Rotary compressor and refrigeration equipment

Abstract

The utility model discloses a rotary compressor and refrigeration equipment, and relates to the technical field of compressors, the rotary compressor comprises a motor, the motor comprises a stator and a rotor, the stator comprises a stator iron core and a stator winding, the stator iron core comprises an annular yoke part and a plurality of tooth parts arranged in the yoke part, the plurality of tooth parts are spaced along the circumferential direction of the yoke part, and the stator winding is arranged in the yoke part; a stator groove is formed between every two adjacent tooth parts, the stator winding is wound in the stator grooves, and the rotor comprises a rotor iron core; the pump body part comprises a crankshaft, an upper bearing and a cylinder; the number of the stator grooves is Q, the number of poles of the rotor is P, the maximum outer circle contour radius of the rotor core is R1, the maximum outer circle contour outer diameter is D1, D1 = 2 * R1, the outer diameter of the part, matched with the upper bearing, of the crankshaft is D2, GCD (Q, P) is the largest common divisor of Q and P, and GCD (Q, P) is larger than or equal to # imgabs0 # 5 and smaller than or equal to 6. The rotary compressor disclosed by the utility model is beneficial to improving the energy efficiency of the rotary compressor and reducing the electric energy consumption during operation.

Description

Technical Field

[0001] The utility model relates to the technical field of compressors, in particular to a rotary compressor and a refrigeration device having the rotary compressor. Background Art

[0002] In related technologies, electric motors, as important devices for converting electrical energy into mechanical energy, play a key role in a variety of fields, including rotary compressors, refrigeration equipment, and household appliances. Electric motors primarily consist of a stator assembly and a rotor assembly. Current in the stator windings generates a rotating magnetic field that interacts with the rotor magnets in the rotor assembly, generating a rotational torque. However, current electric motors used in rotary compressors, when used in conjunction with pump components, exhibit low work efficiency and high energy consumption, leaving room for improvement. Utility Model Content

[0003] The present invention aims to solve at least one of the technical problems existing in the prior art. To this end, the present invention provides a rotary compressor that, by limiting the parameters of the motor and pump components, achieves higher energy efficiency during actual work, thereby reducing power consumption.

[0004] According to an embodiment of the present invention, a rotary compressor comprises: a motor, the motor comprising a stator and a rotor, the rotor being located in the stator, the stator comprising a stator core and a stator winding, the stator core comprising a yoke constructed in an annular shape and a plurality of teeth arranged in the yoke, the plurality of teeth being spaced apart along the circumference of the yoke, and a stator slot being formed between two adjacent teeth, the stator winding being wound in the stator slot, and 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, 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 contour radius of the rotor core is R1 and the maximum outer contour outer diameter is D1, D1=2*R1, the outer diameter of the matching portion of the crankshaft and the upper bearing is D2, GCD(Q, P) is the greatest common divisor of Q and P, and satisfies: 5≤GCD(Q,P)≤6.

[0005] According to the rotary compressor of the embodiment of the present invention, by limiting the sizes of the stator core, the rotor core and the pump body components within the above range, the stator can generate a sufficiently large driving force on the rotor core, thereby realizing a powerful drive of the rotor core. The rotor core and the crankshaft can output an effective driving force to compress a larger volume of refrigerant. At the same time, it can also avoid the structural dimensions of the rotor core and the stator core being too large, and the reasonable cost of the structural component setting can be controlled. The range of 0.7 to 2.7 allows the rotor core and crankshaft to form a sufficiently effective and stable driving force when the rotary compressor is running at a low frequency, reducing the fluctuation of the motor rotation, achieving effective compression of the refrigerant, and improving the overall energy efficiency of the rotary compressor. At the same time, it can avoid the structural dimensions of the rotor core and crankshaft being too large, and avoid the excessive rotational inertia of the rotor core and crankshaft causing large vibration noise when the rotary compressor is running at a high frequency. At the same time, it also reduces the friction energy consumption of the rotor core and crankshaft due to the excessive rotational inertia, which is also beneficial to improving the energy efficiency of the rotary compressor.

