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. A second cavity is formed between the mounting plane of the pump body assembly and the second end face. The total opening area of the exhaust hole is defined as S1. The second cavity has an axial height of H2 and an inner diameter of R7. The second winding end has an axial height of h2, an outer diameter of R3 and an inner diameter of R4. The exhaust capacity of the pump body assembly is P. At least one of the following relationships is satisfied: S1*H2*P / R7*H2*P < 0.5, S1*H2*P / R7*H2*P > 0.5 and S1*H2*P / R7*H2*P = 1. The compressor can reduce exhaust noise.

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 passing through the top exhaust causes vibration noise, resulting in the increase of oil discharge 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 under the premise of ensuring the 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 rotor and a stator arranged at the periphery of the rotor, 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, the first winding end portion being located at one end of the stator core facing the first end shell, and the stator core having a second end face facing away from the first end shell; and

[0007] A pump body assembly arranged in the shell, the pump body assembly comprising a crankshaft connected with the rotor, and a compression component and a muffler sleeved at the periphery of the crankshaft, the muffler being located at one side of the compression component facing the rotor, the muffler having an exhaust hole, and a mounting plane a of the pump body assembly and the second end face forming a second cavity;

[0008] The total opening area of the exhaust hole is defined as S1, the axial height of the second cavity is H2, the inner diameter of the second cavity is R7, the axial height of the second winding end portion is h2, the outer diameter of the second winding end portion is R3, the inner diameter of the second winding end portion is R4, and the exhaust capacity of the pump body assembly is P;

[0009] At least one of the following relationships is satisfied:

[0010] ;

[0011] .

[0012] In an embodiment, a cutout gap is formed between the stator and the housing, and the total area of the cutout gap is S2 in a cross section along the radial direction of the rotor, and S2 is greater than the total opening area S1 of the exhaust hole.

[0013] In an embodiment, the ratio of S1 to S2 satisfies: .

[0014] In an embodiment, the ratio of the total area S2 of the cutout gap formed between the stator and the housing to the inner diameter R5 of the end of the main housing connected to the first end shell is not less than 1.8.

[0015] In an embodiment, the muffler comprises a bottom cover and a muffling cover arranged on one side of the bottom cover, the side of the bottom cover away from the muffling cover is in abutting fit with the compression component, the muffling cover and the compression component surround to form a muffling cavity, the compression component has an exhaust passage in communication with the muffling cavity, the exhaust hole is arranged on the muffling cover and in communication with the muffling cavity, and the exhaust direction of the exhaust hole is tangent to the circumferential direction of the muffling cover.

[0016] In an embodiment, the main housing comprises a main body part and a connecting part, the connecting part comprises a first sub-section and a second sub-section, the first sub-section connects the main body part and the second sub-section, the first sub-section is arranged in a gradually expanding manner towards the first end shell, and the inner side surface of the second sub-section is connected to the outer surface of the first end shell.

[0017] In an embodiment, the main body part is arranged in an equal inner diameter along the axial direction, the inner diameter of the main body part is the inner diameter R7 of the second cavity, the maximum inner diameter of the second sub-section is defined as R5, and the ratio of R5 to R7 is not less than 1.05 and not more than 1.2.

[0018] In an embodiment, the ratio of the outer diameter R1 of the first winding end part to the inner diameter R6 of the first end shell is not less than 0.8 and not more than 0.95, and / or the ratio of the outer diameter R3 of the second winding end part to the inner diameter R7 of the second cavity is not less than 0.8 and not more than 0.95.

[0019] 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 housing, 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, and the muffler is arranged on the side of the first bearing away from the cylinder.

[0020] The application also provides a refrigeration device comprising the compressor as described above.

[0021] The technical scheme of the present application sets the compressor to include a shell, a motor and a pump body assembly, sets the shell to include a main shell and a first end shell, sets the motor to include a rotor and a stator, and sets the two ends of the stator core of the stator to have a first winding end and a second winding end, sets the pump body assembly to include a crankshaft, a compression component and a muffler, and defines a second cavity formed between the mounting plane of the pump body assembly and the second end face of the second winding end, defines the volume of the second cavity as , and the occupied space of the second winding end in the second cavity as , so that ] is the effective buffer escape volume of the second cavity, the ratio of 1000 times the total opening area of the exhaust hole to is between 0 and 0.01, the ratio of the exhaust volume P of the pump body assembly to is between 0.01 and 0.02, and the multi-parameter collaborative control of "exhaust volume-exhaust area-cavity volume" is formed, so that after the high-pressure refrigerant discharged through the exhaust hole enters the second cavity, the pulse energy of the high-pressure refrigerant can be fully dissipated through the buffering effect of the second cavity, the high-temperature refrigerant can flow more gently through the rotor area, the pulse excitation of the rotor surface is more gentle, thereby reducing the axial pulse excitation borne by the rotor shaft system and reducing the vibration noise of the rotor; in the case of ensuring that the pulse energy of the high-pressure refrigerant discharged per unit time by the pump body assembly can be fully dissipated, the exhaust efficiency of the exhaust hole can be ensured, and the volume of the second cavity can also be ensured not to be too large, which is beneficial to the miniaturization of the overall volume of the compressor. BRIEF DESCRIPTION OF DRAWINGS

