Rotary compressor and refrigeration apparatus

Abstract

Disclosed in the present application are a rotary compressor (1000) and a refrigeration apparatus. The rotary compressor comprises: a housing (10); an electric motor (100), which comprises a stator (20), a rotor (30) and a crankshaft (40), wherein the stator is sleeved on the rotor, the crankshaft is connected to the rotor, the stator comprises a stator core (21), and a plurality of tangential flow channels (212) are defined between an outer periphery of the stator core and the housing; and a compression component (200), which comprises at least one compression cavity (201), wherein the total area of the cross sections of the plurality of tangential flow channels is defined as S1mm2, the height of the stator core in the axial direction of the crankshaft is defined as H1mm, and the total volume of the compression cavity is defined as Vmm3, which satisfy formula (1).

Description

Rotary compressor and refrigeration equipment

[0001] Cross-reference to related applications

[0002] The present application is based on and claims priority to Chinese Patent Application No. 202411061516.7 and 202421869974.9, filed on August 2, 2024, the entire contents of which are incorporated herein by reference. TECHNICAL FIELD

[0003] The present application relates to the technical field of compressors, in particular to a rotary compressor and a refrigeration equipment. BACKGROUND

[0004] When the rotary compressor pumps gas, the lubricating oil in the rotary compressor will be pumped out, but the stator cut edge of the motor and the rotary compressor shell define a cut edge flow channel, which can provide lubricating oil backflow when the rotary compressor is working, so as to reduce the loss of lubricating oil. In the related art, the area of the stator cut edge of the motor changes with the number of stator slots, so that the size of the cut edge flow channel also changes, resulting in a change in the backflow resistance of the lubricating oil, affecting the oil return capacity of the rotary compressor, reducing the reliability of the rotary compressor, and there is room for improvement. SUMMARY

[0005] The present application aims to at least solve one of the technical problems existing in the prior art. To this end, one object of the present application is to provide a rotary compressor with strong oil return capacity and high reliability.

[0006] The present application also provides a refrigeration equipment.

[0007] According to the rotary compressor of the first aspect of the present application, the rotary compressor comprises a shell, a motor, a compression component, wherein the motor is arranged in the shell, the motor comprises a stator, a rotor and a crankshaft, the stator is sleeved on the rotor, the rotor comprises a rotor core and a permanent magnet arranged on the rotor core, the number of poles of the rotor is P, the stator comprises a stator core, a plurality of cut edge flow channels are defined between the outer periphery of the stator core and the shell, the stator core has a plurality of stator slots for placing stator windings, and the number of stator slots is Q; the compression component is arranged in the shell, and the compression component comprises at least one compression cavity, wherein the total area of the cross sections of the plurality of cut edge flow channels is S1mm 2 , the height dimension of the stator core in the axial direction of the crankshaft is H1mm, the total volume of the compression cavity is Vmm 3 , and the rotary compressor satisfies: 5≤GCD(Q, P)≤6, wherein GCD(Q, P) is the greatest common divisor of the number of stator slots and the number of poles of the rotor.

[0008] According to the rotary compressor of the embodiments of the present application, by associating S1, H1 and V, i.e. and by limiting the numerical range of on the basis of changing the number of poles of the rotor and the number of stator slots, the rigidity of the stator core can be ensured, the connection rigidity between the stator core and the shell can be ensured, and the oil return capacity of the rotary compressor can be improved, thereby the reliability of the rotary compressor can be improved.

[0009] According to some embodiments of the present application, the rotary compressor satisfies 6000≤V≤31000.

[0010] According to some embodiments of the present application, the rotary compressor is a single-cylinder compressor, and the rotary compressor satisfies:

[0011] According to some embodiments of the present application, the rotary compressor is a double-cylinder compressor, and the rotary compressor satisfies:

[0012] According to some embodiments of the present application, the outer diameter of the rotor core is D1 mm, the height of the rotor core in the axial direction of the crankshaft is H2 mm, and the rotary compressor satisfies:

[0013] According to some embodiments of the present application, the rotor core has a plurality of flow-through holes penetrating the rotor core along the extension direction of the crankshaft, and the total area of the cross sections of the plurality of flow-through holes is S2 mm 2 , the outer diameter of the rotor core is D1 mm, the inner diameter of the stator core is D2 mm, and the rotary compressor satisfies:

[0014] In some embodiments, the cross section of at least one of the flow-through holes is circular; and / or, the cross section of at least one of the flow-through holes is kidney-shaped; and / or, the cross section of at least one of the flow-through holes is trapezoidal.