[0006] According to some embodiments of the present invention, the rotary compressor meets the following requirements:

[0007] According to some embodiments of the present invention, the rotary compressor meets the following requirements:

[0008] According to some embodiments of the rotary compressor of the present invention, an eccentric portion is provided on the other end of the crankshaft, and the eccentric portion is located in the cylinder and rotates eccentrically in the cylinder;

[0009] The axial height of the rotor core is H2, the distance between the centerline of the eccentric portion and the centerline of the crankshaft is e, and the following conditions are satisfied:

[0010] According to some embodiments of the present invention, the rotary compressor meets the following requirements:

[0011] According to the rotary compressor of some embodiments of the present invention, the maximum outer circle radius of the stator core is R2 and the maximum outer circle outer diameter is D4, the axial height of the stator core is H3, the axial height of the cylinder is H1, and the following conditions are satisfied: D4=2R2, and the following conditions are satisfied:

[0012] According to some embodiments of the present invention, the rotary compressor meets the following requirements:

[0013] According to some embodiments of the rotary compressor of the present invention, the inner diameter of the cylinder is D3 and satisfies:

[0014] According to some embodiments of the present invention, the rotary compressor meets the following requirements:

[0015] According to some embodiments of the present invention, the rotary compressor satisfies: 34 mm ≤ D3 ≤ 71 mm; and / or satisfies: 12 mm ≤ H1 ≤ 32 mm.

[0016] According to some embodiments of the present invention, the rotary compressor satisfies the following conditions: 23 mm ≤ R1 ≤ 39 mm;

[0017] And / or, satisfy: 45mm≤R2≤70mm.

[0018] According to some embodiments of the present invention, the rotary compressor satisfies the following conditions: 15≤Q≤18;

[0019] And / or, satisfies: 10≤P≤12.

[0020] According to the rotary compressor of some embodiments of the present invention, the number of slots per pole and per phase of the motor is q, the number of phases of the motor is m, And it satisfies: 0<q<1.

[0021] The utility model also provides a refrigeration device.

[0022] A refrigeration device according to an embodiment of the present invention includes a rotary compressor according to any one of the above embodiments.

[0023] The advantages of the refrigeration device and the above-mentioned rotary compressor over the prior art are the same and will not be described in detail here.

[0024] Additional aspects and advantages of the present invention will be given in part in the following description and will become apparent from the following description or learned through practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0025] The above and / or additional aspects and advantages of the present invention will become apparent and readily understood from the description of the embodiments in conjunction with the following drawings, in which:

[0026] Figure 1 is a cross-sectional view of a rotary compressor according to an embodiment of the present utility model;

[0027] Figure 2 Schematic diagram of the structure of the motor of the embodiment of the present utility model (stator winding is not shown);

[0028] Figure 3 It is a structural schematic diagram of the cylinder of the motor according to an embodiment of the present utility model;

[0029] Figure 4 It is a structural diagram of a motor according to an embodiment of the present utility model;

[0030] Figure 5 It is a cross-sectional view of a rotary compressor (with a housing) according to an embodiment of the present utility model;

[0031] Figure 6 It is a structural schematic diagram of a rotary compressor (including a liquid accumulator) according to an embodiment of the present utility model;

[0032] Figure 7 The compressor of the embodiment of the utility model is rotated Relationship diagram with energy efficiency;

[0033] Figure 8 The compressor of the embodiment of the utility model is rotated Relationship diagram with energy efficiency;

[0034] Figure 9 The compressor of the embodiment of the utility model is rotated Relationship diagram with energy efficiency;

[0035] Figure 10 The compressor of the embodiment of the utility model is rotated Relationship diagram with energy efficiency.

[0036] Reference numerals:

[0037] Rotary compressor 100,

[0038] Motor 1, stator core 11, yoke 111, teeth 112, stator slots 113, stator winding 114, rotor core 12, rotor magnet 121,

[0039] Pump body component 2, crankshaft 21, upper bearing 22, cylinder 23, eccentric part 231, lower bearing 24,

[0040] Shell 3,

[0041] Liquid reservoir 200. DETAILED DESCRIPTION

[0042] The following describes embodiments of the present invention in detail. Examples of the embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are intended only to explain the present invention and are not to be construed as limiting the present invention.

[0043] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings. They are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present invention. In addition, features defined as "first" or "second" may explicitly or implicitly include one or more of such features. In the description of the present invention, unless otherwise specified, "multiple" means two or more.

