

[0015] 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.

[0016] 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.

[0017] 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.

[0018] 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.

[0019] 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.

[0020] In one embodiment, the motor further includes a rotor that passes through the stator axially;

[0021] The pump body assembly comprises a muffler and a crankshaft connected to the rotor, the compression component and the muffler are arranged on the periphery of the crankshaft, the muffler is located on the side of the compression component facing the rotor, and the muffler is provided with an exhaust hole.

[0022] In an embodiment, the compressor is configured as a vertical rotary compressor, the first end shell is configured as an upper end shell of the shell, and the compression component comprises a first bearing, a cylinder and a second bearing arranged in sequence from the side close to the rotor to the direction away from the first end shell.

[0023] The application further provides a refrigeration device comprising the compressor.

[0024] The technical scheme of the application 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 circle radius of the end of the main shell connected to the first end shell as R5, the inner circle radius of the first end shell as R6, the inner circle radius of the end of the main shell close to the second winding as R7, the height of the first winding end portion as h1, the outer circle radius of the first winding end portion as R1, the inner circle radius of the first winding end portion as R2, the height of the second winding end portion as h2, the outer circle radius of the second winding end portion as R3, and the inner circle radius of the second winding end portion as R4, and through calculating the actual volume of the upper cavity exhaust space, through calculating the volume of the first winding end portion, through calculating the actual volume of the lower cavity exhaust space, through calculating the volume of the second winding end portion, the ratio of the difference between the actual volume of the upper cavity exhaust space and the volume of the first winding end portion to the difference between the actual volume of the lower cavity exhaust space and the volume of the second winding end portion is between 2.0 and 2.5, 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. When high-pressure gas is discharged from the pump body assembly, it first enters the lower cavity exhaust space, the smaller exhaust volume of the lower cavity exhaust space can quickly establish an initial exhaust pressure, avoiding the diffusive turbulence of the gas flow under low pressure, and then the gas flow enters the upper cavity exhaust space with a larger volume, reducing the flow velocity through space expansion, reducing the oscillation impact of high-speed gas flow on the shell and the first winding end portion, avoiding the gas flow jamming phenomenon caused by narrow space, reducing pressure fluctuation and pulsating noise; and the larger actual exhaust volume of the upper cavity exhaust space can reserve sufficient space, so that the flow velocity gradually decreases during the ascending process, the lubricating oil mixed in the gaseous refrigerant settles due to gravity, reducing the amount of oil entering the exhaust pipe with the gas flow, thereby reducing the oil discharge amount. BRIEF DESCRIPTION OF DRAWINGS

[0025] In order to make the technical solutions in the embodiments of the present application or the prior art clearer, the accompanying drawings needed in the embodiments or prior art description will be briefly introduced. Obviously, the accompanying drawings in the following description only show some embodiments of the present application, and for those skilled in the art, other drawings can be obtained from the structures shown in the drawings without any creative effort.

[0026] Figure 1 Structure schematic diagram of an embodiment of the compressor provided by the present application;

[0027] Figure 2 Structure schematic diagram of an embodiment of the compressor provided by the present application; Figure 1 Structure schematic diagram of an embodiment of the compressor provided by the present application;

[0028] Figure 3 Structure schematic diagram of an embodiment of the compressor provided by the present application; Figure 1 Structure schematic diagram of an embodiment of the compressor provided by the present application;

[0029] Figure 4 Structure schematic diagram of an embodiment of the compressor provided by the present application; Figure 1 Structure schematic diagram of an embodiment of the compressor provided by the present application;

[0030] Figure 5 Structure schematic diagram of an embodiment of the compressor provided by the present application; Figure 1 Structure schematic diagram of an embodiment of the compressor provided by the present application.

[0031] Explanation of the reference signs:

[0032] 100, compressor; 10, shell; 1011, first cavity; 1012, second cavity; 102, exhaust end; 11, main shell; 111, main body part; 112, connecting part; 1121, first sub-section; 1122, second sub-section; 12, first end shell; 121, inner end face; 122, shell mouth end; 20, pump body assembly; 21, compression component; 21a, mounting plane; 211, first bearing; 212, cylinder; 213, second bearing; 22, muffler; 221, exhaust hole; 23, crankshaft; 30, motor; 31, stator; 311, stator core; 3111, first end face; 3112, second end face; 312, wire-wound winding; 3121, first winding end part; 3122, second winding end part; 32, rotor; 40, liquid accumulator.

