Compressor and air conditioner

Abstract

A compressor and an air conditioner. A compression mechanism is arranged in a shell of the compressor. The compression mechanism comprises an eccentric crankshaft and a first bearing. The eccentric crankshaft comprises a first shaft section. The diameter of the first shaft section is D5. The first bearing is sleeved on the first shaft section. The first bearing comprises a first sub-bearing and a second sub-bearing. The first sub-bearing is arranged at the bottom of the second sub-bearing. An annular groove with a bottom opening is arranged on the first sub-bearing. The annular groove surrounds the first shaft section. The height of the annular groove is H3. The inner diameter of the annular groove is D6. The outer diameter of the annular groove is D7. Wherein, (D7-D6) / D5=[0.09, 0.13], (D7-D6) / H3=[0.2, 0.6], so as to reduce the wear of the first bearing and improve the performance of the compressor.

Description

Technical Field

[0001] The present disclosure relates to the technical field of air conditioning, and in particular to a compressor and an air conditioner. Background Art

[0002] The air conditioner performs the cooling and heating cycle of the air conditioner by using a compressor, a condenser, an expansion valve and an evaporator. Generally, a rolling rotor compressor includes a housing, in which a motor and a compression mechanism are arranged. In a two-cylinder rotor compressor, a second sub-muffler, a second bearing, a second cylinder, a middle partition, a first cylinder, a first bearing, a first sub-muffler and a motor are arranged on the eccentric crankshaft from bottom to top, a second piston is arranged in the second cylinder, and a first piston is arranged in the first cylinder.

[0003] For the fit between the first bearing and the eccentric crankshaft, an annular groove is provided on the first bearing, and the annular groove is provided close to the eccentric crankshaft. The annular groove makes the contact between the first bearing and the eccentric crankshaft a surface contact to improve wear. The proportional relationship between the setting height, inner diameter and other dimensions of the annular groove and the diameter and other dimensions of the eccentric crankshaft will directly affect the radial deformation and wear of the first bearing, thereby affecting the performance of the compressor.

[0004] The above information disclosed in the background technology is only used to increase the understanding of the background technology of the present application, and therefore, it may include information that does not constitute the prior art known to ordinary technicians in the field. Summary of the invention

[0005] In view of the problems pointed out in the background technology, the utility model provides a compressor and an air conditioner, and optimizes the design of the annular groove of the first bearing and the eccentric crankshaft to reduce the wear of the upper bearing and improve the performance of the compressor.

[0006] In order to achieve the above-mentioned utility model purpose, the utility model adopts the following technical solutions:

[0007] On the one hand, a compressor is provided, wherein a compression mechanism is arranged in a shell of the compressor, the compression mechanism includes an eccentric crankshaft and a first bearing, the eccentric crankshaft includes a first shaft section, the diameter of the first shaft section is D5, the first bearing is sleeved on the first shaft section, the first bearing includes a first sub-bearing and a second sub-bearing, the first sub-bearing is arranged at the bottom of the second sub-bearing, an annular groove with a bottom opening is arranged on the first sub-bearing, the annular groove surrounds the first shaft section, the height of the annular groove is H3, the inner diameter of the annular groove is D6, and the outer diameter of the annular groove is D7; wherein, (D7-D6) / D5=[0.09, 0.13], (D7-D6) / H3=[0.2, 0.6], so as to reduce the wear of the first bearing and improve the performance of the compressor.

[0008] On the other hand, an air conditioner is provided, comprising a compressor, an evaporator, a condenser and a throttling device, wherein the compressor is the compressor as described above.

[0009] After reading the specific embodiments of the present invention in conjunction with the accompanying drawings, other features and advantages of the present invention will become more clear. BRIEF DESCRIPTION OF THE DRAWINGS

[0010] Figure 1 is a structural diagram of a compressor according to some embodiments;

[0011] Figure 2A is a schematic diagram of a compressor according to some embodiments;

[0012] Figure 2B is a schematic block diagram of a processor, a sensor, and an exciter according to some embodiments;

[0013] Figure 3 is a cross-sectional view of a compressor body according to some embodiments;

[0014] Figure 4 is a cross-sectional view of a compression mechanism according to some embodiments;

[0015] Figure 5 for Figure 4 A partial enlarged view of the middle circle A;

[0016] Figure 6 is a cross-sectional view of an eccentric crankshaft, a first bearing, and a rotor according to some embodiments;

[0017] Figure 7 A partial view of a first shaft section and a rotor of an eccentric crankshaft according to some embodiments;

[0018] Figure 8 is a cross-sectional view of an eccentric crankshaft and a first bearing according to some embodiments;

[0019] Fig. 9 is a cross-sectional view of a first bearing according to some embodiments;

[0020] Fig.10 is a structural diagram of an eccentric crankshaft according to some embodiments;

[0021] Fig.11 is a cross-sectional view of an eccentric crankshaft according to some embodiments;

[0022] Fig. 12A is another cross-sectional view of an eccentric crankshaft according to some embodiments;

[0023] Fig. 12B for Fig. 12A A partial enlarged view of the middle circle B;

[0024] Fig.13 is a structural diagram of a channel member and a moving member according to some embodiments;

[0025] Fig.14 is another structural diagram of a channel member and a moving member according to some embodiments;

[0026] Fig.15 is a structural diagram of a stator according to some embodiments;

[0027] Fig.16 is a top view of a compressor according to some embodiments;

[0028] Fig.17 is a structural diagram of a bracket according to some embodiments;

[0029] Fig.18 is another structural diagram of a bracket according to some embodiments;

[0030] Fig.19 is a top view of another compressor according to some embodiments;

[0031] Fig. 20 is a structural diagram of another stent according to some embodiments;

[0032] Fig.21 A data curve diagram of the initial oiling time of the compressor according to some embodiments;

[0033] Fig. 22 is a data curve diagram of the oil discharge rate of the compressor according to some embodiments;

[0034] Fig.23 is a graph showing the relationship between (D7-D6) / D5 and the friction loss of the first bearing according to some embodiments;

[0035] Fig.24 is a relationship diagram between (D7-D6) / H3 and the radial deformation of the first bearing according to some embodiments;

[0036] Fig.25 is a graph showing the relationship between D5 / D11×H5 / H4 and the friction loss of the compressor according to some embodiments;

[0037] Fig.26 is a relationship diagram between H5 / H6×D5 / D11 and the radial deformation of the first bearing according to some embodiments;

[0038] Fig. 27 is a graph showing the relationship between H7 / H2 and the COP efficiency of the compressor according to some embodiments;

[0039] Fig.28 is a relationship diagram between (H8+H5) / H9 and the radial deformation of the first bearing according to some embodiments;

[0040] Fig.29 is a relationship diagram between (D8-D9) / (H9-H8) and motor efficiency and radial deformation of the first bearing according to some embodiments;

[0041] Fig.30 is a relationship diagram between (D11-D5) / H5 and the radial deformation of the first bearing according to some embodiments;

[0042] Fig.31 is a graph showing the relationship between D9 / D5 and motor efficiency according to some embodiments;

[0043] Fig.32 is a graph showing the relationship between D8 / D9 and motor efficiency according to some embodiments;

[0044] Fig.33 is a graph showing the relationship between H11 / (H10×H8) and motor efficiency according to some embodiments;

[0045] Fig.34 is a graph showing the relationship between D14 / (H8×D9) and compressor noise and motor efficiency according to some embodiments;

[0046] Fig.35 is a graph showing the relationship between H16 / (H8×S) and motor noise and efficiency according to some embodiments;

[0047] Fig.36 is a graph showing the relationship between d1 / d2 and motor efficiency and speed according to some embodiments;

[0048] Fig.37 4 is a relationship diagram of d4 / S, motor efficiency, and eccentric crankshaft deformation according to some embodiments. DETAILED DESCRIPTION

[0049] Some embodiments of the present disclosure will be described clearly and completely below in conjunction with the accompanying drawings. Obviously, the described embodiments are only part of the embodiments of the present disclosure, rather than all of the embodiments. All other embodiments obtained by ordinary technicians in this field based on the embodiments provided by the present disclosure are within the scope of protection of the present disclosure.

[0050] Unless the context requires otherwise, throughout the specification and claims, the term "comprise" and other forms thereof, such as the third person singular form "comprises" and the present participle form "comprising", are to be interpreted as open, inclusive, that is, "including, but not limited to". In the description of the specification, the terms "one embodiment", "some embodiments", "exemplary embodiments", "example", "specific example" or "some examples" and the like are intended to indicate that specific features, structures, materials or characteristics associated with the embodiment or example are included in at least one embodiment or example of the present disclosure. The schematic representation of the above terms does not necessarily refer to the same embodiment or example. In addition, the specific features, structures, materials or characteristics may be included in any one or more embodiments or examples in any appropriate manner.

[0051] In the following, the terms "first" and "second" are used for descriptive purposes only and are not to be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of the features. In the description of the embodiments of the present disclosure, unless otherwise specified, "plurality" means two or more.