[0044] In the description of this utility model, it should be noted that, unless otherwise expressly specified or limited, the terms "mounted," "connected," and "connected" should be understood in a broad sense. For example, they can refer to fixed connections, detachable connections, or integral connections; mechanical connections, electrical connections; direct connections, indirect connections through an intermediate medium, and internal communication between two components. Those skilled in the art will understand the specific meanings of the above terms in this utility model based on the specific circumstances.

[0045] Reference below Figures 1-6 A rotary compressor 100 according to an embodiment of the present invention is described. The rotary compressor 100 limits the relationship between multiple parameters of the motor 1 and multiple parameters of the pump body component 2, so that the rotary compressor 100 can have higher work efficiency when designed and works with parameters within the limited range, which is beneficial to reducing the power consumption during the operation of the rotary compressor 100, reducing the operating cost of the rotary compressor 100, and meeting the design requirements.

[0046] like Figures 1-6 As shown, a rotary compressor 100 according to an embodiment of the present invention includes: a motor 1 and a pump body component 2. The rotary compressor 100 further includes a housing 3, in which the motor 1 and the pump body component 2 are installed.

[0047] like Figure 1 and Figure 5As shown, the motor 1 includes a stator and a rotor. The rotor is located inside the stator, that is, the stator is sleeved on the outside of the rotor so that the center lines of the stator and the rotor coincide with each other. The stator includes a stator core 11 and a stator winding 114. The stator core 11 includes a yoke 111 having an annular structure and a plurality of teeth 112 arranged in the yoke 111. The plurality of teeth 112 are spaced apart along the circumference of the yoke 111, and a stator slot 113 is formed between two adjacent teeth 112. The stator winding 114 is wound in the stator slot 113. Specifically, as shown in FIG. Figure 2 As shown, the yoke 111 of the stator core 11 can be constructed as a circular ring, and the tooth portion 112 is arranged to extend radially inward on the inner circumferential wall of the yoke 111. A plurality of tooth portions 112 are distributed circumferentially spaced apart on the inner side of the yoke 111, and a 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.

[0048] That is, there are also multiple stator windings 114, and the multiple stator windings 114 are respectively wound around the multiple teeth 112 in a one-to-one correspondence. At the same time, the rotor includes a rotor core 12, which is located within the stator core 11 and the axes of the two coincide. Specifically, a plurality of magnetic steel slots are provided on the outer peripheral wall of the rotor core 12. The plurality of magnetic steel slots are spaced apart and distributed in the circumferential direction of the rotor core 12, and a rotor magnet 121 is provided in each magnetic steel slot. Therefore, when the stator windings 114 are energized, the current in the stator windings 114 generates a rotating magnetic field, which interacts with the rotor magnets 121, thereby generating a rotational torque, driving the rotor core 12 to rotate.

[0049] like Figure 1 and Figure 5 As shown, the pump body component 2 includes a crankshaft 21, an upper bearing 22, and a cylinder 23. One end of the crankshaft 21 is connected to the rotor core 12, and the other end of the crankshaft 21 is inserted into the upper bearing 22 and the cylinder 23. A piston cavity is formed in the cylinder 23, and an eccentric portion 231 is installed in the piston cavity. The eccentric portion 231 can be fixedly connected to the other end of the crankshaft 21. Therefore, 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 portion 231 to rotate eccentrically in the cylinder 23. The cylinder 23 can be connected to the liquid reservoir 200 so that the refrigerant in the liquid reservoir 200 flows into the piston cavity of the cylinder 23, and the refrigerant is compressed under the eccentric rotation of the eccentric portion 231. The pump body component 2 may also include a lower bearing 24, the upper bearing 22 and the lower bearing 24 are fixed in the housing 3, the cylinder 23 is located between the upper bearing 22 and the lower bearing 24, and the crankshaft 21 is sequentially passed through the upper bearing 22, the cylinder 23 and the lower bearing 24.

[0050] The number of stator slots 113 is Q, the number of rotor poles is P, the maximum outer contour radius of the rotor core 12 is R1 and the maximum outer contour outer diameter is D1, D1=2*R1, the outer diameter of the matching portion 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: 5≤GCD(Q, P)≤6, that is, the rotary compressor 100 in the present invention can simultaneously satisfy the parameter relationships defined in the above three formulas, so that the rotary compressor 100 has higher working energy efficiency.