[0022] In order to more clearly illustrate the technical scheme in the embodiments of the present application or the prior art, the drawings needed to be used in the following embodiment or prior art description will be briefly introduced. Obviously, the drawings in the following description are only some embodiments of the present application, and other drawings can also be obtained according to the structures shown in these drawings without creative labor for those skilled in the art.

[0023] Figure 1 The structure schematic diagram of an embodiment of the compressor provided by the present application is shown in the figure.

[0024] Figure 2 The partial enlarged view of A in Figure 1

[0025] Figure 3 The size relationship schematic diagram of the line winding in Figure 1

[0026] Figure 4 Figure 1 ​​​Schematic diagram of size relationship between first cavity and second cavity;

[0027] Figure 5 For Figure 1 Schematic diagram of structure of muffler;

[0028] Figure 6 For Figure 1 Schematic diagram of angle structure of rotor.

[0029] Brief description of the drawings:

[0030] 100, compressor; 10, shell; 1011, first cavity; 1012, second cavity; 102, exhaust end; 103, edge gap; 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; 22a, exhaust hole; 221, bottom cover; 222, muffling cover; 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; 3122, second winding end; 32, rotor; 40, liquid accumulator.

[0031] 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

[0032] The technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the drawings in the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, rather than all the embodiments of the present application. Based on the embodiments in the present application, all other embodiments obtained by those skilled in the art without creative work fall within the protection scope of the present application.

[0033] 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 position relationship, movement condition, etc. between components in a certain posture, and if the certain posture changes, the directional indications also change accordingly.

[0034] In addition, if the description of "first", "second" and the like is involved in the embodiments of the present application, the description of "first", "second" and the like is only for the purpose of description, and cannot be understood as indicating or implying the relative importance of the indicated technical features or implicitly indicating the number of the indicated technical features. Therefore, the features defined as "first", "second" can be explicitly or implicitly included at least one of the features. In addition, if "and / or" or "and / or" appears throughout the text, it means that the three parallel schemes are included, for example, "A and / or B" includes A scheme, or B scheme, or A and B scheme. In addition, the technical solutions of each embodiment can be combined with each other, but it must be based on the realization of the ordinary skilled in the art, 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 protection scope required by the present application.

[0035] In recent years, driven by the demand of portable terminal market, the compressor is designed to be low height and small size. 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 discharging through the top, which causes vibration noise and increases the oil discharge of the compressor.

[0036] The present application provides a kind of compressor 100.

[0037] Please refer to Figures 1 to 6 In an embodiment of the present application, the compressor 100 includes a housing 10, a motor 30 and a pump body assembly 20; the housing 10 includes a main housing 11 and a first end shell 12 arranged at one end of the main housing 11, the motor 30 is arranged in the housing 10, the motor 30 includes a rotor 32 and a stator 31 arranged on the periphery of the rotor 32, the stator 31 includes 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 both ends of the stator core 311, the first winding end 3121 is located at one end of the stator core 311 towards the first end shell 12, the stator core 311 has a second end face 3112 away from the first end shell 12, the pump body assembly 20 is arranged in the housing 10, 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 periphery of the crankshaft 23, the muffler 22 is located on one side of the compression component 21 towards the rotor 32, the muffler 22 has an exhaust hole 22a, and a second cavity 1012 is formed between the mounting plane 21a of the pump body assembly 20 and the second end face 3112.