[0052] When describing some embodiments, the expressions "coupled" and "connected" and their derivatives may be used. The term "connected" should be understood in a broad sense. For example, "connection" can be a fixed connection, a detachable connection, or an integral connection; it can be directly connected or indirectly connected through an intermediate medium. The term "coupled" indicates that two or more components are in direct physical or electrical contact. The term "coupled" or "communicatively coupled" may also refer to two or more components that are not in direct contact with each other, but still cooperate or interact with each other. The embodiments disclosed herein are not necessarily limited to the contents of this document.

[0053] “At least one of A, B, and C” has the same meaning as “at least one of A, B, or C” and both include the following combinations of A, B, and C: A only, B only, C only, the combination of A and B, the combination of A and C, the combination of B and C, and the combination of A, B, and C.

[0054] “A and / or B” includes the following three combinations: A only, B only, and a combination of A and B.

[0055] The use of "adapted to" or "configured to" herein is meant to be open and inclusive language that does not exclude devices adapted or configured to perform additional tasks or steps.

[0056] As used herein, "about," "substantially," or "approximately" includes the stated value and an average value that is within an acceptable range of variation from the particular value as determined by one of ordinary skill in the art taking into account the measurements in question and the errors associated with the measurement of the particular quantity (i.e., the limitations of the measurement system).

[0057] As used herein, "parallel", "perpendicular", and "equal" include the situations described and situations similar to the situations described, and the range of the similar situations is within the acceptable deviation range, wherein the acceptable deviation range is determined by a person of ordinary skill in the art taking into account the measurement in question and the errors associated with the measurement of a particular quantity (i.e., the limitations of the measurement system). For example, "parallel" includes absolute parallelism and approximate parallelism, wherein the acceptable deviation range of approximate parallelism may be, for example, a deviation within 5°; "perpendicular" includes absolute perpendicularity and approximate perpendicularity, wherein the acceptable deviation range of approximate perpendicularity may also be, for example, a deviation within 5°. "Equal" includes absolute equality and approximate equality, wherein the acceptable deviation range of approximate equality may be, for example, the difference between the two equalities is less than or equal to 5% of either one.

[0058] [Air conditioner]

[0059] In some embodiments of the present disclosure, the air conditioner performs a cooling and heating cycle of the air conditioner by using a compressor, a condenser, an expansion valve and an evaporator. The cooling and heating cycle includes a series of processes involving compression, condensation, expansion and evaporation to cool or heat the indoor space.

[0060] The low-temperature and low-pressure refrigerant enters the compressor, which compresses it into high-temperature and high-pressure refrigerant gas and discharges the compressed refrigerant gas. The discharged refrigerant gas flows into the condenser. The condenser condenses the compressed refrigerant into a liquid phase, and the heat is released to the surrounding environment through the condensation process.

[0061] The expansion valve expands the high-temperature and high-pressure liquid refrigerant condensed in the condenser into a low-pressure liquid refrigerant. The evaporator evaporates the refrigerant expanded in the expansion valve and returns the low-temperature and low-pressure refrigerant gas to the compressor. The evaporator can achieve a cooling effect by utilizing the latent heat of evaporation of the refrigerant to exchange heat with the material to be cooled. In the entire cycle, the air conditioner can adjust the temperature of the indoor space.

[0062] The outdoor unit (outdoor unit) of the air conditioner refers to a part of the refrigeration cycle including a compressor and an outdoor heat exchanger, the indoor unit (indoor unit) of the air conditioner includes an indoor heat exchanger, and an expansion valve may be provided in the indoor unit or the outdoor unit.

[0063] The indoor heat exchanger and the outdoor heat exchanger function as a condenser or an evaporator. When the indoor heat exchanger functions as a condenser, the air conditioner performs a heating mode; when the indoor heat exchanger functions as an evaporator, the air conditioner performs a cooling mode.

[0064] The outdoor unit also includes a four-way valve, which is configured to switch the indoor heat exchanger and the outdoor heat exchanger as a condenser or an evaporator. The refrigeration working principle of the air conditioner is: the operation of the compressor makes the indoor heat exchanger (in the indoor, that is, the evaporator) in an ultra-low pressure state, the liquid refrigerant in the indoor heat exchanger evaporates quickly to absorb heat, the wind blown by the indoor fan is cooled by the indoor heat exchanger coil and becomes cold wind to be blown indoors, the evaporated refrigerant is pressurized by the compressor, and condensed into liquid under the high pressure environment of the outdoor heat exchanger (in the outdoor, that is, the condenser), releasing heat, and dissipating the heat into the atmosphere through the outdoor fan, so that the cycle achieves the cooling effect.

[0065] The heating working principle of the air conditioner is as follows: the gaseous refrigerant is pressurized by the compressor, becomes a high-temperature and high-pressure gas, enters the indoor heat exchanger (the condenser at this time), condenses and liquefies to release heat, becomes a liquid, and heats the indoor air at the same time, thereby achieving the purpose of raising the indoor temperature. The liquid refrigerant is decompressed by the throttling device and enters the outdoor heat exchanger (the evaporator at this time), evaporates and vaporizes to absorb heat, becomes a gas, and absorbs heat from the outdoor air (the outdoor air becomes colder), becomes a gaseous refrigerant, and enters the compressor again to start the next cycle.

[0066] [Compressor body]

[0067] The compressor in some embodiments of the present disclosure is a rolling rotor compressor. Figure 1 and Figure 3 The compressor comprises a compressor body 1. The compressor body 1 comprises a first shell 11, and a closed inner cavity is formed in the first shell 11.

[0068] The compressor body 1 comprises a motor 13 which is arranged in the inner cavity.

[0069] In some embodiments, reference Figure 4 The compressor body 1 includes a compression mechanism 14 , which is disposed in an inner cavity of the first shell 11 .

[0070] The motor 13 provides power for the compression mechanism 14. The compression mechanism 14 is configured to compress the refrigerant. The motor 13 is disposed above the compression mechanism 14. Figure 4It is a structural schematic diagram of the compression mechanism 14.

[0071] The first housing 11 includes an upper housing, a circumferential housing and a lower housing. The circumferential housing is arranged between the upper housing and the lower housing. The upper housing is arranged at the top of the circumferential housing, and the lower housing is arranged at the bottom of the circumferential housing. The upper housing, the circumferential housing and the lower housing surround the inner cavity of the compressor body 1.

[0072] In some embodiments, reference Figure 3 The motor 13 includes a stator 310 and a rotor 320. The stator 310 is fixedly connected to the inner wall of the first housing 11 to achieve fixed installation of the motor 13 in the inner cavity of the compressor. Fig.15 A structural diagram of the stator 310 is shown.

[0073] In some embodiments, reference Figure 4 The compression mechanism 14 includes an eccentric crankshaft 110, a cylinder, a piston, a bearing, a muffler, etc.

[0074] In some embodiments, reference Fig.10 and Fig.11 The eccentric crankshaft 110 includes a first shaft section 111, an eccentric shaft section and a second shaft section 115. The first shaft section 111 is fixedly connected to the rotor 320. A piston is arranged in the compression chamber of the cylinder, and the piston is sleeved on the eccentric shaft section. The bearing is fixedly connected to the cylinder, and a bearing exhaust hole is arranged on the bearing, and the bearing exhaust hole is communicated with the compression chamber. A vane groove is arranged on the cylinder, and a vane is arranged in the vane groove. The eccentric crankshaft 110 drives the piston to make circumferential motion in the compression chamber, and the vane reciprocates along the vane groove. The vane always abuts against the piston, and the vane and the piston separate the compression chamber into a high-pressure chamber and a low-pressure chamber.

[0075] The working principle of the compressor is as follows: the stator 310 of the motor 13 generates a magnetic pull after being energized, and the rotor 320 of the motor 13 rotates under the action of the magnetic pull of the stator, and drives the eccentric crankshaft 110 to rotate together. The rotation of the eccentric crankshaft 110 drives the piston sleeved on its eccentric shaft segment to perform eccentric circular motion in the compression chamber of the cylinder, and the vane reciprocates in the vane groove. The vane and the piston divide the compression chamber of the cylinder into a high-pressure chamber and a low-pressure chamber. The eccentric crankshaft 110 drives the piston to rotate one circle, and then air is sucked from the low-pressure chamber and exhausted from the high-pressure chamber to complete one exhaust, thereby realizing the compression of the gas by the compressor, and the compressed gas is discharged through the bearing exhaust hole.

[0076] In some embodiments, the compressor body 1 is a double-cylinder rolling rotor type, referring to Figure 3 and Figure 4The compression mechanism 14 includes an eccentric crankshaft 110, two cylinders (respectively a first cylinder 122 and a second cylinder 121), two bearings (respectively a first bearing 152 and a second bearing 151), two pistons (respectively a first piston 132 and a second piston 131), a middle partition 160, and two silencers 800 (respectively a first sub-silencer 142 and a second sub-silencer 141).