[0015] According to some embodiments of the present application, the outer diameter of the rotor core is D1 mm, the inner diameter of the stator core is D2 mm, and the outer diameter of the stator core is D3 mm, and the rotary compressor satisfies: 0.8≤D2-D1≤1.4,

[0016] In some embodiments, the rotary compressor satisfies: 80≤D3≤150.

[0017] According to some embodiments of the present application, the rotary compressor satisfies: 20≤H1≤60.

[0018] In some embodiments, the number of phases of the stator winding is m, satisfying:

[0019] According to the refrigeration equipment of the second aspect of the embodiments of the present application, the rotary compressor according to the first aspect of the embodiments of the present application is included, by adopting the rotary compressor, the oil return ability of the rotary compressor can be improved, so that the reliability of the rotary compressor can be improved, and the reliability of the refrigeration equipment can be improved.

[0020] Additional aspects and advantages of the present application will be in part apparent and in part pointed out hereinafter. BRIEF DESCRIPTION OF DRAWINGS

[0021] The above and / or additional aspects and advantages of the present application will become apparent and be readily appreciated from the following description, including the appended drawings.

[0022] Fig. 1 is a structural schematic diagram of a rotary compressor according to some embodiments of the present application;

[0023] Fig. 2 is a partial structural schematic diagram of a rotary compressor according to some embodiments of the present application;

[0024] Fig. 3 is a partial structural schematic diagram of a motor according to some embodiments of the present application;

[0025] Fig. 4 is a structural schematic diagram of a stator core according to some embodiments of the present application;

[0026] Fig. 5 is a structural schematic diagram of a rotor according to some embodiments of the present application;

[0027] Fig. 6 is a structural schematic diagram of a rotary compressor according to some embodiments of the present application; and a curve change diagram of oil discharge rate and rigidity;

[0028] Fig. 7 is a structural schematic diagram of a rotary compressor according to some embodiments of the present application; and a curve change diagram of energy efficiency and cost.

[0029] Reference signs: rotary compressor 1000, motor 100, compression component 200, compression cavity 201, shell 10, stator 20, stator core 21, stator slot 211, undercut runner 212, stator winding 22, rotor 30, rotor core 31, flow-through hole 311, permanent magnet 32, crankshaft 40. DETAILED DESCRIPTION

[0030] Embodiments of the present application are described below in detail with reference to the accompanying drawings, in which like or similar elements are denoted by the same or similar reference signs throughout the drawings. The embodiments described below are examples in which the present application is applied, and are merely for the purpose of explaining the present application, and are not to be understood as limiting the present application.

[0031] In the description of the present application, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, and are merely for the purpose of facilitating the description of the present application and simplifying the description, and do not indicate or imply that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore cannot be understood as limiting the present application. In addition, features defined with "first", "second" can explicitly or implicitly include one or more of the features. In the description of the present application, unless otherwise specified, the meaning of "a plurality of" is two or more.

[0032] In the description of the present application, it should be noted that unless otherwise explicitly specified and limited, the terms "mounting", "connecting", "connection" should be understood broadly, for example, it can be fixedly connected, or it can be detachably connected, or integrally connected; it can be mechanically connected, or it can be electrically connected; it can be directly connected, or it can be indirectly connected through an intermediate medium; it can be the communication inside two elements. For those skilled in the art, the specific meaning of the above terms in the present application can be understood according to the specific circumstances.

[0033] The rotary compressor 1000 according to an embodiment of the present application is described below with reference to FIGS. 1-7.

[0034] As shown in FIGS. 1-7, the rotary compressor 1000 according to an embodiment of the present application includes a housing 10, a motor 100, and a compression part 200.

[0035] The motor 100 can be arranged in the shell 10, the motor 100 comprises a stator 20, a rotor 30 and a crankshaft 40, the stator 20 can be sleeved on the outer periphery of the rotor 30, the crankshaft 40 can be connected with the rotor 30, the rotor 30 comprises a rotor core 31 and a permanent magnet 32, the permanent magnet 32 can be arranged in the rotor core 31 to generate a permanent magnetic field in the rotor 30, the stator 20 comprises a stator core 21, the stator core 21 has a plurality of stator slots 211 for placing a stator winding 22, the stator winding 22 can generate a rotating magnetic field in the stator 20 after being energized, the rotating magnetic field of the stator 20 can drive the permanent magnetic field of the rotor 30 to rotate, so that the rotor 30 can be driven to rotate relative to the stator 20 to drive the crankshaft 40 to rotate, and normal operation of the motor 100 can be ensured.