[0038] The total opening area of the exhaust hole 22a is defined as S1, the axial height of the second cavity 1012 is H2, the inner diameter of the second cavity 1012 is R7, the axial height of the second winding end 3122 is h2, the outer diameter of the second winding end 3122 is R3, the inner diameter of the second winding end 3122 is R4, and the exhaust volume of the pump body assembly 20 is P;

[0039] At least one of the following relationships is satisfied:

[0040] ;

[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 shell 10, a motor 30 and a pump body assembly 20 arranged in the shell 10. The shell 10 can further be provided with a liquid accumulator 40 in communication with the suction pipe of the compressor 100. The shell 10 is used to support and protect the internal components, and the shell 10 also cooperates with the internal components to define a passage for the circulation of high-pressure refrigerant. The shell 10 comprises a main shell 11 with two open ends, and a first end shell 12 and a second end shell arranged at the two open ends of the main shell 11, respectively. The first end shell 12 and the second end shell can be welded to the main shell 11 to ensure that the entire shell 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 arranged in the shell 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 shell 10, and finally discharge the high-pressure refrigerant from the exhaust pipe of the first end shell 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 in a cylindrical shape extending vertically, and the first end shell 12 and the second end shell are fixed to the axial ends of the main shell 11 respectively. 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 core and a magnetic steel arranged on the rotor 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 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 rotor 32 drives the crankshaft 23 to rotate. 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. The first winding end 3121 (i.e. 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 (i.e. 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 with the top wall of the first end shell 12. The pump body assembly 20 includes the crankshaft 23 connected with the rotor 32, and the compression component 21 and the 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 22a 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 22a into the gap between the shell 10 and the second winding end 3122 after noise reduction by the muffling cavity. The high-pressure refrigerant sequentially 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 into the external refrigerant circulation system.

[0045] 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 slidably arranged in the vane groove along the radial direction of the cylinder 212. 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. By rotating the crankshaft 23, the piston can be driven to rotate eccentrically along the inner surface of the cylinder 212 to compress the gas in the working chamber and 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. 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 discharge the high-pressure refrigerant in the compression component 21, the first bearing 211 is further provided with a vent hole for communicating the working chamber with the sound attenuation chamber. The high-pressure refrigerant enters the sound attenuation chamber through the vent hole of the first bearing 211, and then is discharged to the cavity of the shell through the exhaust hole 22a, 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. Accordingly, at least two cylinders 212 are provided, and a partition is provided between adjacent two cylinders 212.

[0046] The muffler 22 has an exhaust hole 22a. The exhaust hole 22a can be arranged at the top of the muffler 22 to realize top exhaust, or the exhaust hole 22a can be arranged at the side of the muffler 22 to realize side exhaust. The shape of the exhaust hole 22a can be circular, oval, square, crescent or other special-shaped hole. The number of exhaust holes 22a can be designed to be one, two or more according to actual needs.

[0047] In the present application, the exhaust hole 22a provided in the muffler 22 can be one or more, which is not limited herein. When the exhaust hole 22a is provided with multiple exhaust holes, the sum of the opening areas of the multiple exhaust holes 22a is S1, the plane defined by the connecting point of 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 in the main housing 11, the inner circumferential wall of the main housing 11 is generally provided with multiple welding points, and the plane defined by the multiple welding points is the mounting plane 21a of the pump body assembly 20. The second cavity 1012 is formed between the mounting plane 21a and the second end surface 3112, and thus the axial height H2 of the second cavity 1012 is the axial distance between the mounting plane 21a and the second end surface 3112.

[0048] wherein, is the product of the square difference between the outer radius R3 of the second winding end portion 3122 and the inner radius R4 of the second winding end portion 3122 and the height h2 of the second winding end portion 3122, multiplied by the constant π, and is the actual occupied volume of the second winding end portion 3122 in the second cavity 1012, is the product of the square of the inner radius R7 of the second cavity 1012 and the height H2, multiplied by the constant π, and is the volume of the second cavity 1012. Since the exhaust hole 22a communicates with the second cavity 1012, that is, represents the effective buffer and escape volume of the high-pressure refrigerant gas entering the second cavity 1012 after being discharged from the exhaust hole 22a.

[0049] wherein, the ratio of S1 and multiplied by 1000 is not less than 0 and not more than 0.01; that is, . For example, the ratio of S1 and multiplied by 1000 can be 0.002, 0.004, 0.006, 0.008, 0.01, and other arbitrary point values within the interval [0, 0.01]. The ratio of P and is not less than 0.01 and not more than 0.02; that is, . For example, the ratio of P and can be 0.01, 0.04, 0.08, 0.12, 0.16, 0.02, and other arbitrary point values within the interval [0.01, 0.02].