[0077] Reference Fig.10 and Fig.11 The eccentric crankshaft 110 includes, from top to bottom, a first shaft section 111, a first eccentric shaft section 112, a connecting shaft section 113, a second eccentric shaft section 114 and a second shaft section 115. A first piston 132 capable of eccentric movement is provided in the compression chamber of the first cylinder 122, and the first piston 132 is sleeved on the first eccentric shaft section 112; a second piston 131 capable of eccentric movement is provided in the compression chamber of the second cylinder 121, and the second piston 131 is sleeved on the second eccentric shaft section 114; a middle partition plate 160 is sleeved on the connecting shaft section 113, and the middle partition plate 160 is located between the first cylinder 122 and the second cylinder 121; a first bearing 152 (upper bearing) is sleeved on the first shaft section 111 and connected to the first cylinder 122 at the same time; a second bearing 151 (lower bearing) is sleeved on the second shaft section 115 and connected to the second cylinder 121 at the same time.

[0078] The first eccentric shaft segment 112 and the second eccentric shaft segment 114 are arranged at a relative angle of 180°, the first piston 132 and the second piston 131 rotate eccentrically at the same time, the compressed gas in the compression chamber of the first cylinder 122 is discharged through the exhaust hole on the first bearing 152, and the compressed gas in the compression chamber of the second cylinder 121 is discharged through the exhaust hole on the second bearing 151.

[0079] The first sub-muffler 142 is arranged on the first bearing 152, and the first sub-muffler 142 covers the exhaust hole of the first bearing 152. The compressed gas in the first cylinder 122 is first discharged through the exhaust hole of the first bearing 152 to the space surrounded by the first sub-muffler 142 and the first bearing 152, and then discharged through the exhaust hole of the upper muffler 142 to the inner cavity of the compressor.

[0080] The second sub-muffler 141 is disposed on the second bearing 151 , and the second sub-muffler 141 covers the exhaust hole of the first bearing 151 . The compressed gas in the second cylinder 121 is first discharged into the space enclosed by the second sub-muffler 141 and the second bearing 151 through the exhaust hole on the second bearing 151 .

[0081] In some embodiments, different from the related art, Figure 4There is no exhaust hole on the second sub-muffler 141, and a plurality of air flow channels 170 extending vertically are provided on the first bearing 152, the first cylinder 122, the middle partition plate 160, the second cylinder 121 and the wall of the second bearing 151. The compressed air in the second bearing 151 and the second sub-muffler 141 is discharged upward through the air flow channel 170 to the space surrounded by the first bearing 152 and the first sub-muffler 142, and then discharged into the inner cavity of the compressor through the exhaust hole of the first sub-muffler 142.

[0082] [Gas-Liquid Separator]

[0083] In some embodiments, reference Figure 1 The compressor includes a gas-liquid separator 2, which is arranged outside the compressor body 1 and is configured to provide gaseous refrigerant to the compression chamber of the compression mechanism 14. The gas-liquid separator 2 separates the liquid refrigerant from the gaseous refrigerant to prevent the liquid refrigerant from entering the compression chamber of the compressor body 1 and causing compressor abnormality.

[0084] The gas-liquid separator 2 comprises a second shell 21, and an air outlet pipe 22 is arranged at the bottom of the second shell 21. One end of the air outlet pipe 22 extends into the inner cavity of the second shell 21, and the other end of the air outlet pipe 22 is connected to the compression mechanism 14 to provide gaseous refrigerant to the compression mechanism 14.

[0085] [Structure of the first bearing]

[0086] In some embodiments, reference Figure 8 and Fig. 9 , the first shaft section 111 is sleeved with the first bearing 152. The first bearing 152 includes a first sub-bearing 1521 and a second sub-bearing 1522 of an integrated structure, and the first sub-bearing 1521 is arranged at the bottom of the second sub-bearing 1522. A through shaft hole is arranged in the second sub-bearing 1522, and the first shaft section 111 is inserted into the shaft hole of the second sub-bearing 1522. The first sub-bearing 1521 is provided with an annular groove 1523 with a bottom opening, and the annular groove 1523 surrounds the first shaft section 111, that is, the annular groove 1523 surrounds the shaft hole of the first bearing 152.

[0087] The annular groove 1523 is provided to make the contact between the first bearing 152 and the eccentric crankshaft 110 a surface contact, so as to reduce wear. The proportional relationship between the setting height, inner diameter and other dimensions of the annular groove 1523 and the diameter and other dimensions of the eccentric crankshaft 110 will affect the radial deformation and wear of the first bearing 152, thereby affecting the performance of the compressor.

[0088] Based on this, in some embodiments of the present disclosure, the proportional relationship between the setting height, inner diameter and other dimensions of the annular groove 1523 and the diameter and other dimensions of the eccentric crankshaft 110 is optimized to reduce the wear of the first bearing 152 and improve the performance of the compressor.

[0089] For example, refer to Fig.11 , the diameter of the first shaft section 111 of the eccentric crankshaft 110 is D5. Fig. 9 The height of the annular groove 1523 is H3, the inner diameter of the annular groove 1523 is D6, and the outer diameter of the annular groove 1523 is D7.

[0090] It should be noted that (D7-D6) / D5=[0.09, 0.13]. Within this range, the friction loss of the first bearing 152 is small. Fig.23 The graph shows the relationship between (D7-D6) / D5 and the friction loss of the first bearing 152.

[0091] It should be noted that (D7-D6) / H3=[0.2, 0.6]. Within this range, the first bearing 152 has a small radial deformation and a small force, which is beneficial to reducing wear and improving the reliability of the first bearing 152. Fig.24 The figure shows the relationship between (D7-D6) / H3 and the radial deformation of the first bearing 152.

[0092] In some embodiments, reference Fig. 9 The outer diameter of the shaft shoulder of the second sub-bearing 1522 is D11. The second sub-bearing 1522 is a multi-step structure, and the outer diameter of the second sub-bearing 1522 increases step by step from top to bottom. The outer diameter of the shaft shoulder D11 is the outer diameter of the upper section of the second sub-bearing 1522.

[0093] The height of the first bearing 152 is H4, ie, the distance between the top end of the second sub-bearing 1522 and the bottom end of the first sub-bearing 1521 .

[0094] The first bearing 152 is welded to the inner wall of the first housing 11 of the compressor, and the height distance between the welding point of the first bearing 152 and the top of the second sub-bearing 1522 is H5. For example, the circumferential outer wall of the first sub-bearing 1521 is welded to the circumferential inner wall of the first housing 11.

[0095] It should be noted that when D5 / D11×H5 / H4>0.45, within this range, the friction loss of the compressor is small. Fig.25 This is the relationship diagram between D5 / D11×H5 / H4 and the friction loss of the compressor.

[0096] In some embodiments, reference Fig. 9 The first bearing 152 is welded to the inner wall of the first housing 11, and the height distance between the welding point of the first bearing 152 and the top of the second sub-bearing 1522 is H5. The outer diameter of the shaft shoulder of the second sub-bearing 1522 is D11.

[0097] In some embodiments, reference Fig.11, the height of the first shaft section 111 is H6. When H5 / H6×D5 / D11>0.2, within this range, the radial deformation of the first bearing 152 is small, the force is small, which is conducive to reducing wear and reliability. Fig.26 The figure shows the relationship between H5 / H6×D5 / D11 and the radial deformation of the first bearing 152.

[0098] In some embodiments, reference Figure 4 , the height of the middle partition 160 is H7, the height of the first cylinder 122 is H2, and the heights of the first cylinder 122 and the second cylinder 121 are the same. When H7 / H2=[0.22, 0.35], within this range, the energy conversion efficiency (Coefficient of Performance, COP) of the compressor is high. Fig. 27 This is the relationship diagram between H7 / H2 and the COP efficiency of the compressor.

[0099] [Structure of the first bearing and the motor]

[0100] In some embodiments, the first shaft section 111 of the eccentric crankshaft 110 is sleeved with a first bearing 152 and a motor 13, and the motor 13 is located above the first bearing 152. The size ratio between the first bearing 152 and the motor 13 will directly affect the radial deformation and wear of the first bearing 152, thereby affecting the performance of the compressor.

[0101] Based on this, in some embodiments of the present disclosure, the size ratio relationship between the first bearing 152 and the motor 13 is optimized to reduce the wear of the first bearing 152 and improve the performance of the compressor.

[0102] For example, refer to Fig. 9 The height distance between the welding point of the first sub-bearing 1521 (lateral part) of the first bearing 152 and the top of the first bearing 152 is H5, and the outer diameter of the first sub-bearing 1521 of the first bearing 152 is D8. Figure 3 , Figure 6 and Figure 7 The motor 13 includes a rotor 320 and a stator 310. The rotor 320 is sleeved on the first shaft section 111. The height of the rotor 320 along the axial direction of the eccentric crankshaft 110 is H8. The height distance between the top of the rotor 320 and the welding point of the first sub-bearing 1521 is H9. The outer diameter of the rotor 320 is D9.

[0103] It should be noted that when (H8+H5) / H9>0.9, within this range, the radial deformation of the first bearing 152 is small and the force is small, which is beneficial to reducing wear and improving the reliability of the first bearing 152. Fig.28 The figure shows the relationship between (H8+H5) / H9 and the radial deformation of the first bearing 152.