[0033] The implementation, functional features and advantages of the present application will be further described with reference to the embodiments and the accompanying drawings. DETAILED DESCRIPTION

[0034] With reference to the drawings of the embodiments of the present application, the technical solutions in the embodiments of the present application will be clearly and completely described. Obviously, the described embodiments are only a part of the embodiments of the present application, rather than all the embodiments of the present application. Based on the embodiments of the present application, all the other embodiments obtained by a person of ordinary skill in the art without creative work fall within the scope of the present application.

[0035] It should be noted that if the embodiments of the present application involve directional indications (such as up, down, left, right, front, back, etc.), the directional indications are only used to explain the relative positional relationship, movement condition, etc. between components in a certain posture, and if the certain posture changes, the directional indications also change accordingly.

[0036] In addition, if the embodiments of the present application involve descriptions of “first”, “second”, etc., the descriptions of “first”, “second”, etc. are only for description purposes, and cannot be understood as indicating or implying the relative importance or implicitly indicating the number of the indicated technical features. Therefore, the features limited by “first”, “second” can explicitly or implicitly include at least one of the features. In addition, “and / or” or “and / or” appearing throughout the text means that the three parallel solutions are included, for example, “A and / or B” includes A solution, or B solution, or A and B solutions are satisfied at the same time. In addition, the technical solutions of each embodiment can be combined with each other, but it must be based on the realization of a person of ordinary skill in the art, and when the combination of technical solutions appears contradictory or unachievable, it should be considered that the combination of technical solutions does not exist, and is not within the scope of protection claimed by the present application.

[0037] In recent years, driven by the demand of the portable terminal market, the design of compressors towards low height and small size has become a major trend. However, the miniaturization of the compressor leads to the decrease of the cavity volume inside the compressor, and the axial oscillation impact of the high-pressure refrigerant when it is discharged through the top, which causes vibration noise and increases the oil discharge of the compressor.

[0038] The present application provides a kind of compressor 100.

[0039] Please refer to Figures 1 to 5In an embodiment of the present application, the compressor 100 comprises a housing 10, a motor 30 and a pump body assembly 20; the housing 10 comprises a main housing 11 and a first end housing 12 arranged at one end of the main housing 11; the motor 30 is arranged in the housing 10, the motor 30 comprises a stator 31, the stator 31 comprises a stator core 311 and a wire-wound winding 312, the wire-wound winding 312 has a first winding end 3121 and a second winding end 3122 arranged at two ends of the stator core 311 respectively, the first end housing 12 has an inner end face 121 arranged opposite to the first winding end 3121 and a housing opening end 122 arranged around 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 facing away from the inner end face 121, the pump body assembly 20 is arranged in the housing 10, the pump body assembly 20 comprises a compression component 21, the compression component 21 is located on a side of the second winding end 3122 away from the stator core 311, and the compression component 21 has a mounting plane 21a facing the second end face 3112;

[0040] In the axial direction of the stator 31, the distance between the housing opening end 122 and the first end face 3111 is H1, the distance between the second end face 3112 and the mounting plane 21a is H2, the distance between the inner end face 121 and the housing opening end 122 is H3, the inner radius of the end connected with the first end housing 12 of the main housing 11 is R5, the inner radius of the first end housing 12 is R6, the inner radius of the main housing 11 close to the end of 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, which satisfy:

[0041] .

[0042] In the present application, the compressor 100 can be a vertical compressor 100 or a horizontal compressor 100. The compressor 100 comprises a housing 10 and a motor 30 and a pump body assembly 20 arranged in the housing 10. The housing 10 can further be provided with a liquid accumulator 40 in communication with a suction pipe of the compressor 100. The housing 10 is used to support and protect the internal components, and the housing 10 also cooperates with the internal components to define a passage for the high-pressure refrigerant to flow through. The housing 10 comprises a main housing 11 with two open ends, and a first end housing 12 and a second end housing arranged at the two open ends of the main housing 11 respectively. The first end housing 12 and the second end housing can be welded to the main housing 11 respectively to ensure that the entire housing 10 can withstand high pressure. The first end housing 12 is used to connect an exhaust pipe. The motor 30 and the pump body assembly 20 are arranged in 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, and finally discharge the high-pressure refrigerant from the exhaust pipe of the first end housing 12 to the external refrigerant circulation system.