[0036] The compression component 200 can be arranged in the shell 10, the compression component comprises at least one compression cavity 201, a piston can be installed in the compression cavity 201, the piston can be connected with the crankshaft 40, rotation of the crankshaft 40 can drive the piston to move in the compression cavity 201, which is conducive to compression of the gas and pumping of the gas, and part of the lubricating oil in the compression component 200 can be pumped out when the compression component 200 pumps the gas, a plurality of edge cutting flow channels 212 can be defined between the outer periphery of the stator core 21 and the shell 10, so that the pumped lubricating oil can flow back to the compression component 200 through the edge cutting flow channels 212, the loss of the lubricating oil can be reduced, normal operation of the rotary compressor 1000 can be ensured, and maintenance is facilitated.

[0037] In some embodiments, the compression component can comprise one compression cavity 201, i.e., the rotary compressor 1000 is a single-cylinder compressor, which is conducive to reducing the cost of the rotary compressor 1000 on the basis of ensuring the performance of the rotary compressor 1000; or the compression component can comprise a plurality of compression cavities 201, for example, the compression component can comprise two compression cavities 201, i.e., the rotary compressor 1000 is a double-cylinder compressor, which is conducive to improving the performance of the rotary compressor 1000.

[0038] Wherein, the number of poles of the rotor 30 is P, the number of stator slots 211 is Q, GCD(Q, P) is the greatest common divisor of the number of stator slots 211 and the number of poles of the rotor 30, and GCD(Q, P) can represent the order of the minimum electromagnetic force generated by the motor 100, the vibration of the motor 100 is approximately inversely proportional to the fourth power of the order of the electromagnetic force of the motor 100, if the order of the electromagnetic force of the motor 100 is too small, the vibration of the motor 100 is too large, which affects the stability of the operation of the motor 100 and easily generates large noise, if the order of the electromagnetic force of the motor 100 is too large, the complexity of the electric control of the motor 100 is easily increased, which affects the reliability of the operation of the motor 100.

[0039] Therefore, Q, P, and GCD(Q, P) can be determined according to actual design requirements. For example, GCD(Q, P) can be limited to the range of 5-6, that is, GCD(Q, P) can be 5 or 6. When GCD(Q, P) = 5, the number of poles of rotor 30 can be 10 and the number of stator slots 211 can be 15. When GCD(Q, P) = 6, the number of poles of rotor 30 can be 12 and the number of stator slots 211 can be 18. This is beneficial to reduce the vibration of motor 100, reduce the noise of motor 100, improve the stability of motor 100 operation, simplify the electrical control of motor 100, and improve the reliability of motor 100 operation.

[0040] The total cross-sectional area of ​​the multiple cut-edge flow channels 212 is S1mm. 2 The stator core 21 has an axial height of H1mm on the crankshaft 40, and the total volume of the compression chamber 201 is Vmm. 3 That is, the displacement of the rotary compressor 1000 is Vmm. 3 If S1 increases, the contact area between the stator core 21 and the housing 10 decreases, affecting the rigidity of the stator core 21 and the connection rigidity between the stator core 21 and the housing 10. If S1 decreases, the resistance to lubricating oil return increases, reducing the oil return capacity of the rotary compressor 1000.

[0041] If H1 increases, the length of the tangential flow channel 212 increases, thereby increasing the resistance to lubricating oil return and reducing the oil return capacity of the rotary compressor 1000. If H1 decreases, the contact area between the stator core 21 and the housing 10 decreases, affecting the rigidity of the stator core 21 and the connection rigidity between the stator core 21 and the housing 10. If V increases or decreases, the displacement of the rotary compressor 1000 increases or decreases, affecting the oil return capacity of the rotary compressor 1000.

[0042] Therefore, S1, H1, and V can be associated together, that is... And can Limited to between 3.4 and 27.4, The value can be any one of 3.4, 7.4, 11.4, 15.4, 19.4, 23.4, or 27.4, or a range between any two. Based on ensuring the rigidity of the stator core 21 and the connection rigidity between the stator core 21 and the housing 10, the oil return capacity of the rotary compressor 1000 can be improved, thereby improving the reliability of the rotary compressor 1000.

[0043] According to the rotary compressor 1000 of this application embodiment, by associating S1, H1 and V, that is... And through limitations The numerical range of V can ensure the rigidity of the stator core 21, ensure the connection rigidity between the stator core 21 and the shell 10, and improve the oil return capacity of the rotary compressor 1000, thereby improving the reliability of the rotary compressor 1000, on the basis of changing the number of poles of the rotor 30 and the number of stator slots 211.

