Rotary compressor and refrigeration apparatus

Abstract

A rotary compressor and a refrigeration apparatus, the rotary compressor comprising an electric motor and a pump body component. The electric motor comprises a stator and a rotor, wherein the stator comprises a stator core and stator windings, and the rotor comprises a rotor core; the stator core comprises an annular yoke portion and a plurality of tooth portions arranged in the yoke portion; a stator slot is formed between every two adjacent tooth portions, and the stator windings are wound within the stator slots. The pump body component comprises a crankshaft, an upper bearing and a cylinder. The number of stator slots is Q, the number of poles of the rotor is P, the maximum outer circular contour radius of the rotor core is R1 and the maximum outer circular contour outer diameter is D1, where D1=2*R1, the outer diameter of the part of the crankshaft that engages with the upper bearing is D2, and GCD(Q, P) is the greatest common divisor of Q and P, satisfying: formula (1), formula (2) and formula (3).

Description

Rotary compressor and refrigeration equipment

[0001] Cross-reference to related applications

[0002] The present application is based on Chinese Patent Application No. 202411063273.0, filed on August 2, 2024, in the name of Anhui Meizhi Precision Manufacturing Co., Ltd., entitled "Rotary Compressor and Refrigeration Equipment", 202421873924.8, filed on August 2, 2024, in the name of Anhui Meizhi Precision Manufacturing Co., Ltd., entitled "Rotary Compressor and Refrigeration Equipment", and claims priority to the above-mentioned Chinese Patent Applications, the contents of which are incorporated herein by reference in their entirety. TECHNICAL FIELD

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

[0004] In related art, the motor as an important device for converting electrical energy into mechanical energy plays a key role in rotary compressors, refrigeration equipment, household appliances and other fields. Among them, the motor mainly includes a stator assembly and a rotor assembly, and a rotating magnetic field can be generated by the current in the stator winding to interact with the rotor magnet in the rotor assembly, thereby generating a rotating torque. However, the motor currently applied in the rotary compressor has a low actual work efficiency when cooperating with the pump body component to do work, consumes a large amount of electrical energy, 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, the present application proposes a rotary compressor, by limiting the parameters of the motor and the parameters of the pump body component, so that the rotary compressor has a high work efficiency when actually working, which is beneficial to reduce the consumption of electricity.

[0006] A rotary compressor according to an embodiment of this application includes: a motor, the motor including a stator and a rotor, the rotor being located within the stator, the stator including a stator core and a stator winding, the stator core including a ring-shaped yoke and a plurality of teeth disposed within the yoke, the plurality of teeth being circumferentially spaced along the yoke, and a stator slot being formed between adjacent teeth, the stator winding being wound within the stator slot, and the rotor including a rotor core; a pump body component, the pump body component including a crankshaft, an upper bearing, and a cylinder, one end of the crankshaft being connected to the rotor core, and the other end of the crankshaft being sequentially passed through the upper bearing and the cylinder; wherein, the number of stator slots is Q, the number of poles of the rotor is P, the maximum outer radius of the rotor core is R1 and the maximum outer diameter of the rotor core is D1, D1=2*R1, and the outer diameter of the portion of the crankshaft mating with the upper bearing is D2. Let Q be the greatest common divisor of Q and P, and satisfy: 0.7 ≤ ≤2.7, 1< <3, 5≤ ≤6.

[0007] According to the rotary compressor of this application embodiment, by limiting the dimensions of the stator core, rotor core, and pump body components within the aforementioned range, the stator can generate a sufficiently large driving force on the rotor core, achieving powerful driving of the rotor core. The rotor core and crankshaft can output effective driving force to compress a larger volume of refrigerant. Simultaneously, it avoids excessively large structural dimensions of the rotor core and stator core, controls the reasonable cost of structural component design, and, through... Limiting the value to a range of 0.7 to 2.7 allows the rotor core and crankshaft of the rotary compressor to generate a sufficiently effective and stable driving force when operating at low frequencies. This reduces fluctuations in motor rotation, achieves effective compression of the refrigerant, and improves the overall energy efficiency of the rotary compressor. At the same time, it avoids excessively large structural dimensions of the rotor core and crankshaft, preventing excessive vibration and noise caused by excessive rotational inertia of the rotor core and crankshaft when operating at high frequencies. It also reduces frictional energy consumption caused by excessive rotational inertia of the rotor core and crankshaft, which also helps to improve the energy efficiency of the rotary compressor.

[0008] The rotary compressor according to some embodiments of this application satisfies: 0.9 ≤ ≤1.8.

[0009] The rotary compressor according to some embodiments of this application satisfies: 1.05 ≤ ≤1.1.

[0010] According to some embodiments of the application, the other end of the crankshaft is provided with an eccentric part, the eccentric part is located in the cylinder and eccentrically rotates in the cylinder;

[0011] Wherein, the axial height of the rotor core is H2, the distance between the center line of the eccentric part and the center line of the crankshaft is e, and 0.04≤e / H2≤0.18 is satisfied.

[0012] According to some embodiments of the application, 0.09≤e / H2≤0.11 is satisfied.

[0013] According to some embodiments of the application, the maximum outer contour radius of the stator core is R2 and the maximum outer contour diameter is D4, the axial height of the stator core is H3, the axial height of the cylinder is H1, and D4=2R2 is satisfied, and 1.3≤H3 / H1≤8.8 is satisfied.

[0014] According to some embodiments of the application, 2.3≤H3 / H1≤2.7 is satisfied.

[0015] According to some embodiments of the application, the inner diameter of the cylinder is D3, and 0.59≤D3 / H1≤3.11 is satisfied.

[0016] According to some embodiments of the application, 1.0≤D3 / H1≤1.2 is satisfied.

[0017] According to some embodiments of the application, 34mm≤D3≤71mm is satisfied; and / or, 12mm≤H1≤32mm is satisfied.

[0018] According to some embodiments of the application, 23mm≤R1≤39mm is satisfied;

[0019] and / or, 45mm≤R2≤70 mm is satisfied.

[0020] According to some embodiments of the application, 15≤Q≤18 is satisfied;

[0021] and / or, 10≤P≤12 is satisfied.