[0043] As Figure 1As shown, the vertical rotary compressor 100 is taken as an example. The shell 10 is generally in a cylindrical shape extending vertically, and the first end shell 12 and the second end shell are respectively fixed to the axial ends of the main shell 11. Among them, the first end shell 12 is the upper end shell of the shell 10, and the second end shell is the lower end shell of the shell 10. The first end shell 12 has an exhaust end 102 for connecting the exhaust pipe of the compressor 100. The motor 30 includes a rotor 32 and a stator 31. The stator 31 is fixed in the main shell 11 and is sleeved on the outer periphery of the rotor 32. The rotor 32 is sleeved on the outer periphery of the crankshaft 23 of the pump body assembly 20. The rotor 32 includes a rotor 32 core and a magnetic steel arranged on the rotor 32 core. The stator 31 includes a stator core 311 and a wire-wound winding 312 arranged on the stator core 311. The wire-wound winding 312 is used to connect with the power supply circuit. When the motor 30 works, the induction magnetic field is generated under the cooperation of the stator 31 and the rotor 32, so that the rotor 32 can rotate relative to the stator 31, and then the crankshaft 23 is driven to rotate by the rotor 32. The wire-wound winding 312 includes a first winding end 3121 and a second winding end 3122 located at the two ends of the stator core 311 respectively. Among them, the first winding end 3121 (also known as the positive side of the wire-wound winding 312 end) is located at the upper end of the stator core 311, and the second winding end 3122 (also known as the negative side of the wire-wound winding 312 end) is located at the lower end of the stator core 311. The first winding end 3121 is arranged close to the first end shell 12 and forms a certain gap between the first winding end 3121 and the top wall of the first end shell 12. The pump body assembly 20 includes a crankshaft 23 connected with the rotor 32, and a compression component 21 and a muffler 22 sleeved on the outer periphery of the crankshaft 23. The compression component 21 has a suction passage for the refrigerant to enter and an exhaust passage for the high-pressure refrigerant to discharge. The muffler 22 has a muffling cavity communicating with the exhaust passage and an exhaust hole 221 communicating with the muffling cavity.

[0044] The refrigerant in the external circulation system enters the compression component 21 through the suction passage, and then the compression component 21 performs compression work on the refrigerant. The generated high-pressure refrigerant is discharged from the exhaust passage into the muffling cavity, and then is discharged from the exhaust hole 221 into the gap between the shell 10 and the second winding end 3122 after noise reduction in the muffling cavity. The high-pressure refrigerant successively passes through the gap between the shell 10 and the second winding end 3122, the gap between the shell 10, the stator core 311 and the rotor 32, and the gap between the shell 10 and the first winding end 3121, and is then discharged from the exhaust end 102 on the first end shell 12 to the external refrigerant circulation system.

[0045] Of course, in other embodiments, the compressor 100 can also be a multi-cylinder 212 rotary compressor 100. Correspondingly, the cylinder 212 is provided with at least two cylinders 212, and a partition plate is arranged between the adjacent two cylinders 212.

[0046] It can be understood that the space between the stator 31 and the pump body assembly 20 is approximately the lower cavity exhaust space inside the compressor 100, which can be defined as the second cavity 1012, and the space between the stator 31 and the first end shell 12 is approximately the upper cavity exhaust space inside the compressor 100, which can be defined as the first cavity 1011. In the inner cavity of the compressor 100, the flow path of the exhaust is the exhaust hole 221 of the muffler 22 to the exhaust end 102 of the first end shell 12. When the pump body assembly 20 is exhausting, the high-pressure gaseous refrigerant will first pass through the second cavity 1012, then pass through the gap between the stator 31 and the shell 10 into the first cavity 1011, then from the first cavity 1011 into the exhaust end 102, and finally out of the compressor 100.

[0047] The connecting point where the compression component 21 is connected to the main shell 11 defines a mounting plane 21a, for example, the compression component 21 of the pump body assembly 20 is generally welded in the main shell 11, and the inner peripheral wall of the main shell 11 is generally provided with a plurality of welding points at intervals, and the plane defined by the plurality of welding points is the mounting plane 21a of the compression component 21. The shell opening end 122 around the first winding end portion 3121 can be the opening end of the first end shell 12 towards the main shell 11, and the first winding end portion 3121 can be partially located in the first end shell or entirely located in the main shell 11, which is not limited here.