[0050] It can be understood that the greater the total opening area S1 of the exhaust hole 22a, the more pulse energy of the refrigerant injected into the second cavity 1012 per unit time; the greater the effective buffer and escape volume The larger the ratio, the stronger the pulse dissipation capacity of the high-pressure refrigerant. If the ratio of the total opening area of the exhaust hole 22a to the effective buffer dissipation volume of the second cavity 1012 is too large, the pulse energy of the refrigerant injected into the second cavity 1012 per unit time through the exhaust hole 22a is too much, the effective buffer dissipation volume of the second cavity 1012 and the exhaust area of the exhaust hole 22a are not matched, the pulse energy of the refrigerant cannot be effectively dissipated in time, and a part of the pulse energy of the refrigerant will still directly hit the rotor 32, causing a large pulse excitation to the rotor 32, resulting in deterioration of the axial excitation of the rotor 32 and resonance noise or abnormal sound problems. If the ratio of the total opening area of the exhaust hole 22a to the effective buffer dissipation volume of the second cavity 1012 is too small, although the dissipation effect of the pulse energy is good, the exhaust efficiency of the exhaust hole 22a is limited, the exhaust back pressure is increased, and the exhaust efficiency of the compressor 100 is reduced. In addition, the displacement of the pump body assembly 20 and the effective buffer dissipation volume of the second cavity 1012 should also be reasonably designed to ensure that the effective buffer dissipation volume of the second cavity 1012 can effectively dissipate the pulse energy of the high-pressure refrigerant discharged per unit time. If the ratio of the displacement of the pump body assembly 20 to the effective buffer dissipation volume of the second cavity 1012 is too large, it means that the effective buffer dissipation volume of the second cavity 1012 is smaller than the displacement of the pump body assembly 20, so that the pulse energy of the high-pressure refrigerant discharged per unit time by the pump body assembly 20 cannot be completely dissipated by the effective buffer dissipation volume of the second cavity 1012, and a part of the pulse energy of the refrigerant will still directly hit the rotor 32, causing a large pulse excitation to the rotor 32, resulting in deterioration of the axial excitation of the rotor 32 and resonance noise or abnormal sound problems. If the ratio of the pump body assembly 20 to the effective buffer dissipation volume of the second cavity 1012 is too small, it means that the effective buffer dissipation volume of the second cavity 1012 is much larger than the displacement of the pump body assembly 20, although the pulse energy of the high-pressure refrigerant discharged per unit time by the pump body assembly 20 can be fully dissipated, but the volume of the second cavity 1012 is too large, which is not conducive to the miniaturization of the whole compressor 100.

[0051] In the present embodiment, by reasonably restricting the total exhaust area of the exhaust hole 22a, the displacement of the pump body assembly 20, and the effective buffer dissipation volume of the second cavity 1012, etc., the ratio of the total exhaust area of the exhaust hole 22a to the effective buffer dissipation volume of the second cavity 1012 is limited to be within a reasonable range, and the displacement of the pump body assembly 20 and the effective buffer dissipation volume of the second cavity 1012 are limited to be within a reasonable range. , . Thus, the high-pressure refrigerant discharged through the exhaust hole 22a enters the second cavity 1012, and the pulse energy of the high-pressure refrigerant is fully dissipated by the buffering effect of the second cavity 1012, so that the high-temperature refrigerant can flow more smoothly through the rotor area, thereby reducing the pulse excitation of the high-pressure refrigerant to the end surface of the rotor 32, making the pulsating excitation to the surface of the rotor 32 more gentle, reducing the direct blowing impact force of the high-pressure refrigerant flow to the rotor 32, reducing the axial pulsating excitation borne by the rotor 32 shaft, reducing the vibration noise of the rotor 32, and making the rotation of the rotor 32 more stable. Moreover, under the condition of ensuring that the pulse energy of the high-pressure refrigerant discharged by the pump body assembly 20 per unit time can be fully dissipated, the exhaust efficiency of the exhaust hole 22a can be ensured, and the volume of the second cavity 1012 can also be ensured not to be too large, which is beneficial to the miniaturization of the overall volume of the compressor 100. In addition, the second cavity 1012 provides sufficient buffering effect, so that the flow rate gradually decreases during the rising 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 oil discharge amount.