[0022] According to some embodiments of the application, the number of slots per pole per phase of the motor is q, the number of phases of the motor is m, q= , and 0

[0023] ​​​​​​This application also proposes a refrigeration device.

[0024] The refrigeration equipment according to the embodiments of this application includes a rotary compressor of any of the above embodiments.

[0025] The refrigeration equipment described above has the same advantages over the prior art as the rotary compressor described above, and will not be repeated here.

[0026] Additional aspects and advantages of this application will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of this application. Attached Figure Description

[0027] The above and / or additional aspects and advantages of this application will become apparent and readily understood from the description of the embodiments taken in conjunction with the following drawings, in which:

[0028] Figure 1 is a cross-sectional view of a rotary compressor according to an embodiment of this application;

[0029] Figure 2 is a schematic diagram of the structure of the motor according to an embodiment of this application (stator windings are not shown).

[0030] Figure 3 is a schematic diagram of the structure of the cylinder of the motor according to an embodiment of this application;

[0031] Figure 4 is a schematic diagram of the structure of the motor according to an embodiment of this application;

[0032] Figure 5 is a cross-sectional view (with housing) of a rotary compressor according to an embodiment of this application;

[0033] Figure 6 is a schematic diagram of the structure of a rotary compressor (including a liquid receiver) according to an embodiment of this application.

[0034] Figure 7 shows the compressor during rotation according to an embodiment of this application. A diagram showing the relationship between energy efficiency and other parameters;

[0035] Figure 8 shows the compressor during rotation according to an embodiment of this application. A diagram showing the relationship between energy efficiency and other parameters;

[0036] Figure 9 shows the compressor during rotation according to an embodiment of this application. A diagram showing the relationship between energy efficiency and other parameters;

[0037] Figure 10 shows the compressor during rotation according to an embodiment of this application. A diagram showing the relationship between energy efficiency and energy efficiency.

[0038] Figure label:

[0039] Rotary compressor 100,

[0040] Motor 1, stator core 11, yoke portion 111, tooth portion 112, stator slot 113, stator winding 114, rotor core 12, rotor magnet 121,

[0041] Pump body part 2, crankshaft 21, upper bearing 22, cylinder 23, eccentric portion 231, lower bearing 24,

[0042] Housing 3,

[0043] Reservoir 200. Embodiments of the present application

[0044] Embodiments of the present application will be described in detail below with reference to the drawings, in which the same or similar components are denoted by the same or similar reference numerals, and therefore repeated description is omitted. The embodiments described below by reference to the drawings are exemplary and are for the purpose of explanation only and are not to be understood as limiting the present application.

[0045] In the description of the present application, it should be understood that the orientation or positional relationship indicated by 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 is based on the orientation or positional relationship shown in the drawings, and is only for the purpose of facilitating the description of the present application and simplifying the description, and does 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, the features defined as "first" and "second" can explicitly or implicitly include one or more of the features. In the description of the present application, unless otherwise specified and limited, the term "a plurality of" means two or more.

[0046] 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.

[0047] The rotary compressor 100 according to the embodiments of the present application is described below with reference to FIGS. 1-6. The rotary compressor 100 is designed and operates in a range of parameters defined by the relationship between the parameters of the motor 1 and the parameters of the pump body component 2, so that the rotary compressor 100 has a high operating efficiency, reduces the power consumption during operation of the rotary compressor 100, reduces the operating cost of the rotary compressor 100, and meets the design requirements.

[0048] As shown in FIGS. 1-6, the rotary compressor 100 according to one embodiment of the present application includes a motor 1 and a pump body component 2. The rotary compressor 100 further includes a housing 3, and the motor 1 and the pump body component 2 are installed in the housing 3.

[0049] As shown in FIGS. 1 and 5, the motor 1 includes a stator and a rotor, and the rotor is located in the stator, i.e., the stator is sleeved on the outside of the rotor, so that the center lines of the stator and the rotor are coincidentally distributed. The stator includes a stator core 11 and a stator winding 114. The stator core 11 includes a yoke portion 111 configured in a ring shape and a plurality of tooth portions 112 arranged in the yoke portion 111. The plurality of tooth portions 112 are spaced apart along the circumferential direction of the yoke portion 111, and a stator slot 113 is formed between adjacent two tooth portions 112. The stator winding 114 is wound in the stator slot 113. Specifically, as shown in FIG. 2, the yoke portion 111 of the stator core 11 can be configured in a circular ring shape. The tooth portions 112 are arranged to extend radially inwardly on the inner circumferential wall of the yoke portion 111. The plurality of tooth portions 112 are spaced apart and distributed along the circumferential direction on the inner side of the yoke portion 111. The stator winding 114 is wound on the outer side of each tooth portion 112, so that the stator winding 114 is located in the stator slot 113.

[0050] That is, the stator winding 114 is also a plurality of stator windings 114, and the plurality of stator windings 114 are respectively and one-to-one wound on the outside of the plurality of tooth portions 112. Meanwhile, the rotor includes a rotor core 12, which is located in the stator core 11 and the axes of which coincide. A plurality of magnetic steel slots are arranged on the outer circumferential wall of the rotor core 12, and the plurality of magnetic steel slots are spaced apart and distributed along the circumferential direction of the rotor core 12. A rotor magnet 121 is arranged in each magnetic steel slot. When the stator winding 114 is energized, the current in the stator winding 114 generates a rotating magnetic field, which interacts with the rotor magnet 121 to generate a rotating torque to drive the rotor core 12 to rotate.

[0051] As shown in FIG. 1 and FIG. 5, the pump body component 2 comprises a crankshaft 21, an upper bearing 22 and a cylinder 23, one end of the crankshaft 21 is connected with the rotor core 12, the other end of the crankshaft 21 is arranged in the upper bearing 22 and the cylinder 23, wherein the cylinder 23 is formed with a piston cavity, and an eccentric part 231 is further arranged in the piston cavity, and the eccentric part 231 is fixedly connected with the other end of the crankshaft 21. Thus, when the rotor core 12 rotates, the rotor core 12 can drive the crankshaft 21 to rotate, so that the other end of the crankshaft 21 drives the eccentric part 231 to eccentrically rotate in the cylinder 23, and the cylinder 23 is connected with the liquid accumulator 200, so that the refrigerant at the liquid accumulator 200 flows into the piston cavity of the cylinder 23, and then the refrigerant is compressed under the eccentric rotation of the eccentric part 231. The pump body component 2 can further comprise a lower bearing 24, the upper bearing 22 and the lower bearing 24 are fixed in the shell 3, the cylinder 23 is located between the upper bearing 22 and the lower bearing 24, and the crankshaft 21 is sequentially arranged in the upper bearing 22, the cylinder 23 and the lower bearing 24.