[0048] It can be understood 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, and the volume available for refrigerant flow is further reduced by the volume of the first winding end portion 3121 and the volume of the rotor 32 in the first cavity 1011. 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, and the actual volume available for refrigerant flow needs to be reduced by the volume of the second winding end portion 3122 and the volume of the rotor 32 in the second cavity 1012. In the case where the volume of the rotor 32 is constant, the size of the first winding end portion 3121 and the volume of the first cavity 1011 determine the volume of the first cavity 1011 available for refrigerant flow, and the size of the second winding end portion 3122 and the volume of the second cavity 1012 determine the volume of the second cavity 1012 available for refrigerant flow.

[0049] The actual volume of the first cavity 1011 can be calculated by the formula where H1 is the distance between the shell opening end 122 and the first end face 3111, H3 is the distance between the inner end face 121 and the shell opening end 122, the sum of the two is the height of the first cavity 1011, R5 is the inner circular radius of the connecting end of the main shell 11 and the first end shell 12, V1 = π(R6 - R5)H1 V2 = π(R7 - R6)H2

[0050] The volume of the first winding end portion 3121 in the first cavity 1011 can be calculated by the formula wherein R1 is the outer radius of the first winding end portion 3121, R2 is the inner radius of the first winding end portion 3121, the difference between the squares of R1 and R2 multiplied by π, and the height h1 of the first winding end portion 3121, i.e. the volume of the first winding end portion 3121 in the first cavity 1011.

[0051] The volume of the second cavity 1012 can be calculated by the formula wherein H2 is the distance between the second end face 3112 and the mounting plane 21a, i.e. 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 end portion 3122.

[0052] The volume of the second winding end portion 3122 in the second cavity 1012 can be calculated by the formula wherein R3 is the outer radius of the second winding end portion 3122, R4 is the inner radius of the second winding end portion 3122, the difference between the squares of R3 and R4 multiplied by π, and the height h2 of the second winding end portion 3122, i.e. the volume of the second winding end portion 3122 in the second cavity 1012.

[0053] In the case of a constant rotor volume, the ratio of the difference between the actual volume of the first cavity 1011 and the volume of the first winding end portion 3121, and the difference between the actual volume of the second cavity 1012 and the volume of the second winding end portion 3122, is between 2.0 and 2.5, i.e. satisfies .

[0054] In this way, the exhaust volume of the first cavity 1011 is smaller than that of the second cavity 1012, forming a larger buffer space. When high-pressure gas is discharged from the pump body, it first enters the second cavity 1012, and the smaller volume of the second cavity 1012 can quickly establish an initial exhaust pressure, avoiding the diffusive turbulence of the gas flow at low pressure; then the gas flow enters the first cavity 1011 with a larger volume, reducing the flow rate through space expansion, reducing the impact of high-speed gas flow on the housing 10 and the first winding end portion 3121, and avoiding the phenomenon of gas flow congestion caused by narrow space, thereby reducing pressure fluctuations and pulsating noise.

[0055] The first cavity 1011 serves as a main exhaust passage, and its large volume can reserve sufficient space to gradually reduce the flow rate of the gas flow during the rising process, and the mixed lubricating oil in the gaseous refrigerant can be settled by gravity to reduce the amount of oil entering the exhaust pipe with the gas flow, thereby reducing the oil discharge amount.

[0056] By way of example, the ratio of the difference between the actual volume of the first cavity 1011 and the volume of the first winding end portion 3121 to the difference between the actual volume of the second cavity 1012 and the volume of the second winding end portion 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].