[0104] It should be noted that when (D8-D9) / (H9-H8)=[1, 1.5], the motor efficiency is high within this range, the radial deformation of the first bearing 152 is small, and the force is small, which is conducive to reducing wear and improving the reliability of the first bearing 152. Fig.29 The upward convex arc curve is the relationship diagram between (D8-D9) / (H9-H8) and the motor efficiency, and the downward concave arc curve is the relationship diagram between (D8-D9) / (H9-H8) and the radial deformation of the first bearing 152.

[0105] In some embodiments, reference Fig. 9 The outer diameter of the shaft shoulder of the second sub-bearing 1522 (vertical part) is D11, and the height distance between the welding point of the first sub-bearing 1521 and the top of the first bearing 152 is H5. Fig.11 The outer diameter of the first shaft section 111 is D5, (D11-D5) / H5=[0.1, 0.3]. Within this range, the first bearing 152 has excellent radial deformation and small force, which is beneficial to reducing wear and improving the reliability of the first bearing 152. Fig.30 The figure shows the relationship between (D11-D5) / H5 and the radial deformation of the first bearing 152.

[0106] In some embodiments, reference Figure 6 , the outer diameter of the rotor 320 is D9, refer to Fig.11 , the outer diameter of the first shaft section 111 is D5, D9 / D5=[2.5, 4], and the motor efficiency is high within this range. Fig.31 The figure shows the relationship between D9 / D5 and motor efficiency.

[0107] In some embodiments, reference Fig. 9 , the outer diameter of the first sub-bearing 1521 is D8. Figure 6 , the outer diameter of the rotor 320 is D9, D8 / D9=[1.2, 2], and the motor efficiency is high within this range. Fig.32 The figure shows the relationship between D8 / D9 and motor efficiency.

[0108] In some embodiments, the motor 13 and the first bearing 152 are disposed on the first shaft section 111, and the motor 13 is located above the first bearing 152. A countersunk hole 321 is disposed at the bottom of the rotor 320 of the motor 13, the first shaft section 111 passes through the countersunk hole 321, and the top of the second sub-bearing 1522 of the first bearing 152 extends into the countersunk hole 321 to avoid interference between the first bearing 152 and the motor 13. If the countersunk hole 321 is set at a low height, it will interfere with the first bearing 152; if the countersunk hole 321 is set at a too high height, the compressor efficiency will be reduced.

[0109] Based on this, in some embodiments of the present disclosure, by optimizing the design of the counterbore 321 on the rotor 320, not only can the interference between the motor 13 and the first bearing 152 be avoided, but also the high efficiency of the motor 13 can be ensured.

[0110] For example, refer to Figure 7 The height of the counterbore 321 is H10, the height distance of the second sub-bearing 1522 extending into the counterbore 321 is H11, the stacking height of the rotor 320 is H8, 0.006<H11 / (H10×H8)<0.009, within this range, it is beneficial to improve the efficiency of the motor 13. Fig.33 The figure shows the relationship between H11 / (H10×H8) motor efficiency.

[0111] [Structure of bearing and compressor housing]

[0112] In some embodiments, the first bearing 152 of the compression mechanism 14 is fixed to the inner circumferential wall of the first shell 11 of the compressor body 1 by welding, so as to realize the installation of the compression mechanism 14 in the inner cavity of the first shell 11. Taking a two-cylinder compressor as an example, the first bearing 152 is welded to the inner wall of the first shell 11.

[0113] The number of welding spots between the bearing and the inner wall of the housing will affect welding strength, welding deformation, welding efficiency, etc. If the number of welding spots is small, the welding strength is insufficient, which may easily cause the compression mechanism 14 to fall off and cause danger. If the number of welding spots is large, the bearing or cylinder may be easily deformed, resulting in reduced air tightness, which may also affect welding efficiency.

[0114] In order to solve the above technical problems, in some embodiments of the present disclosure, the weight of the compression mechanism 14, the number of bearing welding points and other parameters are optimized to improve the installation reliability of the compression mechanism 14 and meet the high speed requirements of the compressor.

[0115] For example, refer to Fig.16 , the inner diameter of the first housing 11 of the compressor is D14, the number of welding points between the first bearing 152 and the first housing 11 is N, and the weight of the compression mechanism 14 is G. G / N>[1, 4], D14 / N>[25, 45], within this range, the high speed requirement, 500 times gravity requirement and air leakage requirement of the compressor can be taken into account and met.

[0116] In some embodiments, the motor 13 and the compression mechanism 14 need to match in height direction. When the compression mechanism 14 has a low welding height, the compression mechanism 14 and the motor 13 are positioned lower in the first housing 11. Since the centroid of the compressor is positively correlated with the welding height of the compression mechanism 14, the height of the centroid of the compressor also becomes lower, which is beneficial to improving the stability of the compressor.

[0117] In some embodiments, the welding height of the compression mechanism 14 determines the size of the compressor oil pool. Generally, after the compressor is filled with oil, the oil level does not exceed the upper surface of the first cylinder 122. The filling amount of the refrigeration oil is determined by the refrigerant filling amount of the air conditioning system, and the refrigerant filling amount is related to the compressor displacement. Therefore, after the compressor displacement is determined, the filling amount of the refrigeration oil is basically determined, thereby determining the size of the oil pool.

[0118] Reference Figure 1 The distance between the welding point of the first bearing 152 and the bottom of the first shell 11 is H15, the height of the first shell 11 is H16, H15 / H16=[0.35, 0.45]. This range meets the compressor oil pool volume requirement and makes the compressor center of mass low.

[0119] [Structure of the eccentric crankshaft]

[0120] In some embodiments, an oil pool is formed at the bottom of the inner cavity of the first shell 11 of the compressor body 1 .

[0121] An oil supply passage 116 is provided in the eccentric crankshaft 110 and extends along the axial direction of the eccentric crankshaft 110. The oil supply passage 116 is configured to supply the oil in the oil pool to the friction pairs on the eccentric crankshaft 110, such as bearings, cylinders, pistons, etc.

[0122] Reference Fig.11 , the oil supply channel 116 passes through the eccentric crankshaft 110. A shaft plug 118 is set at the top of the oil supply channel 116. The inner hole diameter of the shaft plug 118 is set to D1, and the diameter of the bottom oil suction port 1191 of the oil supply channel 116 is set to D2. The time from the initial startup of the compressor to the stable oil supply of each friction pair is the oiling time, and the oiling time will become longer as the D1 / D2 ratio becomes smaller. The longer the time, the longer the time that the bearings and other friction pairs are in dry friction and mixed friction, which will easily cause wear of the various friction pairs of the compressor during the startup stage.

[0123] In addition, when the compressor is running at high speed under heavy working conditions, lubricating oil droplets will enter the air conditioning refrigeration system along with the high-pressure refrigerant, which will lead to a reduction in the lubricating oil in the compressor, increase the risk of dry friction between the parts, and reduce the operating reliability of the compressor. If the oil discharge rate is high, the air conditioner will have to return oil frequently after a period of time. At the same time, because the air conditioning refrigeration system is an inner spiral design, the lubricating oil attached to the copper tube will also reduce the heat exchange capacity of the heat exchanger.

[0124] In order to solve the above technical problems, in some embodiments of the present disclosure, the oil supply channel 116 and the shaft plug 118 of the eccentric crankshaft 110 are optimized to shorten the oiling time during the initial startup of the compressor, reduce the wear of each friction pair, and reduce the oil discharge rate.

[0125] For example, refer to Fig.11 The oil supply channel 116 includes a first sub-oil supply channel 1161 and a second sub-oil supply channel 1162 which are connected to each other. The inner diameter of the first sub-oil supply channel 1161 is D3, the inner diameter of the second sub-oil supply channel 1162 is D4, and the diameter of the bottom oil suction port of the second sub-oil supply channel 1162 is D2.

[0126] In some embodiments, reference Figure 4 The oiling blade 117 is arranged in the second sub-oil supply channel 1162 to provide oil delivery power. When the compressor is running, the motor 13 drives the eccentric crankshaft 110 to rotate, and the oiling blade 117 rotates synchronously with the eccentric crankshaft 110, and negative pressure is formed at the oil suction port at the bottom of the eccentric crankshaft 110. The lubricating oil in the oil pool enters the oil supply channel 116 through the oil suction port and then flows to each friction pair.

[0127] The shaft plug 118 is disposed in the first sub-oil supply channel 1161 . The shaft plug 118 is disposed close to the top of the first sub-oil supply channel 1161 . The inner hole diameter of the shaft plug 118 is D1 .

[0128] From the initial startup of the compressor to the stable oil supply to each friction pair, the lubrication time will become longer as the D1 / D2 ratio becomes smaller. Setting D1 / D2=[0.13, 0.65] can achieve the effect of short initial lubrication time.

[0129] Fig.21 The figure shows the relationship between the initial oiling time of the compressor and D1 / D2. Fig.21 , when D1 / D2 increases from 0.13 to 0.65, the initial oiling time decreases from 1s to about 0.56s.