[0052] Wherein, the number of the stator slot 113 is Q, the pole number of the rotor is P, the maximum outer circle profile radius of the rotor core 12 is R1 and the maximum outer circle profile diameter is D1, D1=2*R1, the outer diameter of the matching part of the crankshaft 21 and the upper bearing 22 is D2, GCD(Q, P) is the greatest common divisor of Q and P, and satisfies: 0.7≤D2 / R1≤2.7, 1<D1 / D2<3. 5≤GCD(Q, P)≤6, that is, the rotary compressor 100 in the application can simultaneously satisfy the parameter relationship defined in the above three formulas, so that the rotary compressor 100 has higher working energy efficiency.

[0053] Specifically, GCD (Greatest Common Divisor) means the greatest common divisor, GCD(Q, P) is the greatest common divisor of the number of stator slots 113 Q and the pole number P of the rotor, wherein 5≤GCD(Q, P)≤6, that is, the greatest common divisor of the number of stator slots 113 Q and the pole number P of the rotor can be 5 or 6, for example, when Q is 15, P can be 10, when Q is 18, P can be 12, that is, the application can be applied to the rotary compressor 100 whose greatest common divisor of Q and P is 5 or 6.

[0054] Meanwhile, 1<D1 / D2<3, that is, the number of stator slots 113 Q is greater than the pole number P of the rotor, for example, Q can be set to 15, P can be set to 10, so that is 1.5, or Q is set to 18, P can be set to 12, so that is 1.5, of course, other combinations can also be used, so that is between 1 and 3, for example, so that ​​1.7, 1.6, etc. Among them, by setting 1 < GCD (Q, P) < 2 As can be known from <3>, the motor of the present application is a fractional slot motor, so that the compressor can take into account the production rhythm and the capacity of the winding equipment, but the torque fluctuation of the fractional slot motor is large, and the low-frequency torque compensation current needs to be introduced by the electric control when the compressor is running at low frequency, so as to reduce the vibration problem caused by the torque fluctuation. At the same time, the introduction of current will reduce the motor frequency. In the present application, by setting GCD (Q, P) to 5 or 6, when Q is 15, P can be 10, and when Q is 18, P can be 12. By setting the motor 1 with a larger slot pole common divisor, the rotation fluctuation of the motor 1 can be effectively reduced, and the current for low-frequency torque compensation is also smaller. Moreover, setting GCD (Q, P) to be less than or equal to 6 can also avoid the motor frequency being too large, reduce the frequency of the magnetic field generated by the rotor on the stator side, and ensure the motor efficiency.

[0055] And 0.7 < D2 / D1 < 2.7 As shown in FIG. 1, the outer diameter of the crankshaft 21 and the upper bearing 22 is D2, and the maximum outer diameter of the rotor core 12 is D1. Therefore, the product of the greatest common divisor of the number of stator slots 113 Q and the number of poles P of the rotor and the outer diameter D2 of one end of the crankshaft 21 is divided by the maximum outer diameter D1 of the rotor core 12, and the value obtained is in the range of 0.7-2.7, such as 0.8, 0.9, 1.3, 1.4, 1.9, 2.3, 2.6, 2.7, etc. It can be understood that the larger the outer diameter of the rotor core 12 is set, the greater the driving force that can be formed by the rotor core 12, and the moment of inertia of the rotor core 12 is proportional to the square of the outer diameter of the rotor core 12. Increasing the moment of inertia can again reduce the low-frequency torque fluctuation and improve the efficiency of the motor 1. At the same time, the crankshaft 21 and the rotor core 12 are connected in a sleeve fit, and the crankshaft 21 in the pump body part 2 is fixed by the upper bearing 22. Therefore, the smaller the outer diameter D2 of the crankshaft 21 is set, the smaller the friction during the rotation of the crankshaft 21 will be, but it cannot be set too small under the condition of ensuring the structural strength. Therefore, the outer diameter D2 of the crankshaft 21 is set to be between 0.7 and 2.7. 0.8, 0.9, 1.3, 1.4, 1.9, 2.3, 2.6, 2.7, etc. It can be understood that the larger the outer diameter of the rotor core 12 is set, the greater the driving force that can be formed by the rotor core 12, and the moment of inertia of the rotor core 12 is proportional to the square of the outer diameter of the rotor core 12. Increasing the moment of inertia can again reduce the low-frequency torque fluctuation and improve the efficiency of the motor 1. At the same time, the crankshaft 21 and the rotor core 12 are connected in a sleeve fit, and the crankshaft 21 in the pump body part 2 is fixed by the upper bearing 22. Therefore, the smaller the outer diameter D2 of the crankshaft 21 is set, the smaller the friction during the rotation of the crankshaft 21 will be, but it cannot be set too small under the condition of ensuring the structural strength. Therefore, the outer diameter D2 of the crankshaft 21 is set to be between 0.7 and 2.7.

[0056] And D2 / D1 is set to be between 0.7 and 2.7 The setting between 0.7~2.7 can make the rotor core 12 and the crankshaft 21 have a larger structural size, so that the rotary compressor 100 can form a sufficient effective and stable driving force when the rotary compressor 100 is running at a low frequency, the rotation fluctuation of the motor 1 is small, the effective compression of the refrigerant can be realized, the overall energy efficiency of the rotary compressor 100 is improved, at the same time, the structural size of the crankshaft 21 can be avoided to be too large, the rotary compressor 100 can avoid that the rotary compressor 100 generates larger vibration noise when the rotary compressor 100 is running at a high frequency, the rotary compressor 100 also reduces the friction energy consumption generated by the too large moment of inertia of the rotor core 12 and the crankshaft 21, which is also beneficial to improve the energy efficiency of the rotary compressor 100.