[0057] The technical solution of the present application defines the distance between the shell opening 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 opening end 122 as H3, the inner circle radius of the main shell 11 at the end connected to the first end shell 12 as R5, the inner circle radius of the first end shell 12 as R6, the inner circle radius of the main shell 11 near the end of the second winding end portion 3122 as R7, the height of the first winding end portion 3121 as h1, the outer circle radius of the first winding end portion 3121 as R1, the inner circle radius of the first winding end portion 3121 as R2, the height of the second winding end portion 3122 as h2, the outer circle radius of the second winding end portion 3122 as R3, and the inner circle radius of the second winding end portion 3122 as R4, and through calculating the actual volume of the upper cavity exhaust space, through calculating the volume of the first winding end portion 3121, through calculating the actual volume of the lower cavity exhaust space, through calculating the volume of the second winding end portion 3122, the ratio of the difference between the actual volume of the upper cavity exhaust space and the volume of the first winding end portion 3121 to the difference between the actual volume of the lower cavity exhaust space and the volume of the second winding end portion 3122 is between 2.0 and 2.5, 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. When high-pressure gas is discharged from the pump body assembly 20, it first enters the lower cavity exhaust space, the smaller exhaust volume of the lower cavity exhaust space can quickly establish an initial exhaust pressure, avoiding the diffusive turbulence of the gas flow under low pressure, and then the gas flow enters the upper cavity exhaust space with larger volume, reducing the flow rate through space expansion, reducing the oscillation impact of high-speed gas flow on the shell 10 and the first winding end portion 3121, avoiding the gas flow jamming phenomenon caused by narrow space, reducing pressure fluctuation and pulsating noise; and the large actual exhaust volume of the upper cavity exhaust space can reserve sufficient space to gradually reduce the flow rate of the gas flow during the rising process, and the mixed lubricating oil in the gaseous refrigerant can be settled by gravity to reduce the amount of oil entering the exhaust pipe with the gas flow, thereby reducing the oil discharge amount.

[0058] Optionally, the first winding end 3121 and the second winding end 3122 satisfy the following:

[0059] [h1*(R1 2 -R2 2 )] and [h2*(R3 2 -R4 2 The ratio of )] is not less than 1.2.

[0060] 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.

[0061] 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.

[0062] 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:

[0063] 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.

[0064] And / or, the ratio of the axial height h2 of the second winding end portion 3122 to the axial height H2 of the second cavity 1012 is not less than 0.6 and not more than 0.9.

[0065] 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.

[0066] It can be understood that when the ratio of h1 to H4 is not less than 0.4, the height of the first winding end portion 3121 is sufficient to accommodate sufficient winding turns or thicker wires, thereby improving electromagnetic induction strength, reducing copper loss, and supporting efficient electromagnetic conversion. If the ratio is too small, the insufficient volume of the wire package will result in a decrease in electromagnetic efficiency. When the ratio of h1 to H4 is not more than 0.6, at least 40% of the space in the first cavity 1011 is reserved as an exhaust passage. In the case where the ratio of the difference between the actual volume of the first cavity 1011 and the volume of the first winding end portion 3121 to the difference between the actual volume of the second cavity 1012 and the volume of the second winding end portion 3122 is between 2.0 and 2.5, sufficient buffer space is provided for high-pressure exhaust, so that the flow rate of the gas flow entering the first cavity 1011 is reduced, the impact of high-speed gas flow on the shell and the first winding end portion 3121 is reduced, thereby reducing pulsating noise, and the lower flow rate can cause the lubricating oil to settle by gravity, reducing the amount of oil carried out with the exhaust.

[0067] Exemplarily, the ratio of h1 to H4 can be 0.4, 0.45, 0.5, 0.55, 0.6, and any point value within the interval [0.4, 0.6].

[0068] It can be understood that, under the condition that the ratio of h2 to H2 is not less than 0.6, the height of the second winding end portion 3122 can be more than 60% of the height of the second cavity 1012, and the wire package structure is more compact. Under the condition that the ratio of the difference between the actual volume of the first cavity 1011 and the volume of the first winding end portion 3121, and the difference between the actual volume of the second cavity 1012 and the volume of the second winding end portion 3122 is between 2.0 and 2.5, the airflow can be prevented from diffusing in the small-volume second cavity 1012. When the pump body assembly 20 is exhausted, the exhaust pressure can be quickly established in the second cavity 1012, the airflow diversion resistance is reduced, and the exhaust efficiency is improved. Under the condition that h2 / H2≤0.9, the height of the second winding end portion 3122 is prevented from being too large, which forces the height H2 of the second cavity 1012 to increase, resulting in an increase in the overall size of the compressor 100. By compressing the redundant space of the second winding end portion 3122 and the second cavity 1012, the axial size of the second cavity 1012 is minimized under the premise of meeting the electromagnetic efficiency, so that the compressor 100 is smaller in volume, which is beneficial to miniaturization.