[0044] As shown in FIGS. 1 and 3, according to some embodiments of the present application, the volume of the compression chamber 201 is V mm3 3 If V is large, the displacement of the rotary compressor 1000 is large, which causes the pump-out amount of lubricating oil to increase when the lubricating oil is pumped in the compression component 200, improves the oil discharge amount of the rotary compressor 1000, and causes the pumped lubricating oil to be more than the returned lubricating oil, thereby reducing the oil return capacity of the rotary compressor 1000. If V is small, the displacement of the rotary compressor 1000 is small, which causes the pump-out amount of the compression component 200 to decrease, and reduces the performance of the rotary compressor 1000.

[0045] Therefore, V can be limited to be between 6000 and 31000, and V can be any one of 6000, 11000, 16000, 21000, 26000, and 31000, or a range value between any two of them. On the basis of ensuring the displacement of the rotary compressor 1000, the oil return capacity of the rotary compressor 1000 can be ensured, thereby improving the performance of the rotary compressor 1000 on the basis of reducing the loss amount of lubricating oil, and improving the reliability of the rotary compressor 1000.

[0046] As shown in FIGS. 1 and 3, according to some embodiments of the present application, S1, H1, and V correspond to different numerical ranges in the rotary compressor 1000 in various embodiments, for example, may be limited to be between 5.7 and 23.7, may be any one of 5.7, 7.7, 9.7, 11.7, 13.7, 15.7, 17.7, 19.7, 21.7, and 23.7, or a range value between any two of them, that is, the rotary compressor 1000 can be a single-cylinder compressor, which is conducive to reducing the implementation cost of the rotary compressor 1000 on the basis of ensuring the reliability of the rotary compressor 1000.

[0047] V can be limited to between 6000 and 15000. V can be any one of the following values ​​or a range between any two: 6000, 7000, 8000, 9000, 10000, 11000, 12000, 13000, 14000, 15000, 16000, and 17000. Based on ensuring the reliability of the rotary compressor 1000, the displacement of the rotary compressor 1000 can be reduced, thereby lowering the cost.

[0048] As shown in Figures 1 and 3, according to some embodiments of this application, It can be limited to between 3.4 and 12.3. The value can be any one of the points 3.4, 4.4, 5.4, 6.4, 7.4, 8.4, 9.4, 10.4, 11.4, and 12.3, or a range between any two. That is, the rotary compressor 1000 can be a twin-cylinder compressor. Based on ensuring the reliability of the rotary compressor 1000, the performance of the rotary compressor 1000 can be improved, and the product grade can be enhanced.

[0049] V can be limited to between 15000 and 31000. V can be any one of the following values ​​or a range between any two: 15000, 16000, 17000, 18000, 19000, 20000, 21000, 22000, 23000, 24000, 25000, 26000, 27000, 28000, 29000, 30000, and 31000. Based on ensuring the reliability of the rotary compressor 1000, the displacement of the rotary compressor 1000 can be increased, the performance of the rotary compressor 1000 can be improved, and the grade of the product can be upgraded.

[0050] In some embodiments, when the rotary compressor 100 of this application adopts a single-cylinder design or a twin-cylinder design, the displacement of both types of rotary compressor 100 can reach 15000 mm. 3 The performance of the rotary compressor 1000 in the two embodiments overlaps, which can improve the cost performance of the product and make it easier for users to choose.

[0051] As shown in Figure 2, according to some embodiments of this application, the outer diameter of the rotor core 31 is D1mm, and the axial height of the rotor core 31 on the crankshaft 40 is H2mm. If the volume of the rotor core 31 is... like Increasing the size of the rotary compressor 1000 will increase its cost, but it will also improve its energy utilization efficiency and overall energy efficiency. If the size is reduced, the energy utilization rate of the rotary compressor 1000 will decrease, thus reducing the energy efficiency of the rotary compressor 1000.

[0052] If V increases, the displacement of the rotary compressor 1000 increases, leading to an increase in the cost of the rotary compressor 1000 and a decrease in the energy utilization rate and energy efficiency of the rotary compressor 1000. If V decreases, the displacement of the rotary compressor 1000 decreases, which will improve the energy utilization rate and energy efficiency of the rotary compressor 1000.

[0053] Therefore, D1, H2, and V can be associated together, that is... And can Limited to between 1.5 and 4.1, The value can be any one of 1.5, 2.0, 2.5, 3.0, 3.5, 4.1 or a range between any two. Based on reducing the cost of the rotary compressor 1000, the energy utilization rate of the rotary compressor 1000 can be improved, and the energy efficiency of the rotary compressor 1000 can be improved.