[0057] According to the rotary compressor 100 of the embodiment of the present application, the size of the stator core 11, the rotor core 12 and the pump body part 2 is limited in the above range, the rotary compressor can consider the production rhythm and the capacity of the winding equipment by setting the fractional slot motor, at the same time, the rotation fluctuation of the motor 1 is reduced, the operation efficiency of the motor 1 is improved, the rotor core 12 and the crankshaft 21 can output effective driving force for the compression of larger volume of refrigerant, and the structural size of the rotor core 12 and the stator core 11 can also be avoided to be too large, the reasonable cost of the structure part is controlled, and when the rotary compressor 100 is running at a high frequency or a low frequency, The range of 0.7~2.7 can guarantee good operation efficiency and reduce the power consumption of the rotary compressor 100.

[0058] In some embodiments, 0.9≤ ≤1.8, wherein the outer diameter of one end of the crankshaft 21 is D2, that is, the outer diameter of the end of the crankshaft 21 which is installed and matched with the rotor core 12 is D2, at the same time, the maximum outer diameter of the rotor core 12 is D1, and thus the product of the greatest common divisor of the number Q of stator slots 113 and the pole number P of the rotor and the outer diameter D2 of one end of the crankshaft 21 is divided by the maximum outer diameter D1 of the rotor core 12, and the value is in the range interval of 0.9~1.8, such as 0.9, 1.1, 1.2, 1.4, 1.52, 1.56, 1.61, 1.7, etc.

[0059] Thus, the product of the greatest common divisor of the number Q of stator slots 113 and the pole number P of the rotor and the outer diameter D2 of one end of the crankshaft 21 is divided by the maximum outer diameter D1 of the rotor core 12, and the value is in the range interval of 0.9~1.8, such as The setting is between 0.9~1.8, not only can make the motor 1 can be larger volume of refrigerant compression, play a role in improving the compression efficiency, and can avoid the rotor core 12 and crankshaft 21 setting size too large resulting in the setting cost is too high. And, the parameter range is more accurate, can make the rotor core 12 and crankshaft 21 have a larger structure size, so that the rotary compressor 100 in low frequency operation, rotor core 12 and crankshaft 21 can form a sufficient effective and stable driving force, more effectively reduce the motor 1 operation fluctuation, realize the effective compression of refrigerant, improve the overall energy efficiency of rotary compressor 100, at the same time, can avoid the rotor core 12 and crankshaft 21 structure size is too large, avoid rotary compressor 100 in high frequency operation, rotor core 12 and crankshaft 21 inertia is too large to produce larger vibration noise, at the same time also reduce the rotor core 12 and crankshaft 21 due to the inertia of the rotation of the friction energy consumption, also conducive to improve the energy efficiency of rotary compressor 100, and thus the relationship between the energy efficiency and cost of rotary compressor 100 is more balanced, meet the design requirements of many aspects.

[0060] In other embodiments, 1.05≤ ≤1.1. Thus, the maximum common divisor of the number of stator slots 113 Q and the number of poles P of the rotor is divided by the maximum outer diameter of the rotor core 12 D1, and the product of the outer diameter D2 of one end of the crankshaft 21 is in the range of 1.05~1.1, such as 1.06, 1.07, 1.08, 1.09, 1.1, etc.

[0061] Thus, the is set between 1.05~1.1, the parameter range is more accurate, can make the rotor core 12 and crankshaft 21 have a larger structure size, so that the rotary compressor 100 in low frequency operation, rotor core 12 and crankshaft 21 can form a sufficient effective and stable driving force, more effectively reduce the motor 1 operation fluctuation, realize the effective compression of refrigerant, improve the overall energy efficiency of rotary compressor 100, at the same time, can avoid the rotor core 12 and crankshaft 21 structure size is too large, avoid rotary compressor 100 in high frequency operation, rotor core 12 and crankshaft 21 inertia is too large to produce larger vibration noise, at the same time also reduce the rotor core 12 and crankshaft 21 due to the inertia of the rotation of the friction energy consumption, also conducive to improve the energy efficiency of rotary compressor 100, and thus the relationship between the energy efficiency and cost of rotary compressor 100 is more balanced, meet the design requirements of many aspects.

[0062] As shown in FIG. 7, in combination with the relationship diagram between the energy efficiency of the rotary compressor 100, the overall normal distribution, that is, When the parameter value is set between 0.7 and 2.7, the energy efficiency of the rotary compressor 100 is higher than that corresponding to other values, especially in... When the efficiency is between 0.9 and 1.8, the corresponding rotary compressor 100 exhibits a more concentrated and higher energy efficiency, and in the context of... When the efficiency is limited to between 1.05 and 1.1, the overall energy efficiency of the rotary compressor 100 is relatively high. In other words, the highest energy efficiency point is located between 1.05 and 1.1. Therefore, in this application... By limiting the parameters to the ranges mentioned above, the working efficiency of the rotary compressor 100 during actual operation can be effectively improved, and the power consumption of the motor 1 can be reduced.

[0063] In some embodiments, as shown in Figures 1 and 5, an eccentric portion 231 is provided on the other end of the crankshaft 21. The eccentric portion 231 is located inside the cylinder 23 and rotates eccentrically inside the cylinder 23. That is, the eccentric portion 231 can be fixedly sleeved on the other end of the crankshaft 21 to cooperate with the crankshaft 21 in circumferential transmission. That is, the crankshaft 21 can drive the eccentric portion 231 to rotate eccentrically inside the cylinder 23, thereby compressing the refrigerant during the rotation.

[0064] The maximum outer diameter of the rotor core 12 is D1, the axial height of the rotor core 12 is H2, and the distance between the centerline of the eccentric part 231 and the centerline of the crankshaft 21 is e, satisfying: 0.04 ≤ ≤0.18, meaning the ratio of the square root of e to the product of D1 and H2 is between 0.04 and 0.18. By setting the values ​​to 0.05, 0.06, 0.07, 0.08, 0.09, 0.13, 0.15, 0.17, etc., and by setting the relationship between the above structural parameters between 0.04 and 0.18, the rotary compressor 100 can have greater driving performance and improve the energy efficiency of the rotary compressor 100.