[0130] The oil discharge rate of the compressor is related to the value of (D2+D1) / (D4-D3). The larger the value of (D2+D1) / (D4-D3), the higher the oil discharge rate. Set (D2+D1) / (D4-D3) = [0.3, 1.19] to achieve the effect of reducing the oil discharge rate.

[0131] Fig. 22 The figure shows the relationship between oil discharge rate and (D2+D1) / (D4-D3). Fig. 22 , when (D2+D1) / (D4-D3) decreases from 1.19 to 0.3, the oil discharge rate decreases from about 2.1 to about 0.7.

[0132] In some embodiments, reference Fig.11, an oil suction pipe 119 is provided at the bottom of the second sub-oil supply channel 1162, and the oil suction pipe 119 is inserted in the second sub-oil supply channel 1162. The oil suction pipe 119 is inserted at the bottom of the second sub-oil supply channel 1162 with interference fit, so as to be fixedly mounted on the eccentric crankshaft 110. An oil suction port 1191 is provided at the bottom of the oil suction pipe 119, and the diameter of the oil suction port is D2. The diameter of the oil suction port 1191 is smaller than the inner diameter of the oil suction pipe 119. That is, the bottom of the oil suction pipe 119 is a shrinkage structure.

[0133] In some embodiments, if the diameter of the oil suction port 1191 is large, the amount of oil entering the oil supply channel 116 can be increased, but the oil pump head is low, resulting in a low oil rise height. If the diameter of the oil suction port 1191 is small, the amount of oil entering the oil supply channel 116 is reduced, but the oil pump head becomes higher, which is conducive to oil supply at low speeds.

[0134] In some embodiments of the present disclosure, the ratio between the diameter D2 of the oil suction port 1191 and the inner diameter D4 of the second sub-oil supply channel 1162 is set in the range of [0.3, 1]. Within this range, it helps to improve the oil supply effect of the compressor.

[0135] In some embodiments, when the compressor is running at a low frequency, the oil absorption of the eccentric crankshaft 110 is small, and only a small amount of oil in the oil pool migrates to the upper space of the motor 13 in the compressor and the outside of the compressor. At this time, the oil level in the oil pool can be maintained at a relatively high level. When the compressor is running at a high frequency, the oil absorption of the eccentric crankshaft 110 becomes larger, and a large amount of oil will be transferred to the upper space of the motor 13 and the outside of the compressor, and the oil level in the oil pool will be greatly reduced. Therefore, when the compressor is running at a high speed, increasing the depth of the oil suction port of the eccentric crankshaft 110 inserted into the oil pool is an important measure to maintain the oil level.

[0136] In a twin-cylinder compressor, refer to Figure 4 , the height of the first cylinder 122 is H2, the height distance between the central axis of the air inlet of the first cylinder 122 and the oil suction port is H1, H1 / H2=h. The rated limit operating frequency of the compressor is t, t / h=[20,80]. This range can ensure the oil supply of the eccentric crankshaft 110 and meet the oil supply demand of the friction pair.

[0137] In a single-cylinder compressor, the height of the cylinder is H2, the height distance between the central axis of the air inlet of the cylinder and the oil suction port is H1, H1 / H2=h, and the rated limit operating frequency of the compressor is t, t / h=[20,80]. This range can ensure the oil supply of the eccentric crankshaft 110 and meet the oil supply demand of the friction pair.

[0138] [Eccentric crankshaft exhaust structure]

[0139] When the compressor is stationary, the oil level inside the eccentric crankshaft 110 is the same as that outside. At this time, a part of the upper part of the eccentric crankshaft 110 is refrigerant gas. After the compressor starts running, this part of the gas will be discharged from the eccentric crankshaft 110 first, and then the oil in the bottom oil pool can be sucked in. Therefore, it is necessary to open an exhaust hole on the eccentric crankshaft 110 for exhaust. However, when the speed of the compressor gradually increases, the oil level inside the eccentric crankshaft 110 will increase. At this time, the engine oil will fill the internal space, and at the same time, a part of the oil will be discharged from the exhaust hole. This part of the oil will flow to the upper part of the motor 13 with the refrigerant gas, and may eventually flow out of the compressor, increasing the oil discharge rate of the compressor and affecting reliability. Therefore, the ideal function of the exhaust hole is to only exhaust air, not oil. Usually, the compressor minimizes the discharge of oil by reducing the aperture of the exhaust hole, but it cannot be completely avoided and the effect is not good.

[0140] In order to solve the above technical problems, in some embodiments of the present disclosure, the exhaust hole on the eccentric crankshaft 110 is structurally improved to effectively prevent the oil from being discharged through the exhaust hole when the compressor is running at high speed, thereby reducing the oil discharge rate.

[0141] For example, refer to Fig. 12A and 12B An exhaust passage 410 is provided in the eccentric crankshaft 110 . The exhaust passage 410 is communicated with the oil supply passage 116 . The exhaust passage 410 is configured to discharge the gas in the oil supply passage 116 .

[0142] In some embodiments, an exhaust passage 410 is disposed in the first shaft segment 111 , and the exhaust passage 410 is in communication with the first oil supply sub-passage 1161 .

[0143] A channel member 420 is disposed in the exhaust channel 410. An auxiliary channel 423 is formed in the channel member 420. The auxiliary channel 423 is communicated with the exhaust channel 410, and the inner diameter of the auxiliary channel 423 decreases along the exhaust direction of the gas in the exhaust channel 410.

[0144] For example, the channel member 420 is a metal structural member, and the channel member 420 is interference fitted into the exhaust channel 410 to achieve fixed installation of the channel member 420 in the exhaust channel 410 .

[0145] A moving member 430 is disposed in the auxiliary channel 423 . The moving member 430 is configured to move along the auxiliary channel 423 to open or close the auxiliary channel 423 .

[0146] The moving part 430 is a metal ball, and the metal ball is located in the auxiliary channel 423. The metal ball moves along the auxiliary channel 423. When the metal ball moves to the first position, the metal ball closes the auxiliary channel 423, and the oil cannot be discharged through the exhaust channel 410 and the auxiliary channel 423. When the metal ball moves to the second position, the metal ball opens the auxiliary channel 423, and the refrigerant gas is discharged through the exhaust channel 410 and the auxiliary channel 423.

[0147] The auxiliary channel 423 is closed or opened by the movement of the moving part 430 in the auxiliary channel 423. Since the auxiliary channel 423 is connected to the exhaust channel 410, the exhaust channel 410 is closed or opened. Combined with the operating frequency of the compressor, the compressor can be exhausted when it runs at a low frequency and not discharged when it runs at a high frequency.

[0148] In some embodiments, reference Fig.13 and 14 The inner diameter of the auxiliary channel 423 decreases in the direction from the first end 421 to the second end 422 , the outer diameter of the moving part 430 is larger than the lower limit of the inner diameter of the auxiliary channel 423 , and the outer diameter of the moving part 430 is smaller than the upper limit of the inner diameter of the auxiliary channel 423 .

[0149] The auxiliary channel 423 is a conical channel structure, and the moving part 430 is a spherical structure. The outer diameter of the moving part 430 is smaller than the inner diameter of the first end 421 of the auxiliary channel 423 and larger than the inner diameter of the second end 422 .

[0150] For example, when the moving part 430 moves toward the second end 422 close to the auxiliary channel 423, when the outer wall of the moving part 430 is in contact with the inner wall of the auxiliary channel 423, the auxiliary channel 423 is blocked, thereby preventing oil from being discharged through the exhaust channel 410 when the compressor runs at a high frequency.

[0151] For another example, when the moving part 430 moves toward the first end 421 close to the auxiliary channel 423, when there is a gap between the outer wall of the moving part 430 and the inner wall of the auxiliary channel 423, the auxiliary channel 423 is opened, and the refrigerant gas can be discharged through the exhaust channel 410.

[0152] In some embodiments, reference Fig.13 and Fig.14 A plurality of stoppers 424 are disposed on the channel member 420 , and the plurality of stoppers 424 are arranged at intervals along the circumference of the auxiliary channel 423 . The plurality of stoppers 424 are configured to limit the moving member 430 within the auxiliary channel 423 .

[0153] In some embodiments, the stopper 424 is a plurality of rib structures, the stopper 424 and the channel member 420 are an integral structure, and the stopper 424 is integrally formed at the first end 421 of the channel member 420. When the moving member 430 moves to the first end 421 of the channel member 420, the stopper 424 limits the moving member 430 to prevent the moving member 430 from falling out of the auxiliary channel 423.

[0154] When installing the moving part 430 into the auxiliary channel 423, the moving part 430 is inserted into the auxiliary channel 423 from the first end 421 of the channel part 420. Since the stopper 424 is a rib structure, the rib structure is deformed by force to allow the moving part 430 to be inserted into the auxiliary channel 423 through the first end 421 with a larger diameter. After the moving part 430 is inserted, the rib structure is reset to limit the moving part 430.