[0054] As shown in Figures 2-5, according to some embodiments of this application, the rotor core 31 has multiple flow holes 311. The flow holes 311 can penetrate the rotor core 31 along the extension direction of the crankshaft 40 (the up and down direction as shown in Figure 1), which facilitates the pumping out of gas and lubricating oil through the flow holes 311. There is a gap between the rotor core 31 and the stator core 21, which facilitates the pumping out of gas and lubricating oil through the gap. This can prevent lubricating oil from being pumped out through the cut-edge flow channel 212 due to the oil discharge channel (flow holes 311 and the above-mentioned gap) being too small. This is beneficial to improving the oil return capacity of the rotary compressor 1000 and can improve the reliability of the rotary compressor 1000.

[0055] The total cross-sectional area of ​​the multiple flow holes 311 is S2mm. 2 The outer diameter of rotor core 31 is D1mm, the inner diameter of stator core 21 is D2mm, and the total cross-sectional area of ​​the oil discharge channel is... like If S1 increases or decreases, the oil discharge of the rotary compressor 1000 will increase, resulting in more lubricating oil being pumped out than returning, thus reducing the oil return capacity of the rotary compressor 1000. If S1 decreases or increases, the lubricating oil can be easily pumped out through the tangential flow channel 212, thus occupying the tangential flow channel 212 and reducing the oil return capacity of the rotary compressor 1000.

[0056] Therefore, S1, S2, D1, and D2 can be associated together, that is... And can is defined to be between 0.5 and 2.5, may be any one of 0.5, 1.0, 1.5, 2.0, 2.5 or a range value between any two of them, on the basis of ensuring the performance of the rotary compressor 1000, the oil return capacity of the rotary compressor 1000 can be improved, thereby the reliability of the rotary compressor 1000 can be improved.

[0057] In some embodiments, the cross section of the at least one flow hole 311 can be circular, which can reduce the resistance of gas and lubricating oil flow, be conducive to improving the energy efficiency of the rotary compressor 1000, and be conducive to improving the reliability of the rotary compressor 1000, while the stress distribution of the flow hole 311 can be uniform, the service life of the rotor 30 can be improved, and processing is facilitated.

[0058] In some embodiments, the cross section of the at least one flow hole 311 can be waist-shaped, on the basis of fully utilizing the internal space of the rotor 30, the flow area of the flow hole 311 can be increased, the gas and lubricating oil flow capacity can be improved, which is conducive to improving the energy efficiency of the rotary compressor 1000 and the reliability of the rotary compressor 1000.

[0059] In some embodiments, the cross section of the at least one flow hole 311 can be trapezoidal, which can improve the guiding effect of gas flow and reduce turbulence and flow loss in the flow hole 311, thereby being conducive to improving the energy efficiency of the rotary compressor 1000.

[0060] In some embodiments, the plurality of flow holes 311 can all be circular; or the plurality of flow holes 311 can all be waist-shaped; or the plurality of flow holes 311 can all be trapezoidal; or a part of the plurality of flow holes 311 can be circular, and another part of the plurality of flow holes 311 can be waist-shaped; or a part of the plurality of flow holes 311 can be circular, and another part of the plurality of flow holes 311 can be trapezoidal; or a part of the plurality of flow holes 311 can be waist-shaped, and another part of the plurality of flow holes 311 can be trapezoidal; or the plurality of flow holes 311 include circular flow holes, waist-shaped flow holes, and trapezoidal flow holes.

[0061] As shown in FIGS. 4 and 5, according to some embodiments of the present application, the outer diameter of the rotor core 31 is D1 mm, and the inner diameter of the stator core 21 is D2 mm. If D1 is large, the volume of the rotor core 31 will be large, which will cause the cost of the rotary compressor 1000 to increase, and the gap between the rotor core 31 and the stator core 21 will be small, which will cause the oil discharge channel (the gap described above) of the rotary compressor 1000 to be small, and the lubricating oil will be easily pumped out through the trimming flow channel 212 to occupy the trimming flow channel 212, thereby reducing the oil return capacity of the rotary compressor 1000.

[0062] If D1 decreases, the volume of the rotor core 31 decreases, which reduces the energy utilization rate of the rotary compressor 1000 and reduces its energy efficiency. At the same time, the gap between the rotor core 31 and the stator core 21 increases, which leads to a larger oil discharge passage (the aforementioned gap) of the rotary compressor 1000. This increases the amount of oil discharged by the rotary compressor 1000, causing more lubricating oil to be pumped out than to return, thereby reducing the oil return capacity of the rotary compressor 1000.