[0065] Specifically, in actual design, the maximum outer diameter D1 of the rotor core 12 and the axial height H2 of the rotor core 12 can be set to be relatively large, so that the rotor core 12 has a larger structural volume. The rotor core 12 has a larger moment of inertia during rotation, which can drive a larger volume of refrigerant for compression, thus improving the energy efficiency of the rotary compressor 100. It also avoids the reduced stability of motor 1 due to excessively large structural dimensions of the rotor core 12, ensuring the reliability of motor 1 operation. At the same time, the larger the distance e between the centerline of the eccentric part 231 and the centerline of the crankshaft 21, the greater the compression of the eccentric part 231, which is beneficial for increasing the compression volume. It should be noted that when the rotary compressor 100 operates at low frequency, the combination design of the larger rotor core 12 and the larger eccentric part 231 with the distance e between the centerline and the centerline of the crankshaft 21 results in greater working efficiency of the rotary compressor 100 at low frequency, enabling high-load refrigerant compression and increasing the working efficiency of the rotary compressor 100. However, when the rotary compressor 100 operates at high frequency, the combination design of the larger rotor core 12 and the larger eccentric part 231 with the distance e between the centerline and the centerline of the crankshaft 21 causes the rotation amplitude of the rotor core 12 to be too large. At the same time, the vibration generated by the rotation of the crankshaft 21 and the eccentric part 231 becomes more obvious, and the corresponding frictional resistance is also greater.

[0066] Therefore, this application will Setting the value between 0.04 and 0.18 allows for the maximization of the energy efficiency of the rotary compressor 100 while reducing the rotational resistance of the rotor core 12 and the pump body component 2, thus improving the energy efficiency of the rotary compressor 100. Furthermore, this dimensional design enables the rotary compressor 100 to achieve better energy efficiency in both low-frequency and high-frequency operation, adapting to energy efficiency requirements under different operating conditions.

[0067] Furthermore, in other embodiments, the following condition is satisfied: 0.09 ≤ ≤0.11, meaning the ratio of the square root of e to the product of D1 and H2 is between 0.09 and 0.11. By setting the values ​​to 0.091, 0.092, 0.095, 0.098, 0.101, 0.103, 0.105, 0.110, etc., and setting the relationship between the above structural parameters between 0.09 and 0.11, the rotary compressor 100 can have greater driving performance and improve the energy efficiency of the rotary compressor 100.

[0068] It should be noted that, as shown in Figure 8, in conjunction with the figure... The relationship between the energy efficiency of the rotary compressor 100 and the overall energy efficiency shows a normal distribution, which means that... When the parameter value is set to be between 0.04 and 0.18, the energy efficiency of the rotary compressor 100 is greater than that corresponding to other values, especially when the parameter value is between 0.09 and 0.11. In other words, the highest energy efficiency point is between the energy efficiency corresponding to 0.09 and 0.11. Thus, in the present application, the parameter value is defined as 0.09. By sequentially limiting the parameter value in the above range, the design of maximizing the energy efficiency of the rotary compressor 100 can be realized while reducing the rotation resistance of the rotor core 12 and the pump body part 2, which is beneficial to improving the energy efficiency of the rotary compressor 100.

[0069] In some embodiments, 3.5mm≤e≤5.5mm is satisfied, i.e., the distance e between the center line of the eccentric part 231 and the center line of the crankshaft 21 is set to be between 3.5mm and 5.5mm, such as 3.6mm, 3.8mm, 3.9mm, 4.1mm, 4.5mm, 4.8mm, 4.9mm, 5.2mm, etc., thereby setting the distance e between the center line of the eccentric part 231 and the center line of the crankshaft 21 in the above range, which is beneficial to improving the energy efficiency of the rotary compressor 100.

[0070] Specifically, the distance e between the center line of the eccentric part 231 and the center line of the crankshaft 21 is set to be greater than or equal to 3.5mm, so that the eccentric part 231 has a larger compression range, realizing the rotary compressor 100 for a larger volume of refrigerant, thereby enhancing the compression efficiency. At the same time, the distance e between the center line of the eccentric part 231 and the center line of the crankshaft 21 is set to be less than or equal to 5.5mm, avoiding the situation that the size is too large, which causes the rotary compressor 100 to have excessive rotational inertia of the eccentric part 231 when operating at high frequency, resulting in excessive vibration noise and friction resistance, reducing the loss, and being beneficial to improving the overall energy efficiency.

[0071] In some embodiments, 20mm≤H2≤80mm, i.e., the axial height H2 of the rotor core 12 is set to be between 20mm and 80mm, such as 23mm, 27mm, 34mm, 41mm, 55mm, 67mm, 71mm, 72mm, etc., thereby setting the axial height H2 of the rotor core 12 in the above range, which is beneficial to improving the energy efficiency of the rotary compressor 100.

[0072] Specifically, the axial height H2 of the rotor core 12 is set to be greater than or equal to 20 mm, so that the rotor core 12 has a larger structural volume, a greater range of rotational torque output is achieved, and compression of a larger volume of refrigerant is facilitated, thereby enhancing the compression efficiency. Meanwhile, the axial height H2 of the rotor core 12 is set to be less than or equal to 80 mm, so that the rotor core 12 does not have excessively large rotational inertia when the rotary compressor 100 is operated at a high frequency, thereby preventing excessive vibration noise and frictional resistance, reducing losses, and facilitating improvement of the overall energy efficiency.

[0073] In some embodiments, as shown in FIG. 2, the maximum outer profile radius of the stator core 11 is R2 and the maximum outer profile diameter is D4, the axial height of the stator core 11 is H3, the axial height of the cylinder 23 is H1, and the following conditions are satisfied: D4 = 2 R2, and 1.3 ≤ ≤ 8.8, i.e., the ratio between the product of the maximum outer profile diameter D4 of the stator core 11 and the axial height H3 of the stator core 11 and the axial height H1 of the cylinder 23 is between 1.3 and 8.8, so that the rotary compressor 100 has a larger working energy efficiency. Specifically, the ratio can be set to 1.3, 1.8, 2.2, 3.4, 5.3, 5.5, 6.8, 6.9, 7.2, 8.1, etc.