[0155] In some embodiments, a plurality of stoppers 424 are disposed at the first end 421 of the channel member 420, and the stoppers 424 include an integrally structured first extension segment 4241 and a second extension segment 4242, the first extension segment 4241 and the second extension segment 4242 being disposed at an angle, for example, at a 90-degree angle. The first extension segment 4241 extends from the first end 421 of the channel member 420 in a direction away from the channel member 420, and the second extension segment 4242 extends from the first extension segment 4241 in an axial direction close to the auxiliary channel 423.

[0156] The second extended section 4242 forms a limiting claw to limit the moving member 430 to prevent the moving member 430 from escaping from the first end 421 of the channel member 420 .

[0157] In some embodiments, referring to FIG. 12 , the exhaust passage 410 extends obliquely upward from the oil supply passage 116 .

[0158] When the operating frequency of the compressor is lower than the set frequency, the moving member 430 approaches the first end 421 of the channel member 420 to open the auxiliary channel 423 .

[0159] In some embodiments, when the operating frequency of the compressor is lower than the set frequency, the diagonal component f' of the centrifugal force of the moving part 430 is lower than the diagonal component g' of the gravity. At this time, the moving part 430 is still at the bottom, that is, the moving part 430 is located at the first end 421 of the channel part 420. Since the outer diameter of the moving part 430 is smaller than the inner diameter of the first end 421 of the channel part 420, there is a gap between the moving part 430 and the auxiliary channel 423, and the refrigerant gas flows out of the eccentric crankshaft 110 through the auxiliary channel 423.

[0160] When the operating frequency of the compressor is greater than the set frequency, the moving member 430 approaches the second end 422 of the channel member 420 to close the auxiliary channel 423 .

[0161] In some embodiments, when the operating frequency of the compressor is greater than the set frequency, the diagonal component f' of the centrifugal force of the moving part 430 is greater than the diagonal component g' of the gravity. At this time, the moving part 430 will move upward, that is, move toward the second end 422 of the channel part 420. The moving part 430 will block the auxiliary channel 423, and the oil will not be able to be discharged from the auxiliary channel 423.

[0162] The inclination angle of the auxiliary channel 423 needs to be designed in association with the gravity of the moving part 430 and the frequency h of the compressor exhaust stopping and oil discharge starting.

[0163] In some embodiments, reference Fig. 12A , Fig.13 and Fig.14 The exhaust passage 410 extends horizontally from the oil supply passage 116 , and correspondingly, the auxiliary passage 423 also extends horizontally, and a spring 440 is disposed in the auxiliary passage 423 .

[0164] When the operating frequency of the compressor is lower than the set frequency, the centrifugal force of the moving part 430 is lower than the elastic force of the spring 440 , and the spring 440 pushes the moving part 430 toward the first end 421 close to the channel part 420 . There is a gap between the moving part 430 and the auxiliary channel 423 , and the refrigerant gas flows out of the eccentric crankshaft 110 through the auxiliary channel 423 .

[0165] When the operating frequency of the compressor is greater than the set frequency, the centrifugal force of the moving part 430 is greater than the elastic force of the spring 440, and the moving part 430 moves toward the second end 422 close to the channel part 420. The spring 440 is squeezed by the moving part 430 and contracts. Since the outer diameter of the moving part 430 is greater than the inner diameter of the second end 422 of the auxiliary channel 423, the moving part 430 closes the auxiliary channel 423, and the engine oil cannot be discharged from the auxiliary channel 423.

[0166] The elastic coefficient k of the spring 440 needs to be designed in association with the frequency h of the end of exhaust and the start of oil discharge.

[0167] In some embodiments, the exhaust passage 410 exhausts the gas into the space between the motor 13 and the bearing. Taking a two-cylinder compressor as an example, the exhaust passage 410 exhausts the gas into the space between the motor 13 and the first bearing 152.

[0168] In some embodiments, an auxiliary channel 423 is provided in the exhaust channel 410 . The auxiliary channel 423 is connected to the exhaust channel 410 . The inner diameter of the auxiliary channel 423 decreases along the exhaust direction of the gas in the exhaust channel 410 .

[0169] A moving member 430 is disposed in the auxiliary channel 423. The moving member 430 is configured to move along the auxiliary channel 423 to open or close the auxiliary channel 423.

[0170] When the operating frequency of the compressor is greater than the set frequency, the moving part 430 closes the auxiliary channel 423 to achieve low-frequency exhaust.

[0171] When the operating frequency of the compressor is lower than the set frequency, the moving part 430 opens the auxiliary channel 423 to avoid high-frequency oil discharge.

[0172] The auxiliary channel 423 is formed by the channel member 420 , that is, the channel member 420 is fitted into the exhaust channel 410 by interference, and a through auxiliary channel 423 is formed in the channel member 420 , and the auxiliary channel 423 is in communication with the exhaust channel 410 .

[0173] In some embodiments, the inner diameter of the first shell of the compressor is greatly affected by the displacement. Generally, the larger the displacement, the larger the inner diameter of the first shell. Moreover, when the displacement is larger, in order to reduce the oil discharge rate and the refrigerant gas pressure loss, the inner diameter of the exhaust pipe also needs to be larger.

[0174] Based on this, the inner diameter of the first shell 11 is set to D14. Figure 1 and Figure 3 An exhaust pipe 12 is disposed on the top of the first shell 11. The inner diameter of the exhaust pipe 12 is D16, and D1 / D16=[8, 12]. Within this range, the oil discharge rate of the compressor and the pressure loss of the refrigerant gas can be reduced.

[0175] [Motor structure]

[0176] In some embodiments, the inner diameter of the first shell 11 determines the maximum size of the motor 13. If the outer diameter of the rotor 320 is too large, the amount of stator 310 core used will be reduced, the magnetic flux density of the stator 310 core will be high, and the iron loss of the motor 13 will be high, which will have an adverse effect on the efficiency of the motor 13; at the same time, as a moving body, if the rotor 320 is large in size, it will have an adverse effect on the noise. If the outer diameter of the rotor 320 is small, the amount of magnets used will be small, the permanent magnet flux will be low, and the noise will be low, but it will have an adverse effect on the efficiency and high power of the motor 13. In addition, the stator and rotor stack thickness of the motor 13, as a vertical dimension, acts together with the inner diameter of the first shell 11 and the outer diameter of the rotor 320, affecting the volume of the motor 13 and affecting the noise and performance of the motor 13.

[0177] Based on this, in some embodiments of the present disclosure, the inner diameter of the housing, the height of the stator and rotor, and the outer diameter of the rotor 320 are optimized to improve the efficiency of the motor 13 and reduce noise.

[0178] In some embodiments, reference Fig.16 , the inner diameter of the first shell 11 is D14, refer to Figure 6 and Figure 7The stack height of the rotor 320 is H8, the outer diameter of the rotor 320 is D9, and D14 / (H8×D9)=(0.028, 0.032). This range is beneficial for reducing the noise of the compressor while improving the efficiency of the motor 13. Fig.34 This is the relationship diagram between D14 / (H8×D9) and compressor noise and motor efficiency.

[0179] In some embodiments, the gap between the stator 310 and the rotor 320 of the motor 13 and the stacking thickness are related to the size of the magnetic flux density of the motor 13. A large magnetic flux density of the motor 13 will cause the motor 13 to have a large magnetostriction, thereby causing the motor 13 to have a large electromagnetic noise. A small magnetic flux density will cause the motor 13 to have a low efficiency.

[0180] The gap between the stator 310 and the rotor 320 of the motor 13 and the stacking thickness and the total height of the first housing 11 of the compressor affect the oiling and oil return of the compressor. If the height of the motor 13 accounts for a small proportion of the overall height of the first housing 11, the proportion of the upper and lower cavities of the motor 13 is large, and it is easier to guide the oil in the motor section; if the gap between the stator 310 and the rotor 320 is small, and the stacking thickness of the stator and rotor 320 is high, the motor section is long and it is difficult to guide the oil, which will cause too much oil to accumulate in the upper cavity of the motor 13.

[0181] Based on this, in some embodiments, refer to Figure 1 , the height of the first housing 11 is H16, refer to Figure 7 , the stack height of the rotor 320 is H8, the gap between the stator 310 and the rotor 320 is S, H16 / (H8×S)=(6.5, 9.5), and this range is beneficial to limiting and balancing the noise of the compressor, improving efficiency, and improving the problem of oil accumulation in the upper cavity of the motor 13. Fig.35 This is the relationship diagram between H16 / (H8×S) and motor noise and efficiency.

[0182] In some embodiments, the smaller the thickness of the silicon steel sheet of the motor 13, the lower the iron loss, the higher the efficiency, the greater the centrifugal force at high speed, and the silicon steel sheet of the rotor 320 is prone to breakage.

[0183] Based on this, the silicon steel sheet thickness of the rotor 320 / the silicon steel sheet thickness of the stator 310 is set to [1.15, 1.75], which ensures the efficiency of the motor 13 while improving the anti-fracture ability of the rotor 320.