[0063] If D2 increases, the gap between the rotor core 31 and the stator core 21 increases, which leads to a larger oil discharge passage (the aforementioned gap) of the rotary compressor 1000. This increases the oil discharge volume of the rotary compressor 1000, causing more lubricating oil to be pumped out than to return, thereby reducing the oil return capacity of the rotary compressor 1000. If D2 decreases, the oil discharge passage (the aforementioned gap) of the rotary compressor 1000 decreases, and lubricating oil can easily be pumped out through the tangential flow channel 212, thus occupying the tangential flow channel 212 and reducing the oil return capacity of the rotary compressor 1000.

[0064] Therefore, D1 and D2 can be associated together, i.e., D2-D1, and D2-D1 can be limited to between 0.8 and 1.4. D2-D1 can be any one of the point values ​​of 0.8, 0.9, 1.0, 1.1, 1.2, 1.3, and 1.4 or any range between two of them. Based on reducing the cost of the rotary compressor 1000 and improving the energy efficiency of the rotary compressor 1000, the oil return capability of the rotary compressor 1000 can be improved, and the reliability of the rotary compressor 1000 can be improved.

[0065] The outer diameter of the stator core 21 is D3mm. The dimensions of the stator 20 of the motor 100 can be related to the greatest common divisor of the number of stator slots 211 and the number of poles of the rotor 30. For example, the ratio of the outer diameter to the inner diameter of the stator core 21 can be multiplied by the greatest common divisor of the number of stator slots 211 and the number of poles of the rotor 30, i.e. like If the size is too large or too small, it will easily reduce the working efficiency of motor 100 and increase the cost of motor 100.

[0066] Therefore, it can be Limited to between 3 and 3.25. The value can be any one of the points 3, 3.05, 3.10, 3.15, 3.20, or 3.25, or a range between any two, thereby allowing the input of a predetermined GCD(Q, P) to... The ratio of the outer diameter of the stator core 21 to the inner diameter of the stator core 21 can be determined, which is beneficial for the designer to determine a reasonable size of the motor 100, thereby improving the working efficiency of the motor 100 and reducing the cost of the motor 100.

[0067] As shown in FIG. 4, in some embodiments, if D3 is too large, the volume of the motor 100 is increased, which affects the arrangement of the motor 100, and if D3 is too small, the manufacturing difficulty of the motor 100 is increased, and the performance of the motor 100 is difficult to guarantee. Therefore, D3 can be limited to 80-150, and D3 can be any one of 80, 90, 100, 110, 120, 130, 140, and 150 or a range value between any two of them. On the basis of guaranteeing the performance of the motor 100, the volume of the motor 100 can be appropriately reduced, which is beneficial for the miniaturization of the motor 100 and facilitates the arrangement of the motor 100.

[0068] As shown in FIG. 1, according to some embodiments of the present application, if H1 is large, the length of the trimming runner 212 is long, thereby increasing the resistance of the lubricating oil backflow and reducing the oil return capacity of the rotary compressor 1000, and if H1 is small, the contact area between the stator core 21 and the shell 10 is small, which affects the rigidity of the stator core 21 and the connection rigidity between the stator core 21 and the shell 10.

[0069] Therefore, H1 can be limited to 20-60, and H1 can be any one of 20, 30, 40, 50, and 60 or a range value between any two of them. On the basis of guaranteeing the rigidity of the stator core 21 and on the basis of guaranteeing the connection rigidity between the stator core 21 and the shell 10, the oil return capacity of the rotary compressor 1000 can be improved, and the reliability of the rotary compressor 1000 can be improved.

[0070] In some embodiments, the number of phases of the stator winding 22 is m, and the number of slots occupied by each phase winding under each magnetic pole is By limiting The motor 100 can use fractional slots, which is beneficial for saving energy, improving working efficiency, reducing noise, and adopting concentrated winding, which is beneficial for improving the regularity of automatic winding, improving the utilization rate of the space in the stator slot 211, and keeping the variable loss and the invariable loss of the motor 100 at a relatively average level, thereby improving the working efficiency of the motor 100 and the power density of the motor 100.

[0071] In some embodiments, the number of stator slots 211 is Q, the number of poles of rotor 30 is P, the vibration degree of motor 100 is inversely proportional to the order of the minimum electromagnetic force generated by motor 100, and GCD(Q,P) can represent the order of the minimum electromagnetic force generated by motor 100. Designers can limit P to between 10 and 12, and designers can limit Q to between 15 and 18. That is, P can be any value among 10, 11, and 12, and Q can be any value among 15, 16, 17, and 18.