[0074] Specifically, the maximum outer profile diameter D4 of the stator core 11 and the axial height H3 of the stator core 11 are positively correlated with the volume of the stator core 11. Thus, the greater the product of D4 and H3, the larger the stator core 11, the greater the power that can drive the rotor core 12 to rotate, and the greater the displacement that can be achieved, facilitating compression of a larger volume of refrigerant. The greater the axial height H1 of the cylinder 23, the greater the volume of the cylinder 23, the greater the volume of refrigerant that can be compressed, and the greater the refrigerant compression capacity that can be achieved. Thus, the ratio is set to be greater than or equal to 1.3, so that the stator core 11 can drive a larger displacement of the cylinder 23 to operate, and a larger displacement of refrigerant compression is achieved. Thus, the ratio is set to be less than or equal to 1.3, so that the stator core 11 does not have excessively large dimensions, preventing excessively high costs, preventing the stator core 11 from occupying excessively large space in the rotary compressor 100, and preventing the axial dimensions of the cylinder 23 from being excessively large, thereby reducing mechanical wear and tear and reducing the current consumption of the motor 1 and the electrical control, thereby improving the overall energy efficiency.

[0075] In other embodiments, the following conditions are satisfied: 2.3 ≤ ​​≤2.7. That is, the ratio between the square root of the product of the maximum outer diameter D4 of the stator core 11 and the axial height H3 of the stator core 11, and the axial height H1 of the cylinder 23, is between 2.3 and 2.7, so that the rotary compressor 100 has a higher working efficiency. Specifically, it can be... The values ​​can be set to 2.3, 2.32, 2.35, 2.41, 2.52, 2.56, 2.67, 2.69, 2.7, etc.

[0076] Therefore, Setting it to 2.3 or greater allows the stator core 11 to drive a larger displacement cylinder 23, achieving larger displacement refrigerant compression. Setting it to less than or equal to 2.7 can prevent the stator core 11 from being too large, which would lead to excessive setup costs, and prevent the stator core 11 from occupying too much space within the rotary compressor 100.

[0077] It should be noted that, as shown in Figure 9, in conjunction with the figure... The relationship between the energy efficiency of the rotary compressor 100 and the overall energy efficiency shows a normal distribution, which means that... When the parameter value is set between 1.3 and 8.8, the energy efficiency of the rotary compressor 100 is higher than that corresponding to other values, especially in... When the efficiency rating is between 2.3 and 2.7, the energy efficiency of the rotary compressor 100 is more concentrated. In other words, the highest energy efficiency point is located between 2.3 and 2.7. Therefore, in this application... By limiting the parameters to the above range, the design can maximize the energy efficiency of the rotary compressor 100 while reducing the cost of setting the rotor core 12 and cylinder 23, which is beneficial to improving the energy efficiency of the rotary compressor 100.

[0078] In some embodiments, as shown in FIG3, the inner diameter of cylinder 23 is D3, and satisfies: 0.59 ≤ ≤3.11, meaning the ratio between the square root of the product of the maximum outer diameter D4 of the stator core 11 and the axial height H3 of the stator core 11 and the inner diameter D3 of the cylinder 23 is between 0.59 and 3.11, is to ensure that the rotary compressor 100 has a higher working efficiency. Specifically, it can be... Set to 0.6, 0.7, 1.35, 1.41, 1.52, 2.11, 2.67, 2.69, 3.11, etc.

[0079] Specifically, the outer diameter D4 of the maximum outer circle of the stator core 11 and the axial height H3 of the stator core 11 are both positively correlated with the volume of the stator core 11. Therefore, the larger the product of D4 and H3, the larger the stator core 11, the greater the power it can generate to drive the rotor core 12, and the larger the displacement that can be achieved, which is beneficial for achieving larger volume refrigerant compression. The larger the inner diameter D3 of the cylinder 23, the larger the volume within the cylinder 23, the larger the volume of refrigerant that can be compressed, and the greater the amount of refrigerant compression that can be achieved. Thus, Setting it to greater than or equal to 0.59 allows the stator core 11 to drive a larger displacement cylinder 23, achieving larger displacement refrigerant compression, and Setting it to less than or equal to 3.11 can prevent the stator core 11 from being too large, which would lead to excessive setup costs, prevent the stator core 11 from occupying too much space in the rotary compressor 100, and prevent the cylinder 23 from being too large, which would lead to excessive mechanical wear. This will reduce the current consumption of the motor 1 and the electronic control system, and improve the overall energy efficiency of the machine.

[0080] In other embodiments, the following condition is satisfied: 1.0 ≤ ≤1.2. That is, the ratio between the square root of the product of the maximum outer diameter D4 of the stator core 11 and the axial height H3 of the stator core 11, and the inner diameter D3 of the cylinder 23, is between 1.0 and 1.2, so that the rotary compressor 100 has a higher working efficiency. Specifically, it can be... Set to 1.02, 1.05, 1.11, 1.13, 1.15, 1.16, 1.17, 1.19, 1.2, etc.

[0081] Therefore, Setting it to a value greater than or equal to 1.0 allows the stator core 11 to drive a larger displacement cylinder 23, achieving larger displacement refrigerant compression. Setting it to less than or equal to 1.2 can prevent the stator core 11 from being too large, which would lead to excessive setup costs and prevent the stator core 11 from occupying too much space within the rotary compressor 100.

[0082] It should be noted that, as shown in Figure 10, in conjunction with the figure... The relationship between the energy efficiency of the rotary compressor 100 and the overall energy efficiency shows a normal distribution, which means that... When the parameter value is set between 0.59 and 3.11, the energy efficiency of the rotary compressor 100 is higher than that corresponding to other values, especially in... When the efficiency rating is between 1.0 and 1.2, the energy efficiency of the rotary compressor 100 is more concentrated. In other words, the highest energy efficiency point is located between 1.0 and 1.2. Therefore, in this application... By sequentially limiting the above parameters within the range, the design of maximizing the energy efficiency of the rotary compressor 100 can be achieved while reducing the setting cost of the rotor core 12 and the cylinder 23, which is conducive to improving the energy efficiency of the rotary compressor 100.