[0052] The technical scheme of the present application sets the compressor 100 to include a shell, a motor 30 and a pump body assembly 20, sets the shell to include a main shell 11 and a first end shell 12, sets the motor 30 to include a rotor 32 and a stator 31, and sets the two ends of the stator core 311 of the stator 31 to have a first winding end 3121 and a second winding end 3122, sets the pump body assembly 20 to include a crankshaft 23, a compression component 21 and a muffler 22, and defines the second cavity 1012 formed between the mounting plane 21a of the pump body assembly 20 and the second end face 3112 of the second winding end 3122, defines the volume of the second cavity as , the occupied space of the second winding end 3122 in the second cavity as , makes ] the effective buffering and dissipation volume of the second cavity 1012, makes the ratio of 1000 times the total opening area of the exhaust hole 22a to between 0 and 0.01, and makes the exhaust volume P of the pump body assembly 20 The ratio of the volume of the second cavity 1012 to the total opening area of the exhaust hole 22a is between 0.01 and 0.02, forming a multi-parameter coordinated control of "displacement-exhaust area-cavity volume", so that the high-pressure refrigerant discharged through the exhaust hole 22a enters the second cavity 1012, and then the buffering effect of the second cavity 1012 can fully dissipate the pulse energy of the high-pressure refrigerant, so that the high-temperature refrigerant can flow more smoothly through the rotor 32 area, reducing the pulse excitation of the high-pressure refrigerant to the end surface of the rotor 32, making the pulsating excitation to the surface of the rotor 32 more gentle, thereby reducing the axial pulsating excitation of the rotor 32 shaft system and reducing the vibration noise of the rotor 32; in the case of ensuring that the pulse energy of the high-pressure refrigerant discharged per unit time by the pump body assembly 20 can be fully dissipated, the exhaust efficiency of the exhaust hole 22a can be ensured, and the volume of the second cavity 1012 can also be ensured not to be too large, which is beneficial to the miniaturization of the overall volume of the compressor 100.

[0053] Optionally, a cut edge gap is formed between the stator and the shell, and the total area of the cut edge gap defined in the cross section along the radial direction of the rotor is S2, which is greater than the total opening area S1 of the exhaust hole.

[0054] It can be understood that the outer peripheral contour of the stator core 311 of the stator 31 is generally not a regular circle, but has a stator 31 cut edge, so that after the stator 31 is assembled with the shell, a certain cut edge gap 103 is formed between the outer wall surface of the stator 31 and the inner wall surface of the shell. By designing the cut edge gap 103, it is beneficial to the flow of high-pressure refrigerant, and also beneficial to the return of refrigeration oil at the top of the motor 30 to the lower part of the compressor 100 through the cut edge gap 103. When the stator 31 cut edge is one, a single cut edge gap 103 is formed between the stator 31 and the shell, and the total area S2 of the cut edge gap 103 is the area of the single cut edge gap 103 in the cross section along the radial direction of the rotor. When the stator 31 cut edge is provided with multiple cut edges, multiple cut edge gaps 103 are formed between the stator 31 and the shell, and the total area S2 of the cut edge gap 103 is the sum of the areas of the multiple cut edge gaps 103 in the cross section along the radial direction of the rotor.

[0055] It can be understood that when the high-pressure refrigerant is discharged from the exhaust hole 22a of the muffler 22, part of the high-pressure refrigerant will flow into the cavity formed by the second winding end portion 3122, and then flow towards the first end shell 12 through the gap between the rotor 32 and the stator 31, and another part of the high-pressure refrigerant will flow towards the first end shell 12 from the cut edge gap 103 between the stator 31 and the shell. In the existing design, due to the unreasonable flow distribution design of the exhaust flow path of the high-pressure refrigerant, it usually causes the high-pressure refrigerant discharged through the exhaust hole 22a to directly hit the rotor 32, and the high-pressure exhaust refrigerant flow is concentrated on the lower surface of the rotor 32, which causes the axial vibration of the rotor 32 to deteriorate and even axial movement, resulting in resonance noise or abnormal sound.

[0056] In order to improve the impact of high-pressure refrigerant on the rotor 32, in the present embodiment, the relationship between the total opening area S1 of the exhaust hole 22a and the total area S2 of the edge gap 103 in the rotor radial cross section is optimized, so that S2 is greater than S1. If S2 is less than S1, the refrigerant gas flow will directly impact the rotor 32, the high-pressure exhaust refrigerant flow is concentrated on the lower surface of the rotor 32, which causes the axial vibration of the rotor 32 to deteriorate and even axial movement, resonance noise or abnormal sound, and the refrigerant gas flow cannot be fully diffused in the edge channel, forming a "bottleneck effect", causing the flow rate to surge, turbulent noise and increased frictional resistance. Under the condition that S2 is greater than S1, the gas flow discharged from the exhaust hole 22a (small area) can be rapidly diffused to the edge channel, reducing the local flow rate, avoiding noise caused by gas flow impacting the stator 31 and the rotor 32, and reducing vibration caused by gas flow excitation, achieving the effect of improving exhaust pulsation, low noise and high efficiency. At the same time, the flow rate is further reduced during the rising process, so that the lubricating oil mixed in the gaseous refrigerant is more easily separated from the gaseous refrigerant due to gravity, thereby reducing the oil discharge amount.

[0057] Optionally, the ratio of S1 to S2 satisfies: .