[0069] Exemplarily, the ratio of h2 to H2 can be 0.6, 0.7, 0.8, 0.9, and any point value within the interval [0.6, 0.9].

[0070] The above designs for the first winding end portion 3121 and the second winding end portion 3122 can meet any one of them, or both at the same time, which is not specifically limited here.

[0071] As shown in Figure 3 , Figure 4 Optionally, the ratio of the outer radius R1 of the first winding end portion 3121 to the inner radius R6 of the first end shell 12 is not less than 0.8 and not greater than 0.95.

[0072] And / or, the ratio of the outer radius R2 of the second winding end portion 3122 to the inner radius R7 of the main shell 11 close to one end of the second winding end portion 3122 is not less than 0.8 and not greater than 0.95.

[0073] It can be understood that a first passage gap for the circulation of refrigerant is formed between the outer circumferential surface of the first winding end portion 3121 and the inner circumferential surface of the first end shell 12. If the ratio of R1 to R6 is too small, the first passage gap between the first winding end portion 3121 and the inner diameter R6 of the first end shell 12 is too wide, and after the high-pressure exhaust gas enters the first cavity 1011, a diffusion flow field is easily formed, resulting in uneven flow velocity distribution, increased local turbulent flow, and further causing airflow impact noise and secondary entrainment of lubricating oil mist. If the ratio of R1 to R6 is too large, the gap is too narrow, which can cause the airflow velocity to rise sharply, and the high-speed airflow can easily wrap 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, the first cavity 1011 can form a "smooth flow channel" on the basis of a large volume, the airflow flows uniformly along the line outside the circumference, reduces local vortex flow, and can cooperate with the ratio of the height H1 of the first cavity 1011 to the height h1 of the first winding end portion 3121 0.4≤h1 / H1≤0.6 to realize the dual optimization of low flow velocity and stable flow field.

[0074] Exemplarily, the ratio of R1 to R6 can be 0.8, 0.85, 0.9, 0.95, and any point value within the interval [0.8, 0.95].

[0075] The outer circumferential surface of the second winding end portion 3122 and the inner circumferential surface of the main shell 11 form a second passage gap for the circulation of refrigerant. By setting the ratio of the outer radius R2 of the second winding end portion 3122 to the inner radius R7 of the main shell 11 near the end of the second winding end portion 3122 to be between 0.8 and 0.95, the second passage gap can be ensured to be relatively narrow, and the ratio of the difference between the actual volume of the first cavity 1011 and the volume of the first winding end portion 3121 to the difference between the actual volume of the second cavity 1012 and the volume of the second winding end portion 3122 can be between 2.0 and 2.5, so that the airflow quickly passes through the second cavity 1012 and establishes a stable pressure, reducing the diffusion resistance of the airflow caused by a too wide gap, or the pressure loss caused by a too narrow gap.

[0076] Exemplarily, the ratio of R3 to R5 can be 0.8, 0.85, 0.9, 0.95, and any point value within the interval [0.8, 0.95].

[0077] When the above two conditions are met, i.e. R1 / R6 and R3 / R5 are both controlled at 0.8-0.95, 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 vortex when the airflow is diverted due to the too large difference between the upper and lower gaps.

[0078] As shown in Figure 1 , Figure 2 In an embodiment, the main housing 11 includes a main body part 111 and a connecting part 112 connected with the first end housing 12, and the connecting part 112 is flared towards the first end housing 12.

[0079] It can be understood that the volume of the first cavity 1011 is determined by the axial height of the first cavity 1011 and the radial width of the first cavity 1011. When the connecting part 112 is flared towards the first end housing 12, the main housing 11 is non-equal-diameter, and the inner diameter of the main housing 11 on the side of the connecting part 112 is larger than the inner diameter of the main housing 11 away from the first end housing 12. In this way, the width of the first cavity 1011 inside the connecting part 112 can be increased, and under the condition that the volume of the first cavity 1011 remains unchanged, the overall height of the first cavity 1011 can be reduced, thereby reducing the overall height of the compressor 100, thereby facilitating the miniaturization of the compressor 100. Moreover, the flared connecting part 112 can increase the distance between the inner side surface of the main housing 11 and the first winding end part 3121, and when the connecting part 112 is welded with the first end housing 12, it can prevent the first winding end part 3121 from being damaged by high-temperature welding.