[0083] In some embodiments, 20mm≤H3≤80mm is satisfied, that is, the axial height H3 of the stator core 11 can be set to be within 20mm-80mm, such as 23mm, 27mm, 34mm, 41mm, 55mm, 67mm, 71mm, 72mm, etc., thereby setting the axial height H3 of the stator core 11 within the above range, which is conducive to improving the energy efficiency of the rotary compressor 100.

[0084] Specifically, the axial height H3 of the stator core 11 is set to be greater than or equal to 20mm, so that the stator core 11 has a larger structural volume, and a larger range of rotational torque can be formed on the rotor core 12, which is conducive to compressing a larger volume of refrigerant and thereby enhancing the compression efficiency. At the same time, the axial height H3 of the stator core 11 is set to be less than or equal to 80mm, which avoids the stator core 11 occupying too much space in the rotary compressor 100 and reduces the setting cost of the stator core 11.

[0085] In other embodiments, 34mm≤D3≤71mm, that is, the inner diameter D3 of the cylinder 23 can be set to be within 34mm-71mm, such as 34mm, 41mm, 55mm, 67mm, 71mm, etc., thereby setting the inner diameter D3 of the cylinder 23 within the above range, which is conducive to improving the energy efficiency of the rotary compressor 100.

[0086] Specifically, the inner diameter D3 of the cylinder 23 is set to be greater than or equal to 34mm, so that the cylinder 23 has a larger volume, which is conducive to compressing a larger volume of refrigerant and thereby enhancing the compression efficiency. At the same time, the inner diameter D3 of the cylinder 23 is set to be less than or equal to 71mm, which avoids the cylinder 23 occupying too much space in the rotary compressor 100 and reduces the setting cost of the cylinder 23.

[0087] In yet other embodiments, 12mm≤H1≤32mm, that is, the axial height H1 of the cylinder 23 can be set to be within 12mm-32mm, such as 13mm, 17mm, 24mm, 25mm, 26mm, 27mm, 31mm, 32mm, etc., thereby setting the axial height H1 of the cylinder 23 within the above range, which is conducive to improving the energy efficiency of the rotary compressor 100.

[0088] Specifically, the axial height H1 of the cylinder 23 is set to be greater than or equal to 12 mm, so that the cylinder 23 has a larger volume, facilitating the compression of a larger volume of refrigerant, thereby enhancing the compression efficiency, and at the same time, the axial height H1 of the cylinder 23 is set to be less than or equal to 32 mm, avoiding that the size is too large to cause the cylinder 23 to occupy too much space in the rotary compressor 100, and reducing the setting cost of the cylinder 23.

[0089] In some embodiments, 15≤Q≤18, that is, the number Q of stator slots 113 is set to be between 15 and 18, such as 15, 16, 17 or 18, the number Q of stator slots 113 is set to be greater than or equal to 15, so that the number of stator windings 114 is larger to drive the rotor core 12 to effectively output power, achieving powerful driving of the eccentric part 231, and at the same time, the number Q of stator slots 113 is set to be less than or equal to 18, avoiding that the size of the stator core 11 is too large to cause the setting cost to be too high, facilitating the reasonable arrangement of the stator core 11 in the rotary compressor 100.

[0090] In other embodiments, 10≤P≤12, that is, the number P of poles of the rotor is set to be between 10 and 12, such as 10, 11 or 12, the number P of poles of the rotor is set to be greater than or equal to 10, so that the power output by the rotor core 12 is larger, achieving powerful driving of the eccentric part 231, facilitating an increase in the compression amount of the refrigerant, and at the same time, the number P of poles of the rotor is set to be less than or equal to 12, avoiding that the size of the rotor is too large to cause the setting cost to be too high, facilitating the reasonable arrangement of the rotor in the rotary compressor 100.

[0091] In some embodiments, the number of slots per pole per phase of the motor 1 is q, the number of phases of the motor 1 is m, q= , and satisfies 0

[0092] In some embodiments, 23mm≤R1≤39mm, that is, the radius R1 of the rotor core 12 is set to be between 23 mm and 39 mm, such as 23 mm, 27 mm, 29 mm, 31 mm, 32 mm, 33 mm, 37 mm or 39 mm, thereby setting the radius R1 of the rotor core 12 in the above range, facilitating an improvement in the energy efficiency of the rotary compressor 100.

[0093] Specifically, the radius R1 of the rotor core 12 is set to be greater than or equal to 23 mm, so that the rotor core 12 has a larger structural volume, realizes a greater range of output of rotational torque, is conducive to compressing a larger volume of refrigerant, and further enhances the compression efficiency. At the same time, the radius R1 of the rotor core 12 is set to be less than or equal to 39 mm, so as to avoid that the size is too large to cause the rotor core 12 to generate too large rotational inertia when the rotary compressor 100 is operated at a high frequency, resulting in too large vibration noise and friction resistance, reducing the loss, and being conducive to improving the overall energy efficiency.

[0094] In other embodiments, 45 mm≤R2≤70 mm, that is, the radius R2 of the stator core 11 can be set to be between 45 mm and 70 mm, such as 45 mm, 47 mm, 49 mm, 51 mm, 52 mm, 63 mm, 67 mm, 70 mm, and the like. Thus, the radius R2 of the stator core 11 is set in the above range, which is conducive to improving the energy efficiency of the rotary compressor 100.

[0095] Specifically, the radius R2 of the stator core 11 is set to be greater than or equal to 45 mm, so that the stator core 11 can be provided with more stator windings 114, and further output larger rotational torque to the rotor core 12, which is conducive to compressing a larger volume of refrigerant, and further enhances the compression efficiency. At the same time, the radius R2 of the stator core 11 is set to be less than or equal to 70 mm, so as to avoid that the size is too large to cause the rotary compressor 100 to drive the rotor core 12 to generate too large rotational inertia when operated at a high frequency, resulting in too large vibration noise and friction resistance, reducing the loss, and being conducive to improving the overall energy efficiency.