[0184] In some embodiments, in the rotor 320 compressor, the efficiency improvement of the permanent magnet synchronous motor is inversely proportional to the motor loss. The lower the motor loss, the higher the motor efficiency. The motor loss is mainly composed of the copper loss of the copper wire and the iron loss of the silicon steel. Under the premise of keeping the motor cost basically unchanged, the change of the motor shape will lead to changes in the copper loss and iron loss of the motor. For example, increasing the stator slot area will lead to an increase in the amount of copper used and a decrease in the weight of silicon steel, and the copper loss and iron loss of the motor will change.

[0185] Based on this, the weight of the stator 310 is set to G1, the weight of the rotor 320 is set to G2, G1 / G2=(3.2, 5.2), and this range is beneficial to reducing the copper loss and iron loss of the motor 13 and improving the efficiency of the motor 13.

[0186] In some embodiments, when the compressor uses a high-speed motor (e.g., the maximum motor speed can reach more than 140rps), the back electromotive force will be low at a low speed (e.g., a speed of 5-15rps), causing the compressor to run unsteadily or fail to run. In order to meet the design requirements of high speed, the height of the motor will increase, thereby increasing the length of the eccentric crankshaft 110, which will aggravate the deformation of the eccentric crankshaft 110 and easily cause bore sweeping.

[0187] In order to solve the above technical problems, in some embodiments of the present disclosure, the diameter of the copper wire of the motor 13 is set to d1, the thickness of the silicon steel sheet of the motor 13 is set to d2, and d1 / d2=(1.5, 8].

[0188] It should be noted that the gap between the stator 310 and the rotor 320 is set to S, the height of the motor 13 is d4, and d4 / S=(50, 150].

[0189] The above interval setting can meet the design requirements of high speed and low speed of the compressor while ensuring the efficiency of the compressor. Fig.36 The figure shows the relationship between d1 / d2 and motor efficiency and speed. Fig.37 The figure shows the relationship between d4 / S, motor efficiency, and deformation of the eccentric crankshaft 110.

[0190] In some embodiments, reference Figure 3 An exhaust pipe 12 is disposed on the top of the first shell 11 .

[0191] Reference Figure 1 The compressor body 1 also includes an oil equalizing pipe 15, one end of which is connected to the first shell 11 and communicates with the inner cavity of the first shell 11, and the other end of the oil equalizing pipe 15 is connected to the exhaust pipe 12. The connection position of the oil equalizing pipe 15 and the first shell 11 is lower than the first bearing 152.

[0192] The distance between the connection position of the oil equalizing pipe 15 and the first housing 11 and the bottom of the first housing 11 is H17. The distance between the central axis of the air intake of the first cylinder 122 and the bottom of the first housing 11 is H18, H17 / H18=[0.9, 1.2]. This range helps to improve the COP efficiency of the compressor.

[0193] In some embodiments, reference Fig.15 The height of the stator 310 is H19, the outer diameter of the stator 310 is D15, and a plurality of convex portions 311 and concave portions 312 are arranged at intervals on the outer peripheral wall of the stator 310. The convex portion 311 is fixedly connected to the inner wall of the first shell 11. The area of ​​the plurality of convex portions 311 is S1, S1 / π×D15×H19=[0.35, 0.5]. Within this range, the efficiency of the motor 13 and optical character recognition (OCR) are taken into consideration.

[0194] In some embodiments, reference Figure 1 and Figure 3 The inner diameter of the first shell 11 is D14, the exhaust pipe 12 is arranged on the top of the first shell 11, the inner diameter of the exhaust pipe 12 is D16, the height of the distance from the bottom end of the exhaust pipe 12 to the top end of the eccentric crankshaft 110 is H20, D14 / (D16×H20)=(3.81, 4.62), and this range is beneficial to reducing the oil discharge rate of the compressor.

[0195] [Compressor body]

[0196] The amplitude of the compressor has a great contribution to the noise of the outdoor unit. Usually, the vibration noise of the compressor is reduced by setting a vibration-damping foot at the bottom of the compressor, which is passive vibration reduction and has poor effect.

[0197] In order to solve the above technical problems, in some embodiments of the present disclosure, the vibration of the compressor is effectively suppressed by actively reducing the vibration of the compressor, thereby reducing the vibration noise of the compressor and the air conditioner.

[0198] For example, refer to Figure 2A and Figure 2B A sensor 510 (acceleration sensor) is disposed on the circumferential wall of the first shell 11 , and the sensor 510 is configured to obtain a tangential vibration time domain signal of the first shell 11 .

[0199] An exciter 520 (inertial exciter) is provided on the circumferential wall of the first shell 11. The exciter 520 is configured to emit an excitation signal of equal amplitude and opposite phase according to the tangential vibration time domain signal obtained by the sensor 510 to reduce the vibration of the compressor.

[0200] The sensor 510 and the vibrator 520 are fixedly mounted to the outside of the circumferential wall of the first shell 11 , which is convenient for assembly and disassembly, does not occupy the internal space of the first shell 11 , and does not interfere with the installation of the internal motor 13 and the compression mechanism 14 .

[0201] The exciter 520 generates an excitation signal with the same amplitude and opposite phase as the first housing 11 to actively reduce vibration of the compressor and effectively suppress the vibration of the compressor.

[0202] In some embodiments, the compressor includes a processor 530 (data processor), which is configured to receive the tangential vibration time domain signal acquired by the sensor 510 and transmit the time domain signal to the exciter 520 after the phase is reversed by 180°.

[0203] The air conditioner further includes a controller, which includes a processor 530. The processor 530 may include a central processing unit (CPU), a microprocessor (microprocessor), or an application specific integrated circuit (ASIC), and may be configured to perform corresponding operations described in the controller when the processor 530 executes a program stored in a non-transitory computer readable medium coupled to the controller.

[0204] It should be noted that the controller is coupled to the sensor 510 and the exciter 520 respectively.

[0205] When the compressor is working, the sensor 510 obtains the tangential vibration time domain signal of the first shell 11 and transmits it to the data processor 530. Using the time-frequency analysis method, the phase of the time domain signal is reversed by 180°, and then the signal is transmitted to the exciter 520. The exciter 520 sends out an excitation signal with the same amplitude and opposite phase as the compressor, so that the vibration of the compressor is effectively suppressed, realizing active vibration reduction and noise reduction.

[0206] [Structure of gas-liquid separator]

[0207] The gas-liquid separator 2 protects the compressor body 1, but it is also one of the important sources of noise generation and radiation. On the one hand, the compressor body 1 is a vertical rotor type. If there is no gas-liquid separator, its rotation center should be the geometric center of the compressor body 1; but if there is a gas-liquid separator 2, the center of mass of the compressor body 1 deviates from the rotation center, which leads to increased compression vibration. Since the rotation center of the gas-liquid separator 2 is the farthest, the vibration acceleration at the edge of the gas-liquid separator 2 is also the largest. On the other hand, according to the moment of inertia formula I = mr 2It can be seen that when the mass of an object cannot be increased, the rotational inertia of the compressor body 1 can be increased by increasing the rotation radius r, and the larger the rotational inertia, the more stable the rotation of the object.

[0208] Therefore, there is a certain proportional relationship between the distance between the rotation center of the gas-liquid separator 2 and the rotation center of the compressor body 1. By properly optimizing the proportional relationship, the effect of reducing the vibration and noise of the compressor can be achieved.

[0209] Based on this, in some embodiments of the present disclosure, the diameter and height between the gas-liquid separator 2 and the compressor body 1 are optimized to reduce the vibration and noise of the compressor.

[0210] For example, refer to Figure 1 The outer diameter of the first shell 11 of the compressor body 1 is D12, and the height of the compressor body 1 is H12. The outer diameter of the second shell 21 of the gas-liquid separator 2 is D13, and the height of the gas-liquid separator 2 is H13.

[0211] It should be noted that D13 / D12=(0.45, 0.56), H13 / H12=(0.4, 0.6), and this range is helpful to reduce the vibration of the gas-liquid separator 2.

[0212] In some embodiments, reference Fig.16 The compressor further includes a bracket 200, and the bracket 200 is configured to connect the first shell 11 and the second shell 21. The bracket 200 is welded to the first shell 11, the number of welding points between the bracket 200 and the first shell 11 is n, the inner diameter of the first shell 11 is D14, the height of the first shell 11 is H16, D14 / n×10=(6, 7.5), H16 / n×20=(4.5, 6).

[0213] The above arrangement can effectively increase the frequency of the rigid body torsional mode of the gas-liquid separator 2 without increasing the process flow and welding costs, thereby reducing the probability of abnormal noise generation in the compressor.

[0214] In some embodiments, reference Figures 16 to 18 The compressor includes two symmetrically arranged brackets 200 , and the two brackets 200 are configured to connect the first shell 11 and the second shell 21 .