[0080] As shown in Figure 1 , Figure 2 In an embodiment, the connecting part 112 includes a first sub-section 1121 and a second sub-section 1122, the first sub-section 1121 connects the main body part 111 and the second sub-section 1122, the first sub-section 1121 is gradually expanded towards the first end housing 12, and the inner side surface of the second sub-section 1122 is connected with the outer surface of the first end housing 12.

[0081] 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.

[0082] 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.

[0083] 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.

[0084] 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.

[0085] like Figure 1 , Figure 3 As shown, the motor 30 also includes a rotor 32, which passes through the stator 31 axially;

[0086] The pump body assembly 20 comprises a muffler 22 and a crankshaft 23 connected with the rotor 32, the compression component 21 and the muffler 22 are sleeved on the periphery of the crankshaft 23, the muffler 22 is located on the side of the compression component 21 facing the rotor 32, and the muffler 22 is provided with an exhaust hole 221.

[0087] The stator 31 is fixed in the main shell 11 and sleeved on the periphery of the rotor, the rotor is sleeved on the periphery of the crankshaft 23 of the pump body assembly 20, and the rotor comprises a rotor core and a magnetic steel arranged on the rotor core. When the motor works, an induced magnetic field is generated under the cooperation of the stator 31 and the rotor, so that the rotor can rotate relative to the stator 31, and then the rotor drives the crankshaft 23 to rotate.

[0088] The pump body assembly 20 comprises the crankshaft 23 connected with the rotor, and the compression component 21 and the muffler 22 sleeved on the periphery of the crankshaft 23. The compression component 21 is provided with a suction passage for the refrigerant to enter and an exhaust passage for high-pressure refrigerant to discharge, and the muffler 22 is provided with a muffling cavity in communication with the exhaust passage and an exhaust hole in communication with the muffling cavity. After the refrigerant in the external circulation system enters the compression component 21 through the suction passage, the compression component 21 performs compression work on the refrigerant, and the generated high-pressure refrigerant is discharged from the exhaust passage into the muffling cavity, and then discharged into the second cavity 1012 through the exhaust hole after noise reduction in the muffling cavity.

[0089] With the 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 vane, the cylinder 212 has a working chamber and a vane groove in communication with the working chamber, the piston is eccentrically rotatable arranged in the working chamber of the cylinder 212, the vane is radially slidably arranged in the vane groove, and one end of the vane is in abutment or hinged with the piston. The crankshaft 23 has an eccentric portion, the piston is sleeved on the periphery of the eccentric portion of the crankshaft 23, and the piston can drive the piston to rotate eccentrically along the inner surface of the cylinder 212 by rotating the crankshaft 23, so as to compress the gas in the working chamber to form high-pressure refrigerant. The first bearing 211 and the second bearing 213 are respectively arranged on opposite sides of the cylinder 212 to seal the two ends of the cylinder 212 and support the crankshaft 23. Among them, the first bearing 211 is located on the side of the cylinder 212 close 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 an upper bearing (i.e. a main bearing), and the second bearing 213 is a lower bearing (i.e. a secondary bearing). In order to be able to discharge the high-pressure refrigerant in the compression component 21, the first bearing 211 is also provided with an air hole for communicating the working chamber with the sound attenuation chamber, the high-pressure refrigerant enters the sound attenuation chamber through the air hole of the first bearing 211, and then is discharged to the cavity of the shell through the exhaust hole 221, and then passes through the gap between the shell and the motor 30 and the internal gap of the motor 30, and is discharged to 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, and correspondingly, at least two cylinders 212 are arranged, and a partition plate is arranged between the adjacent two cylinders 212.

[0090] As shown in Figure 1 , Figure 3 , Figure 4 , 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 shell 10, and the compression component 21 includes the first bearing 211, the cylinder 212 and the second bearing 213 arranged in sequence from the side close to the rotor to the direction away from the first end shell 12. The specific structure and working process of the vertical rotary compressor 100 have been introduced in the foregoing, 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 end shell or the right end shell of the shell.