[0051] Specifically, GCD (Greatest Common Divisor) means the greatest common divisor, and GCD(Q, P) is the greatest common divisor of the number Q of stator slots 113 and the number P of rotor poles, where 5≤GCD(Q, P)≤6, that is, the greatest common divisor of the number Q of stator slots 113 and the number P of rotor poles can be 5 or 6. For example, when Q is 15, P can be 10, and when Q is 18, P can be 12, that is, the present application can be applied to the rotary compressor 100 whose greatest common divisor of Q and P is 5 or 6.

[0052] at the same time, That is, the number Q of the stator slots 113 is greater than the number P of the rotor poles. For example, Q can be set to 15 and P can be set to 10, so that 1.5, or Q is set to 18 and P can be set to 12 to make is 1.5, of course, other combination settings can also be used, so that Between 1 and 3, such as 1.7, 1.6, etc. Among them, by setting It can be seen that the motor of the present invention is a fractional slot motor, which allows the compressor to take into account both the production cycle and the capacity of the winding equipment. However, the torque fluctuation of the fractional slot motor is large, and the electronic control needs to introduce a low-frequency torque compensation current when the compressor is running at a low frequency to reduce the vibration problem of the whole machine caused by the torque fluctuation. At the same time, the introduction of current will reduce the motor frequency. In the present invention, by setting GCD (Q, P) to 5 or 6, such as when Q is 15, P can be 10, and when Q is 18, P can be 12, the rotation fluctuation of the motor 1 can be effectively reduced by setting a larger slot pole common divisor. The corresponding low-frequency torque compensation current is also smaller. In addition, setting GCD (Q, P) to less than or equal to 6 can also avoid the motor's electrical frequency being too high, reduce the frequency of the magnetic field generated by the rotor alternating on the stator side, and ensure the motor efficiency.

[0053] as well as, like Figure 1As shown, the outer diameter of the portion where the crankshaft 21 and the upper bearing 22 meet is D2. Meanwhile, the outer diameter of the maximum outer circle of the rotor core 12 is D1. Therefore, the product of the greatest common divisor of the number Q of the stator slots 113 and the number P of the rotor poles and the outer diameter D2 of one end of the crankshaft 21 divided by the outer diameter D1 of the maximum outer circle of the rotor core 12 yields a value in the range of 0.7 to 2.7. It is 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 the rotor core 12 can generate, 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 further reduce low-frequency torque fluctuations and improve the efficiency of the motor 1. At the same time, the crankshaft 21 is connected to the inner diameter of the rotor core 12, and the crankshaft 21 in the pump body component 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 force during the rotation of the crankshaft 21 can be. However, it cannot be set too small while ensuring its structural strength. Therefore, Setting it between 0.7 and 2.7 can not only reduce the rotation fluctuation of the motor 1 and improve the efficiency of the motor 1, but also reduce the friction power consumption during the rotation of the crankshaft 1, thereby improving the compression energy efficiency, and avoid the situation where the setting size of the rotor core 12 and the crankshaft 21 is too large, resulting in excessive setting costs.

[0054] And will Setting it between 0.7 and 2.7 can make the rotor core 12 and the crankshaft 21 have a larger structural size, so that when the rotary compressor 100 is running at a low frequency, the rotor core 12 and the crankshaft 21 can form a sufficiently effective and stable driving force, and the rotation fluctuation of the motor 1 is small, which can achieve effective compression of the refrigerant and improve the overall energy efficiency of the rotary compressor 100. At the same time, it can avoid the structural size of the crankshaft 21 being too large, and avoid the rotary compressor 100 running at a high frequency. The rotor core 12 and the crankshaft 21 are too large to generate large vibration noise due to excessive rotational inertia. At the same time, it also reduces the friction energy consumption of the rotor core 12 and the crankshaft 21 due to excessive rotational inertia, which is also beneficial to improving the energy efficiency of the rotary compressor 100.