[0058] Illustratively, the ratio of S1 to S2 can be 0.05, 0.06, 0.07, 0.08, 0.09, 0.10, 0.11, and other arbitrary point values in the interval [0.05, 0.12]. Thus, under the premise that S2 is greater than S1, the ratio of the two is further limited to between 0.05 and 0.12, so that the total area of the edge gap 103 in the rotor radial cross section is much larger than the total area of the exhaust hole 22a, which can make the gas flow discharged from the exhaust hole 22a rapidly diffuse to the edge channel formed by the edge gap 103, rather than directly flow to the annular gap enclosed by the rotor 32 and the stator 31, which can reduce the local flow rate during exhaust, avoid noise caused by gas flow impacting the stator 31 structure, and reduce vibration caused by gas flow excitation, achieving the effect of improving exhaust pulsation, low noise and high efficiency. And by limiting the ratio of S1 to S2 to be less than 0.12, the relative proportion of the edge gap 103 on the stator 31 is limited while the edge gap 103 is the main exhaust path, avoiding the exhaust hole 22a area being too large to damage the connection stability of the stator 31 and the shell, ensuring smooth refrigerant exhaust while ensuring safety and reliability.

[0059] As shown in Figure 3 In an embodiment, the inner diameter of the main shell 11 at the connection end with the first end shell 12 is defined as R5, and the ratio of the total area S2 of the edge gap 103 formed between the stator 31 and the shell 10 to R5 is not less than 1.8.

[0060] In this invention, the side of the first end shell 12 facing the first winding end 3121 can be defined as the inner end face 121, and the side of the stator core 311 facing the inner end face 121 can be defined as the first end face 3111. A first cavity 1011 can be formed between the first end face 3111 and the inner end face 121. Since the tangential gap 103 is opened on the outside of the stator core 311, the tangential gap 103 actually connects the first cavity 1011 and the second cavity 1012. The inner diameter of the end of the main shell 11 connected to the first end shell 12 can be defined as the inner diameter of the first cavity 1011. The cross-section of the first inner cavity can be expressed by the formula π*R5. 2 It was calculated that, with the constant π remaining unchanged, the ratio of S2 to R5 was defined, which in turn defined the ratio of the cross-section of the first inner cavity to the area of ​​the tangential gap 103.

[0061] By limiting the ratio of S2 to R5 to no less than 1.8, it can be ensured that the total area of ​​the tangential gap 103 along the radial cross-section of the rotor is sufficiently large compared to the cross-section of the first inner cavity. This allows the tangential gap 103 to provide sufficient exhaust flow area, especially when the main housing 11 needs to meet the requirements of small size and miniaturization, and the inner diameter R5 cannot be increased indefinitely. By limiting S2 / R5 to ≥ 1.8, the minimum value of the tangential gap 103 can be forcibly guaranteed with a fixed R5, ensuring that the tangential gap 103 provides sufficient exhaust flow area. This avoids a surge in flow velocity, turbulence noise, and increased frictional resistance due to insufficient exhaust flow area, allowing the refrigerant airflow to flow smoothly along the tangential gap 103.

[0062] Furthermore, a sufficiently large tangential gap 103 allows the airflow to rapidly diffuse into the tangential channel after exiting the exhaust port 22a, avoiding a "throttling effect" due to insufficient channel area. Simultaneously, with a ratio of 0.05 ≤ S1 / S2 < 0.12, the total area S1 of the exhaust port 22a is ensured to match the total area S2 of the tangential gap 103 along the rotor's radial cross-section, further reducing flow resistance, provided that the tangential gap 103 dominates the exhaust path.

[0063] like Figure 1 , Figure 5 As shown, in one embodiment, the muffler 22 includes a bottom cover 221 and a muffler hood 222 disposed on one side of the bottom cover 221. The side of the bottom cover 221 away from the muffler hood 222 abuts against the compression component 21. The muffler hood 222 and the compression component 21 surround to form a muffler cavity. The compression component 21 has an exhaust channel communicating with the muffler cavity. The exhaust port 22a is disposed on the muffler hood 222 and communicates with the muffler cavity. The exhaust direction of the exhaust port 22a is tangent to the circumferential direction of the muffler hood 222.