[0091] The application further provides a refrigeration equipment, which comprises the compressor 100, and the specific structure of the compressor 100 is referred to the above-mentioned embodiments. Since all the technical solutions of the above-mentioned embodiments are adopted in the refrigeration equipment, all the beneficial effects brought by the technical solutions of the above-mentioned embodiments are at least possessed by the refrigeration equipment, and thus will not be repeated here. The refrigeration equipment includes but is not limited to a refrigerator, an integrated air conditioner, a split air conditioner, a ducted air conditioner, a window air conditioner and the like.

[0092] The above-mentioned is only an exemplary embodiment of the application, and does not limit the protection scope of the application. Any equivalent structural transformation, direct / indirect application in other related technical fields or the like made by referring to the content of the specification and drawings of the application within the technical concept of the application is included in the protection scope of the application.

Claims

1. A compressor characterized by, The application relates to a motor-pump assembly. The motor-pump assembly comprises a housing, a motor and a pump body assembly. The housing comprises a main housing and a first end housing arranged at one end of the main housing. The motor is arranged in the housing and comprises a stator. The stator comprises a stator core and a wire-wound winding. 。 2. The compressor of claim 1, wherein, The wire-wound winding has a first winding end and a second winding end arranged at two ends of the stator core. the ratio of [h1*(R1 2 -R2 2 )] to [h2*(R3 2 -R4 2 )] is not less than 1.

2.

3. The compressor of claim 1, wherein, The first end housing has an inner end surface opposite to the first winding end and a housing opening end arranged around the first winding end. The stator core has a first end surface facing the inner end surface and a second end surface away from the inner end surface. The pump body assembly is arranged in the housing and comprises a compression component.

4. The compressor of claim 1, wherein, The compression component is arranged at a side of the second winding end away from the stator core and has a mounting surface facing the second end surface. In the axial direction of the stator, the distance between the housing opening end and the first end surface is H1, the distance between the second end surface and the mounting surface is H2, the distance between the inner end surface and the housing opening end is H3, the inner radius of the main housing at the connecting end of the first end housing is R5, the inner radius of the first end housing is R6, the inner radius of the main housing close to the second winding end is R7, the height of the first winding end is h1, the outer radius of the first winding end is R1, the inner radius of the first winding end is R2, the height of the second winding end is h2, the outer radius of the second winding end is R3, and the inner radius of the second winding end is R4.

5. The compressor of claim 1, wherein, The ratio of the axial height h1 of the first winding end to the axial height H4 of the first cavity is not less than 0.4 and not more than 0.

6.

6. The compressor of claim 5, wherein, The ratio of the axial height h2 of the second winding end to the axial height H2 of the second cavity is not less than 0.6 and not more than 0.

9. The ratio of the outer radius R1 of the first winding end to the inner radius R6 of the first end housing is not less than 0.8 and not more than 0.

95. The ratio of the outer radius R2 of the second winding end to the inner radius R7 of the main housing close to the second winding end is not less than 0.8 and not more than 0.

95. The main housing comprises a main body and a connecting part connected with the first end housing. The connecting part is arranged in a flared manner towards the first end housing. The connecting part comprises a first sub-section and a second sub-section. The first sub-section is connected with the main body and the second sub-section. The first sub-section is arranged in a gradually expanding manner towards the first end housing. The inner side surface of the second sub-section is connected with the outer surface of the first end housing.

7. The compressor of claim 6, wherein, The main body part is of equal inner diameter along the axial direction, the inner circle radius of the main body part is the inner circle radius R7 of the main shell near one end of the second winding end part, the maximum inner circle radius of the second sub-section is the inner circle radius R5 of the main shell connected with one end of the first end shell, the ratio of R5 to R7 is not less than 1.05 and not more than 1.

2.

8. The compressor of any one of claims 1 to 7, wherein, The motor further comprises a rotor, which is arranged in the stator along the axial direction; The pump body assembly comprises a muffler and a crankshaft, the crankshaft is connected with the rotor, the compression component and the muffler are arranged on the periphery of the crankshaft, the muffler is located on the side of the compression component facing the rotor, and the muffler is provided with exhaust holes.

9. The compressor of claim 8, wherein, The compressor is configured as a vertical rotary compressor, the first end shell is configured as an upper end shell of the shell, and the compression component comprises a first bearing, a cylinder and a second bearing arranged in sequence from the side close to the rotor to the direction away from the first end shell.

10. A refrigeration appliance characterized in that, The compressor comprises the compressor according to any one of claims 1 to 9.

Images