[0055] According to the rotary compressor 100 of the embodiment of the present invention, the sizes of the stator core 11, the rotor core 12 and the pump body component 2 are limited within the above range. By setting a fractional slot motor, the rotary compressor can take into account the production rhythm and the capacity of the winding equipment, while reducing the rotation fluctuation of the motor 1 and improving the operating efficiency of the motor 1. The rotor core 12 and the crankshaft 21 can output an effective driving force to compress a larger volume of refrigerant, and can also avoid the structural dimensions of the rotor core 12 and the stator core 11 being too large, and the reasonable cost of the control structure setting, and when the rotary compressor 100 is operating at high frequency or low frequency, The range of 0.7 to 2.7 can ensure good operating energy efficiency and reduce the power consumption of the rotary compressor 100.

[0056] In some embodiments, the following conditions are met: Among them, the outer diameter of one end of the crankshaft 21 is D2, that is, the outer diameter of the end of the crankshaft 21 that is installed and matched with the rotor core 12 is D2. At the same time, the maximum outer diameter of the outer circle of the rotor core 12 is D1. Therefore, the product of the greatest common divisor of the number Q of the stator slots 113 and the number of rotor poles P and the outer diameter D2 of one end of the crankshaft 21 is divided by the maximum outer diameter of the outer circle of the rotor core 12 D1, and the value is within the range of 0.9 to 1.8. They are 0.9, 1.1, 1.2, 1.4, 1.52, 1.56, 1.61, 1.7, etc.

[0057] Therefore, Setting it between 0.9 and 1.8 not only enables the motor 1 to compress a larger volume of refrigerant, thereby improving compression efficiency, but also avoids the situation where the rotor core 12 and the crankshaft 21 are too large in size, resulting in excessively high installation costs. In addition, making the above-mentioned parameter range more precise can make the rotor core 12 and the crankshaft 21 have larger structural dimensions, so that when the rotary compressor 100 is operating at low frequency, the rotor core 12 and the crankshaft 21 can form a sufficiently effective and stable driving force, more effectively reduce the fluctuation of the motor 1 operation, achieve effective compression of the refrigerant, and improve the overall energy efficiency of the rotary compressor 100. At the same time, it can avoid the structural dimensions of the rotor core 12 and the crankshaft 21 being too large, and avoid the rotary compressor 100 running at high frequency. The rotor core 12 and the crankshaft 21 are too large to produce large vibration noise due to excessive rotational inertia. At the same time, it also reduces the friction energy consumption of the rotor core 12 and the crankshaft 21 due to excessive rotational inertia, which is also beneficial to improving the energy efficiency of the rotary compressor 100, and thus making the relationship between the energy efficiency and cost of the rotary compressor 100 more balanced, meeting various design requirements.

[0058] In a further embodiment, it is satisfied that: Therefore, the product of the greatest common divisor of the number Q of the stator slots 113 and the number of rotor poles P and the outer diameter D2 of one end of the crankshaft 21 divided by the maximum outer diameter D1 of the rotor core 12 is within the range of 1.05 to 1.1, as shown in FIG. They are 1.06, 1.07, 1.08, 1.09, 1.1, etc.

[0059] Therefore, It is set between 1.05 and 1.1, so that the above parameter range is further precise, which can make the rotor core 12 and the crankshaft 21 have a larger structural size, so that when the rotary compressor 100 is running at a low frequency, the rotor core 12 and the crankshaft 21 can form a sufficiently effective and stable driving force, more effectively reduce the fluctuation of the motor 1 operation, achieve effective compression of the refrigerant, and improve the overall energy efficiency of the rotary compressor 100. At the same time, it can avoid the structural size of the rotor core 12 and the crankshaft 21 being too large, and avoid the rotary compressor 100 running at a high frequency. The rotor core 12 and the crankshaft 21 are too large to produce large vibration noise due to excessive rotational inertia. At the same time, it also reduces the friction energy consumption of the rotor core 12 and the crankshaft 21 due to excessive rotational inertia, which is also beneficial to improving the energy efficiency of the rotary compressor 100, and thus making the relationship between the energy efficiency and cost of the rotary compressor 100 more balanced, meeting various design requirements.

[0060] Among them, Figure 7 As shown in the figure, The relationship between the energy efficiency of the rotary compressor 100 and the energy efficiency of the rotary compressor 100 is shown to be normally distributed. When the parameter value is set to between 0.7 and 2.7, the energy efficiency of the rotary compressor 100 is greater than that corresponding to other values, especially When the value is between 0.9 and 1.8, the energy efficiency of the corresponding rotary compressor 100 is more concentrated and high. When the energy efficiency is limited to 1.05-1.1, the overall energy efficiency of the rotary compressor 100 is relatively high. In other words, the highest energy efficiency point is between the energy efficiencies corresponding to 1.05-1.1. By limiting the parameters in the above ranges, 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.