[0072] and This ensures that the motor 100 adopts a fractional-slot concentrated winding form. That is, in order to simplify the electrical control and make the winding of the stator winding 22 more regular, the designer can choose to have 15 stator slots 211 and 10 poles of the rotor 30, or the designer can choose to have 18 stator slots 211 and 12 poles of the rotor 30. This can reduce the vibration and noise of the motor 100, simplify the electrical control of the motor 100, make the winding of the winding 12 more regular, and facilitate manufacturing.

[0073] The refrigeration equipment according to the embodiments of this application includes a rotary compressor 1000. By using the rotary compressor 1000, the oil return capability of the rotary compressor 1000 can be improved, thereby improving the reliability of the rotary compressor 1000 and the reliability of the refrigeration equipment.

[0074] Figure 6 shows the rotary compressor 1000. The diagram shows the changes in the curves of oil yield and rigidity. As can be seen from Figure 6, with... As the temperature rises, the rigidity of the stator core 21 decreases, and the connection rigidity between the stator core 21 and the housing 10 decreases. Simultaneously, the oil discharge rate of the rotary compressor 1000 decreases, meaning the oil return capacity of the rotary compressor 1000 becomes stronger, until... Equals 27.4, when When the oil discharge rate of the rotary compressor 1000 is greater than 27.4, the oil discharge rate remains relatively stable, but the rigidity of the stator core 21 and the connection rigidity between the stator core 21 and the housing 10 decrease rapidly, making it difficult to ensure the safe operation of the rotary compressor 1000.

[0075] along with As the oil content decreases, the rigidity of the stator core 21 increases, and the connection rigidity between the stator core 21 and the housing 10 also increases. Simultaneously, the oil discharge rate of the rotary compressor 1000 increases, meaning the oil return capacity of the rotary compressor 1000 deteriorates, until... Equals 3.4, when When the ratio is less than 3.4, the rigidity of the stator core 21 and the connecting rigidity between the stator core 21 and the housing 10 are maintained stable, but the oil discharge rate of the rotary compressor 1000 rapidly increases, that is, the oil return ability of the rotary compressor 1000 is suddenly weakened, which affects the reliability of the rotary compressor 1000, and thus, the ratio needs to be limited to 3.4-17.4. 3.4-17.4.

[0076] FIG. 7 is a graph showing the relationship between the ratio and the cost and the energy efficiency of the rotary compressor 1000, and FIG. 8 is a graph showing the relationship between the ratio and the oil return ability of the rotary compressor 1000. As can be seen from FIG. 7, as the ratio increases, the cost of the rotary compressor 1000 increases, and at the same time, the energy efficiency of the rotary compressor 1000 improves, until the ratio is equal to 4.1, and when the ratio is greater than 4.1, the energy efficiency of the rotary compressor 1000 is maintained stable, but the cost of the rotary compressor 1000 still increases more obviously, which affects the performance-price ratio of the rotary compressor 1000. As can be seen from FIG. 7, as the ratio increases, the cost of the rotary compressor 1000 increases, and at the same time, the energy efficiency of the rotary compressor 1000 improves, until the ratio is equal to 4.1, and when the ratio is greater than 4.1, the energy efficiency of the rotary compressor 1000 is maintained stable, but the cost of the rotary compressor 1000 still increases more obviously, which affects the performance-price ratio of the rotary compressor 1000.

[0077] As can be seen from FIG. 7, as the ratio increases, the cost of the rotary compressor 1000 increases, and at the same time, the energy efficiency of the rotary compressor 1000 improves, until the ratio is equal to 4.1, and when the ratio is greater than 4.1, the energy efficiency of the rotary compressor 1000 is maintained stable, but the cost of the rotary compressor 1000 still increases more obviously, which affects the performance-price ratio of the rotary compressor 1000. As can be seen from FIG. 7, as the ratio increases, the cost of the rotary compressor 1000 increases, and at the same time, the energy efficiency of the rotary compressor 1000 improves, until the ratio is equal to 4.1, and when the ratio is greater than 4.1, the energy efficiency of the rotary compressor 1000 is maintained stable, but the cost of the rotary compressor 1000 still increases more obviously, which affects the performance-price ratio of the rotary compressor 1000. As can be seen from FIG. 7, as the ratio increases, the cost of the rotary compressor 1000 increases, and at the same time, the energy efficiency of the rotary compressor 1000 improves, until the ratio is equal to 4.1, and when the ratio is greater than 4.1, the energy efficiency of the rotary compressor 1000 is maintained stable, but the cost of the rotary compressor 1000 still increases more obviously, which affects the performance-price ratio of the rotary compressor 1000.