[0064] In the embodiment, the bottom cover 221 comprises opposite first and second sides, the muffler 222 is arranged on the first side of the bottom cover 221, and the second side of the bottom cover 221 is in abutting engagement with the first bearing 211 of the compression component 21, so as to connect the muffler 222 and the compression component 21. The muffler 222 protrudes from the bottom cover 221 to form a boss structure away from the compression component 21, and one side of the muffler 222 away from the bottom cover 221 has an opening for the shaft cylinder of the first bearing 211 to pass through. When the compressor 100 is running, the refrigerant is compressed by the compression component 21 to form high-pressure refrigerant, the high-pressure refrigerant is discharged into the muffling cavity of the muffler 222 through the exhaust passage, and the high-pressure refrigerant can be preliminarily damped and reduced in noise through the muffling cavity. Then, the high-pressure refrigerant is discharged into the shell 10 through the exhaust hole 22a of the muffler 222. Since the exhaust direction of the exhaust hole 22a is tangent to the circumference of the muffler 222, the high-pressure refrigerant discharged from the exhaust hole 22a can be discharged along the tangent direction of the muffler 222, rather than directly flowing out in the axial direction. In this way, the high-pressure refrigerant can be prevented from being directly discharged upward to the rotor 32, so as to reduce the impact force of the high-pressure refrigerant on the end face of the rotor 32, reduce the axial pulsation excitation of the rotor 32, make the operation of the rotor 32 more stable, and thus reduce the vibration noise of the rotor 32.

[0065] As shown in FIGS. 1 and 2, in an embodiment, the main shell 11 comprises a main body portion 111 and a connecting portion 112, the connecting portion 112 comprises a first sub-portion 1121 and a second sub-portion 1122, the first sub-portion 1121 connects the main body portion 111 and the second sub-portion 1122, and the first sub-portion 1121 is arranged in a diverging manner towards the first end shell 12. Figure 1 、 Figure 2 As shown in FIGS. 1 and 2, in an embodiment, the main shell 11 comprises a main body portion 111 and a connecting portion 112, the connecting portion 112 comprises a first sub-portion 1121 and a second sub-portion 1122, the first sub-portion 1121 connects the main body portion 111 and the second sub-portion 1122, and the first sub-portion 1121 is arranged in a diverging manner towards the first end shell 12.

[0066] It can be understood that the volume of the first cavity 1011 is determined by the height of the first cavity 1011 in the axial direction and the width of the first cavity 1011 in the radial direction. When the first sub-portion 1121 is arranged in a diverging manner towards the first end shell 12, the main shell 11 is arranged in a non-equal-diameter manner, and the inner diameter of the main shell 11 on one side of the connecting portion 112 is greater than the inner diameter of the main shell 11 away from the first end shell 12. In this way, the width of the first cavity 1011 in the connecting portion 112 can be increased, and the overall height of the first cavity 1011 can be reduced under the condition that the volume of the first cavity 1011 is unchanged, so as to reduce the overall height of the compressor 100, thereby facilitating the miniaturization of the compressor 100.

[0067] Furthermore, the gradual expansion of the first sub-section 1121 increases the local inner diameter of the first cavity 1011, and the gradual expansion of the first sub-section 1121 increases the strength of the connection part 112 of the main body 111. In order to facilitate the connection of the connection part 112 and the first end shell 12, the connection part 112 is further provided with a second sub-section 1122, the inner side surface of the second sub-section 1122 is connected with the outer surface of the first end shell 12, the second sub-section 1122 serves as a connection and cooperation with the first end shell 12, the inner side surface of the second sub-section 1122 can adapt to the shape of the outer surface of the first end shell 12, which is conducive to the tight welding of the first end shell 12 and the connection part 112. In this way, the overall height of the first cavity 1011 is reduced, and the connection tightness of the main shell 11 and the first end shell 12 is further increased.

[0068] In addition, the inner side surface of the second sub-section 1122 is connected with the outer surface of the first end shell 12, so that the first cavity 1011 is arranged in a non-equal diameter along the height direction. The inner diameter of the first cavity 1011 at the first end shell 12 part is smaller than the inner diameter of the first cavity 1011 at the second sub-section 1122 part. When the first end shell 12 is arranged in an equal diameter, the inner radius of the first end shell 12 can be defined as R6.

[0069] Optionally, the main body 111 is arranged in an equal inner diameter along the axial direction, the inner diameter of the main body 111 is the inner diameter R7 of the second cavity 1012, the maximum inner diameter of the second sub-section 1122 is defined as R5, and the ratio of R5 to R7 is not less than 1.05 and not more than 1.2.

[0070] R7 is the inner radius of the main body 111, R5 is the inner radius of the connection part 112, which is also the maximum inner radius of the second sub-section 1122. By gradually expanding the connection part 112, the maximum inner diameter of the first cavity 1011 is increased, which provides more radial space for the first cavity 1011. Under the premise of meeting the miniaturization of the compressor 100, i.e. the height of the first cavity 1011 cannot be too high, it is convenient to realize that the actual volume of the first cavity 1011 is greater than that of the second cavity 1012, so as to reduce the exhaust resistance and make the exhaust smooth.