[0215] The bracket 200 includes a bracket part 210, a bracket part 220, a bracket part 3 230 and a bracket part 4 240 connected in sequence. The bracket part 1 210 and the bracket part 3 230 are located on the same side of the bracket part 220, and the bracket part 220 and the bracket part 4 240 are located on different sides of the bracket part 3 230. The bracket part 220 is adapted to the outer contour of the second shell 21 and is fixedly connected, such as by welding. The bracket part 1 210 and the bracket part 3 230 extend between the first shell 11 and the second shell 21 respectively. The bracket part 1 210 and the bracket part 4 240 are fixedly connected to the first shell 11 respectively, such as by welding. The length of the bracket part 210 is greater than the length of the bracket part 3 230, and the two bracket parts 4 240 are close to each other.

[0216] For each bracket 200, by welding the first bracket part 210 and the fourth bracket part 240 to the first shell 11, two fixations with the first shell 11 are achieved. Then, when two brackets 200 are used together, there are four fixations on the first shell 11, which improves the connection stability between the bracket 200 and the first shell 11.

[0217] When the two brackets 200 are used together, the two bracket second parts 220 together clamp the gas-liquid separator 2 to improve the connection stability between the bracket 200 and the second shell 21 .

[0218] In some embodiments, an opening 250 is disposed on the support portion 210 , and the opening 250 extends along the length direction of the support portion 210 . The width of the opening 250 is H14 , and the length of the opening 250 is L1 , where H14 / L1=(0, 0.82].

[0219] By changing the size of the opening 250 , the connection stiffness of the gas-liquid separator 2 can be changed, which is beneficial to optimizing the natural frequency and obtaining the required natural frequency.

[0220] In some embodiments, the width of the second bracket portion 220 is W3, the outer contour radius of the second shell 21 is R2, and the range of W3 / R2 is [1.4, 2.2]. Within this range, it is helpful to improve the natural frequency of the gas-liquid separator 2.

[0221] In some embodiments, the distance from the intersection of the first bracket 210 and the second bracket 220 to the symmetry plane of the two brackets 200 is W1, the distance from the third bracket 230 to the symmetry plane of the two brackets 200 is W2, the outer contour radius of the second shell 21 is R2, the outer contour radius of the first shell 11 is R1, (W1 / R2)×(W2 / R1)>0.3.

[0222] Within the above range, the double torsional frequency of the gas-liquid separator 2 tends to be stable, and the fixed top frequency is increased to above 510 Hz, which is suitable for a twin-cylinder compressor with a maximum speed of 180 rps.

[0223] In some embodiments, the bracket part 210 includes a bracket part one section 211 and a bracket part two section 212 of an integrated structure, the bracket part one section 211 extends obliquely outward from the first end of the bracket part two section 212, the bracket part one section 211 is adapted and fixedly connected to the first shell 11, and the second end of the bracket part two section 212 is intersected and connected with the bracket part two 220.

[0224] In some embodiments, reference Fig.19 and Fig. 20 The bracket 200 includes a bracket main body 260, and bracket extensions 270 are symmetrically arranged at opposite ends of the bracket main body 260. The bracket main body 260 is adapted to the outer contour of the first shell 11 and is fixedly connected, for example, by welding.

[0225] In some embodiments, the integral structure of the bracket extension 270 includes a first extension section 271 and a second extension section 272. The first extension section 271 is connected between the bracket body 260 and the second extension section 272. The second extension section 272 is fixedly connected to the outer contour of the second housing 21, such as by welding.

[0226] For example, the outer contour radius of the first shell 11 is R1, the outer contour radius of the second shell 21 is R2, the distance between the extension section 271 and the symmetry plane of the bracket 200 is W4, 2W4 / (R1+R2)=[0.35, 0.55]. Within this range, it is helpful to reduce the vibration of the gas-liquid separator 2.

[0227] It should be noted that any one of the technical solutions disclosed in the present disclosure can solve one or more of the above-mentioned technical problems and achieve certain disclosure purposes to a certain extent; multiple technical disclosures can also be combined into an overall solution to solve one or more of the above-mentioned technical problems and achieve certain disclosure purposes; some technical disclosures can also be selected to be combined into an overall solution, while adopting related technologies and deteriorated solutions, but the deterioration trend can be compensated by the means disclosed in this technology, and one or more of the above-mentioned technical problems can be solved to a certain extent as a whole and achieve certain disclosure purposes; each technical disclosure combined into a complete technical solution constitutes an organic and inseparable overall solution, which solves technical problems as a whole and achieves certain disclosure purposes.

[0228] Any technical disclosure in the present disclosure, as well as the recombination of multiple technical disclosures, can form a complete technical solution and can solve one or more of the above-mentioned technical problems and achieve the purpose of disclosure. They all belong to the content of the present disclosure and belong to the content that is directly and unambiguously determined based on the content of the present disclosure.

[0229] Those skilled in the art will understand that the scope of the present disclosure is not limited to the above specific embodiments, and certain elements of the embodiments may be modified and replaced without departing from the spirit of the present application. The scope of the present application is limited by the appended claims.

Claims

1. A compressor, comprising: case; a compression mechanism disposed in the shell, the compression mechanism being configured to compress a refrigerant; Characterized in that the compression mechanism comprises: An eccentric crankshaft, comprising a first shaft section, wherein the diameter of the first shaft section is D5; a first bearing, sleeved on the first shaft section, the first bearing comprising a first sub-bearing and a second sub-bearing, the first sub-bearing being arranged at the bottom of the second sub-bearing, an annular groove with a bottom opening being arranged on the first sub-bearing, the annular groove surrounding the first shaft section, the height of the annular groove being H3, the inner diameter of the annular groove being D6, and the outer diameter of the annular groove being D7; Among them, (D7-D6) / D5=[0.09, 0.13], (D7-D6) / H3=[0.2, 0.6].

2. The compressor according to claim 1, characterized in that The outer diameter of the shaft shoulder of the second sub-bearing is D11, and the height of the first bearing is H4; The first bearing is welded to the inner wall of the housing, and the height distance between the welding point of the first bearing and the top end of the second sub-bearing is H5; Among them, D5 / D11×H5 / H4>0.

45.

3. The compressor according to claim 1, characterized in that The first bearing is welded to the inner wall of the housing, and the height distance between the welding point of the first bearing and the top end of the second sub-bearing is H5; The height of the first shaft section is H6, and the outer diameter of the shoulder of the second sub-bearing is D11; Among them, H5 / H6×D5 / D11>0.

2.

4. The compressor according to claim 1, characterized in that The eccentric crankshaft comprises a first shaft segment, a first eccentric shaft segment, a connecting shaft segment, a second eccentric shaft segment and a second shaft segment which are connected in sequence; A first bearing is sleeved on the first shaft section, a first cylinder is sleeved on the first eccentric shaft section, a middle partition is sleeved on the connecting shaft section, a second cylinder is sleeved on the second eccentric shaft section, and a second bearing is sleeved on the second shaft section; The height of the middle partition is H7, the height of the first cylinder is H2, and the height of the first cylinder is the same as that of the second cylinder; Among them, H7 / H2=[0.22, 0.35].

5. The compressor according to any one of claims 1 to 4, characterized in that An oil supply passage is formed inside the eccentric crankshaft, and the oil supply passage extends along the axial direction of the eccentric crankshaft; An exhaust passage is formed inside the eccentric crankshaft, the exhaust passage is communicated with the oil supply passage, and the exhaust passage is configured to discharge the gas in the oil supply passage; The compression mechanism also includes: A channel member is disposed in the exhaust channel, wherein a through auxiliary channel is formed in the channel member, the auxiliary channel is communicated with the exhaust channel, and the inner diameter of the auxiliary channel decreases along the exhaust direction of the gas in the exhaust channel; A moving member is disposed in the auxiliary channel, and the moving member is configured to move along the auxiliary channel to open or close the auxiliary channel.

6. The compressor according to claim 5, characterized in that The inner diameter of the auxiliary channel decreases from the first end to the second end, the outer diameter of the moving part is larger than the lower limit of the inner diameter of the auxiliary channel, and the outer diameter of the moving part is smaller than the upper limit of the inner diameter of the auxiliary channel.

7. The compressor according to claim 6, characterized in that The exhaust passage extends obliquely upward from the oil supply passage; When the operating frequency of the compressor is less than the set frequency, the moving member is close to the first end of the channel member to open the auxiliary channel; When the operating frequency of the compressor is greater than a set frequency, the moving member is close to the second end of the channel member to close the auxiliary channel.

8. The compressor according to claim 6, characterized in that The exhaust passage extends horizontally from the oil supply passage, and a spring is arranged in the auxiliary passage; When the operating frequency of the compressor is less than the set frequency, the spring pushes the moving member toward the first end close to the channel member to open the auxiliary channel; When the operating frequency of the compressor is greater than the set frequency, the moving part moves toward the second end close to the channel part to close the auxiliary channel, and the spring is squeezed by the moving part to shrink.

9. The compressor according to claim 5, characterized in that A bearing is arranged on the eccentric crankshaft; The compressor further includes a motor, which is disposed on the eccentric crankshaft, and the exhaust passage discharges gas into a space between the motor and the bearing.

10. An air conditioner, comprising a compressor, an evaporator, a condenser and a throttling device, characterized in that: The compressor is the compressor according to any one of claims 1 to 9.

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