[0078] The other configurations and operations of the rotary compressor 1000 according to the embodiments of the present application are known to those skilled in the art, and thus, will not be described in detail. In the description of the present application, the "first feature" and the "second feature" can include one or more features. Among them, the up-down direction, the left-right direction and the front-rear direction are based on the up-down direction, the left-right direction and the front-rear direction shown in the drawings.

[0079] In the description of the present application, unless explicitly specified and limited, the "above" or "below" of the first feature to the second feature can include that the first and second features are in direct contact, or that the first and second features are not in direct contact but are in contact through another feature between them. Moreover, the "above", "upper" and "upper surface" of the first feature to the second feature include that the first feature is directly above and obliquely above the second feature, or only means that the first feature is horizontally higher than the second feature.

[0080] ​​​​In the description of the application, reference has been made to descriptive terms such as "one embodiment", "some embodiments", "an embodiment", "example", "specific example" or "some examples" etc. It is emphasized that each of these terms refers to a specific feature, structure, material or characteristic described in connection with a particular embodiment or example. The descriptive terms are not necessarily referring to the same embodiment or example. Moreover, the specific features, structures, materials, or characteristics can be combined in any suitable manner in one or more embodiments or examples.

[0081] While embodiments of the application have been shown and described, it is to be understood that the application is not limited to the details of the embodiments described, since the scope of the application is defined with respect to the appended claims.

Claims

1. A rotary compressor, wherein, Comprising: a housing; a motor provided in the housing, the motor comprising a stator, a rotor and a crankshaft, the stator sheathed on the rotor, the crankshaft connected with the rotor, the rotor comprising a rotor core and a permanent magnet provided on the rotor core, the rotor having a pole number of P, the stator comprising a stator core, a plurality of cut-edge flow channels defined between an outer periphery of the stator core and the housing, the stator core having a plurality of stator slots for placing stator windings, the number of the stator slots being Q; A compression component is arranged in the housing, the compression component comprising at least one compression cavity, wherein the total cross-sectional area of the plurality of cut-edge flow channels is S1 mm 2 The height dimension of the stator core in the axial direction of the crankshaft is H1 mm, and the total volume of the compression cavity is V mm 3 The rotary compressor satisfies: wherein GCD(Q, P) is a greatest common divisor of the number of the stator slots and the pole number of the rotor.

2. The rotary compressor of claim 1, wherein, The rotary compressor satisfies: 6000≤V≤31000.

3. The rotary compressor of any one of claims 1-2, wherein, The rotary compressor is a single-cylinder compressor, and the rotary compressor satisfies:

4. The rotary compressor of any one of claims 1-3, wherein, The rotary compressor is a double-cylinder compressor, and the rotary compressor satisfies:

5. The rotary compressor of any one of claims 1-4, wherein, An outer diameter of the rotor core is D1 mm, a height of the rotor core in an axial direction of the crankshaft is H2 mm, and the rotary compressor satisfies:

6. The rotary compressor of any one of claims 1-5, wherein, The rotor core has a plurality of flow-through holes that penetrate the rotor core in the extension direction of the crankshaft, the total area of the cross sections of the plurality of flow-through holes being S2 mm 2 The outer diameter of the rotor core is D1 mm, the inner diameter of the stator core is D2 mm, and the rotary compressor satisfies:

7. The rotary compressor of claim 6, wherein, A cross section of at least one of the flow-through holes is circular; and / or, a cross section of at least one of the flow-through holes is kidney-shaped; and / or, a cross section of at least one of the flow-through holes is trapezoidal.

8. The rotary compressor of any one of claims 1-7, wherein, An outer diameter of the rotor core is D1 mm, an inner diameter of the stator core is D2 mm, an outer diameter of the stator core is D3 mm, and the rotary compressor satisfies:

9. The rotary compressor of claim 8, wherein, The rotary compressor satisfies: 80≤D3≤150.

10. The rotary compressor of any one of claims 1-9, wherein, The rotary compressor satisfies: 20≤H1≤60.

11. The rotary compressor of any one of claims 1-10, wherein, The number of phases of the stator winding is m, satisfying:

12. A refrigeration appliance, wherein, A rotary compressor according to any one of claims 1-11.

Images