[0061] In some embodiments, as Figure 1 and Figure 5As shown, an eccentric portion 231 is provided on the outside of the other end of the crankshaft 21. The eccentric portion 231 is located in the cylinder 23 and rotates eccentrically in the cylinder 23. That is, the eccentric portion 231 can be fixedly sleeved on the outside of the other end of the crankshaft 21 to cooperate with the circumferential transmission of the crankshaft 21. That is, the crankshaft 21 can drive the eccentric portion 231 to rotate eccentrically in the cylinder 23, thereby realizing compression of the refrigerant during the rotation process.

[0062] The maximum outer diameter of the rotor core 12 is D1, the axial height of the rotor core 12 is H2, the distance between the center line of the eccentric portion 231 and the center line of the crankshaft 21 is e, and the following conditions are satisfied: That is, the ratio of the square root of the product of e and D1 and H2 is between 0.04 and 0.18. It is set to 0.05, 0.06, 0.07, 0.08, 0.09, 0.13, 0.15, 0.17, etc. 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.

[0063] 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 larger, so that the rotor core 12 has a larger structural volume. The rotor core 12 has a larger moment of inertia during rotation, and can drive a larger volume of refrigerant for compression, which is beneficial to improving the energy efficiency of the rotary compressor 100. It also avoids the structural size of the rotor core 12 being too large, which leads to a decrease in the stability of the motor 1, and ensures the reliability of the operation of the motor 1. At the same time, the larger the distance e between the center line of the eccentric portion 231 and the center line of the crankshaft 21, the greater the compression amount of the eccentric portion 231, which is beneficial to increasing the compression volume. It should be noted that when the rotary compressor 100 operates at low frequency, the combined design of the distance e between the center line of the larger rotor core 12 and the larger eccentric part 231 and the center line of the crankshaft 21 enables the rotary compressor 100 to have greater working efficiency in the low-frequency stage, realizes large-load refrigerant compression, and increases the working efficiency of the rotary compressor 100. When the rotary compressor 100 operates at high frequency, the combined design of the distance e between the center line of the larger rotor core 12 and the larger eccentric part 231 and the center line of the crankshaft 21 will make the rotation amplitude of the rotor core 12 too large, and at the same time, the vibration generated by the rotation of the crankshaft 21 and the eccentric part 231 will be more obvious, and the corresponding friction resistance will be greater.

[0064] Therefore, the present invention will Setting the value between 0.04 and 0.18 can maximize the energy efficiency of the rotary compressor 100 while reducing the rotational resistance of the rotor core 12 and the pump body 2, thereby improving the energy efficiency of the rotary compressor 100. Furthermore, the above-mentioned dimension design can ensure that the rotary compressor 100 has better energy efficiency in both low-frequency and high-frequency operation, adapting to the energy efficiency requirements under different operating conditions.

[0065] And, in a further embodiment, it is satisfied that: That is, the ratio of the square root of the product of e and D1 and H2 is between 0.09 and 0.11. It is set to 0.091, 0.092, 0.095, 0.098, 0.101, 0.103, 0.105, 0.110, etc. By 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.

[0066] It should be noted that, Figure 8 As shown in the figure, The relationship between the energy efficiency of the rotary compressor 100 and the energy efficiency of the rotary compressor 100 is shown to be normally distributed. When the parameter value is set to 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 energy efficiency of the rotary compressor 100 is between 0.09 and 0.11, the energy efficiency of the rotary compressor 100 is more concentrated. In other words, the highest energy efficiency point is between the energy efficiency corresponding to 0.09 and 0.11. By limiting the above-mentioned parameter ranges in turn, the energy efficiency of the rotary compressor 100 can be maximized while reducing the rotational resistance of the rotor core 12 and the pump body component 2, which is beneficial to improving the energy efficiency of the rotary compressor 100.

[0067] In some embodiments, if the following condition is satisfied: 3.5mm≤e≤5.5mm, the distance e between the center line of the eccentric portion 231 and the center line of the crankshaft 21 can be set to 3.5mm~5.5mm, such as setting e to 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 portion 231 and the center line of the crankshaft 21 within the above range, which is beneficial to improving the energy efficiency of the rotary compressor 100.