[0096] In other embodiments, 45 mm≤R2≤70 mm, that is, the radius R2 of the stator core 11 can be set to be between 45 mm and 70 mm, such as 45 mm, 47 mm, 49 mm, 51 mm, 52 mm, 63 mm, 67 mm, 70 mm, and the like. Thus, the radius R2 of the stator core 11 is set in the above range, which is conducive to improving the energy efficiency of the rotary compressor 100.

[0097] Specifically, the radius R2 of the stator core 11 is set to be greater than or equal to 45 mm, so that the stator core 11 can be provided with more stator windings 114, and further output larger rotational torque to the rotor core 12, which is conducive to compressing a larger volume of refrigerant, and further enhances the compression efficiency. At the same time, the radius R2 of the stator core 11 is set to be less than or equal to 70 mm, so as to avoid that the size is too large to cause the rotary compressor 100 to drive the rotor core 12 to generate too large rotational inertia when operated at a high frequency, resulting in too large vibration noise and friction resistance, reducing the loss, and being conducive to improving the overall energy efficiency.

[0098] As shown in Fig. 6, the compressor 100 further comprises a liquid accumulator 200, which is in communication with the cylinder 23 of the rotary compressor 100 through a pipe, so that the refrigerant in the liquid accumulator 200 can enter the cylinder 23 through the pipe for compression.

[0099] The application further provides a refrigeration equipment.

[0100] The refrigeration equipment according to the embodiments of the application comprises the rotary compressor 100 of any of the above embodiments, by limiting the sizes of the stator core 11, the rotor core 12 and the pump body part 2 within the above ranges, the stator can generate a large enough driving force on the rotor core 12, so as to realize powerful driving of the rotor core 12, the rotor core 12 and the crankshaft 21 can output effective driving force to compress refrigerant with a larger volume, meanwhile, the structural sizes of the rotor core 12 and the stator core 11 and the like can be prevented from being too large, the reasonable cost of the control structure part is set, and when the rotary compressor 100 is operated at high or low frequency, good operation efficiency can be ensured, and the power consumption of the rotary compressor 100 is reduced.

[0101] In the description of the present specification, the description referring to the terms "one embodiment", "some embodiments", "exemplary embodiment", "example", "specific example", or "some examples" and the like means that the specific features, structures, materials or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present application. In the present specification, the exemplary description of the above terms does not necessarily mean the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described can be combined in any one or more embodiments or examples in a suitable manner.

[0102] Although the embodiments of the present application have been shown and described, those skilled in the art can understand that various changes, modifications, replacements and variations can be made to the embodiments without departing from the principles and purposes of the present application, and the scope of the present application is defined by the claims and their equivalents.

Claims

1. A rotary compressor, wherein, Comprising: a motor, the motor comprising a stator and a rotor, the rotor being located within the stator, the stator comprising a stator core and a stator winding, the stator core comprising a yoke portion configured in a ring shape and a plurality of tooth portions provided within the yoke portion, the plurality of tooth portions being spaced apart along a circumferential direction of the yoke portion, and a stator slot being formed between two adjacent tooth portions, the stator winding being wound around the stator slot, the rotor comprising a rotor core; a pump body component, the pump body component comprising a crankshaft, an upper bearing, and a cylinder, one end of the crankshaft being connected to the rotor core, the other end of the crankshaft being sequentially provided through the upper bearing and the cylinder; Wherein, the number of the stator slots is Q, the pole number of the rotor is P, the maximum outer profile radius of the rotor core is R1 and the maximum outer profile outer diameter is D1, D1=2*R1, the outer diameter of the crankshaft and the upper bearing matching part is D2, GCD(Q, P) is the greatest common divisor of Q and P, and satisfies: 0.7 ≤ GCD(Q, P) / Q < 1.0 ≤2.7，1＜ ＜3，5≤ ≤6。 2. The rotary compressor of claim 1, wherein, satisfies: 0.9 ≤ ≤ 1.

8.

3. The rotary compressor of claim 2, wherein the following is satisfied: 1.05≤ ≤1.1。 4. The rotary compressor of any one of claims 1-3, wherein, an eccentric portion being provided outside the other end of the crankshaft, the eccentric portion being located within the cylinder and eccentrically rotating within the cylinder; In the formula, the axial height of the rotor core is H2, the distance between the center line of the eccentric portion and the center line of the crankshaft is e, and the following is satisfied: 0.04 ≤ e / H2 ≤ 0.20 ≤0.18。 5. The rotary compressor of claim 4, wherein, satisfies: 0.09 ≤ ≤ 0.

11.

6. The rotary compressor of any one of claims 1-5, wherein, The maximum outer circular profile radius of the stator core is R2 and the maximum outer circular profile outer diameter is D4, the axial height of the stator core is H3, the axial height of the cylinder is H1, and the following is satisfied: D4 = 2R2, and the following is satisfied: 1.3 ≤ H3 / H1 ≤ 8.

8. ≤8.

8.

7. The rotary compressor of claim 6, wherein the following is satisfied: 0.5 < L < 1.

5. 2.3≤ ≤2.7。 8. The rotary compressor of claim 6 or 7, wherein, The inner diameter of the cylinder is D3, and satisfies: 0.59≤D3 / D1≤3.

11. ≤3.

11.

9. The rotary compressor of claim 8, wherein, satisfying: 1.0≤ ≤1.2。 10. The rotary compressor of claim 8 or 9, wherein, satisfying: 34mm≤D3≤71mm; and / or, satisfying: 12mm≤H1≤32mm.

11. The rotary compressor of any one of claims 6-10, wherein, satisfying: 23mm≤R1≤39mm; and / or, satisfying: 45mm≤R2≤70mm.

12. The rotary compressor of any one of claims 1-11, wherein, satisfying: 15≤Q≤18; and / or, 10≤P≤12.

13. The rotary compressor of any one of claims 1-12, wherein, The number of slots per pole per phase of the motor is q, the number of phases of the motor is m, q = m , and 0 < q < 1 is satisfied.

14. A refrigeration appliance, wherein, A rotary compressor comprising any one of claims 1-13.

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