[0071] In addition, if the ratio of R5 to R7 is too large, the difference between the upper and lower end inner diameters will be too large, which will cause the airflow entering the first cavity 1011 from the lower cavity to be sharply diverted, forming a local vortex area and increasing the exhaust resistance and pressure loss.

[0072] As Figure 3 , Figure 4As shown, in an embodiment, the outer diameter of the first winding end portion 3121 is defined as R1, the inner diameter of the first end shell 12 is defined as R6, the outer diameter of the second winding end portion 3122 is defined as R3, the inner diameter of the second cavity 1012 is defined as R7, the ratio of R1 to R6 is not less than 0.8 and not greater than 0.95, and / or the ratio of R3 to R7 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, which leads to uneven flow velocity distribution, increased local turbulent flow, and further causes 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 causes the airflow velocity to increase sharply, and the high-speed airflow easily entrains lubricating oil and impacts 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, the local vortex is reduced, and the ratio of the height H1 of the first cavity 1011 to the height h1 of the first winding end portion 3121 is 0.4≤h1 / H1≤0.6, which realizes 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] A second passage gap for the circulation of refrigerant is formed between the outer circumferential surface of the second winding end portion 3122 and the inner circumferential surface of the main shell 11. 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 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] 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].

[0077] 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.

[0078] like Figure 1 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 32 toward the direction away from the first end shell 12. The muffler 22 is located on the side of the first bearing 211 away from the cylinder 212. 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.

[0079] 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.

[0080] The above description is merely an exemplary embodiment of the present invention and does not limit the scope of protection of the present invention. Any equivalent structural transformations made based on the technical concept of the present invention and the contents of the specification and drawings of the present invention, or direct / indirect applications in other related technical fields, are included within the scope of protection of the present invention.

Claims

1. A compressor, characterized in that, include: The housing includes a main housing and a first end housing disposed at one end of the main housing; An electric motor, disposed within the housing, includes a rotor and a stator disposed around the rotor. The stator includes a stator core and a coil winding. The coil winding has a first winding end and a second winding end located at opposite ends of the stator core. The first winding end is located at the end of the stator core facing the first end housing. The stator core has a second end face facing away from the first end housing. A pump body assembly is disposed within the housing. The pump body assembly includes a crankshaft connected to the rotor, a compression component and a muffler sleeved around the crankshaft, the muffler being located on the side of the compression component facing the rotor, the muffler having an exhaust port, and a second cavity being formed between the mounting plane of the pump body assembly and the second end face. The total opening area of ​​the exhaust port is defined as S1, the axial height of the second cavity is H2, the inner diameter of the second cavity is R7, the axial height of the end of the second winding is h2, the outer diameter of the end of the second winding is R3, the inner diameter of the end of the second winding is R4, and the exhaust volume of the pump assembly is P. At least one of the following relations must be satisfied: ； 。 2. The compressor as described in claim 1, characterized in that, A tangential gap is formed between the stator and the housing. The total area of ​​the tangential gap is defined as S2 on the cross-section along the radial direction of the rotor. S2 is greater than the total opening area S1 of the exhaust port.

3. The compressor as described in claim 2, characterized in that, The ratio of S1 to S2 satisfies: .

4. The compressor as described in claim 2, characterized in that, The inner diameter of the end where the main housing connects to the first end shell is defined as R5, and the ratio of the total area S2 of the tangential gap formed between the stator and the housing to R5 is not less than 1.

8.

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

6. The compressor as claimed in claim 1, characterized in that, The main housing includes a main body and a connecting part. The connecting part 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. 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 diameter of the main body is the inner diameter R7 of the second cavity. The maximum inner diameter of the second sub-segment is defined as R5. The ratio of R5 to R7 is not less than 1.05 and not greater than 1.

2.

8. The compressor as described in claim 6, characterized in that, Define the outer diameter of the first winding end as R1, the inner diameter of the first end shell as R6, the outer diameter of the second winding end as R3, and the inner diameter of the second cavity as R7. The ratio of R1 to R6 is not less than 0.8 and not greater than 0.95; and / or the ratio of R3 to R7 is not less than 0.8 and not greater than 0.

95.

9. The compressor as claimed in any one of claims 1 to 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, the compression component includes a first bearing, a cylinder and a second bearing arranged sequentially from the side near the rotor toward the direction away from the first end shell, and the muffler is located on the side of the first bearing away from the cylinder.

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

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