[0068] Specifically, the distance e between the center line of the eccentric portion 231 and the center line of the crankshaft 21 is set to be greater than or equal to 3.5 mm, so that the eccentric portion 231 has a larger compression range, realizing a 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 portion 231 and the center line of the crankshaft 21 is set to be less than or equal to 5.5 mm, to avoid the excessive size causing the eccentric portion 231 to generate excessive rotational inertia when the rotary compressor 100 operates at high frequency, resulting in excessive vibration noise and friction resistance, reducing losses, and helping to improve overall energy efficiency.

[0069] In some embodiments, 20mm≤H2≤80mm, that is, the axial height H2 of the rotor core 12 can be set to 20mm~80mm, such as setting H2 to 23mm, 27mm, 34mm, 41mm, 55mm, 67mm, 71mm, 72mm, etc., thereby setting the axial height H2 of the rotor core 12 within the above range, which is beneficial to improving the energy efficiency of the rotary compressor 100.

[0070] 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, realizing the output of a wider range of rotational torque, which is conducive to compressing a larger volume of refrigerant, thereby enhancing the compression efficiency. At the same time, the axial height H2 of the rotor core 12 is set to be less than or equal to 80 mm to avoid the excessive size causing the rotor core 12 to generate excessive rotational inertia when the rotary compressor 100 operates at high frequency, resulting in excessive vibration noise and friction resistance, reducing losses, and helping to improve overall energy efficiency.

[0071] In some embodiments, as Figure 2 As shown, the maximum outer circle radius of the stator core 11 is R2 and the maximum outer circle outer diameter is D4, the axial height of the stator core 11 is H3, the axial height of the cylinder 23 is H1, and it satisfies: D4=2R2, and it satisfies: That is, the ratio of 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 to the axial height H1 of the cylinder 23 is between 1.3 and 8.8, so that the rotary compressor 100 has a greater working energy efficiency. Specifically, Settings include 1.3, 1.8, 2.2, 3.4, 5.3, 5.5, 6.8, 6.9, 7.2, 8.1, etc.

[0072] Specifically, the maximum outer diameter D4 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 that can drive the rotor core 12 to rotate, the larger the achievable displacement, and the greater the refrigerant compression volume. The larger the axial height H1 of the cylinder 23, the larger the volume inside the cylinder 23, the larger the volume of the refrigerant that can be compressed, and the greater the achievable refrigerant compression volume. Therefore, Setting it to be greater than or equal to 1.3 can enable the stator core 11 to drive the cylinder 23 with a larger displacement to operate, thereby achieving a larger displacement of refrigerant compression, and Setting it to be less than or equal to 1.3 can prevent the stator core 11 from being too large in size, resulting in too high a cost, prevent the stator core 11 from occupying too much space in the rotary compressor 100, and avoid the axial size of the cylinder 23 being too large, resulting in excessive mechanical wear, reduce the current consumption of the motor 1 and the electronic control, and improve the energy efficiency of the entire machine.

[0073] In a further embodiment, it is satisfied that: That is, the ratio of 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 to the axial height H1 of the cylinder 23 is between 2.3 and 2.7, so that the rotary compressor 100 has a greater working energy efficiency. Specifically, Settings include 2.3, 2.32, 2.35, 2.41, 2.52, 2.56, 2.67, 2.69, 2.7, etc.

[0074] Therefore, Setting it to be greater than or equal to 2.3 can enable the stator core 11 to drive the cylinder 23 with a larger displacement to operate, thereby achieving a larger displacement of refrigerant compression, and Setting it to be less than or equal to 2.7 can prevent the stator core 11 from being too large in size, which leads to too high a cost, and prevent the stator core 11 from occupying too much space in the rotary compressor 100 .

[0075] It should be noted that, Figure 9 As shown in the figure, The relationship between the energy efficiency of the rotary compressor 100 and the energy efficiency of the rotary compressor 100 is shown to be normally distributed. When the parameter value is set to between 1.3 and 8.8, the energy efficiency of the rotary compressor 100 is greater than that corresponding to other values, especially When the energy efficiency is between 2.3 and 2.7, the energy efficiency of the corresponding rotary compressor 100 is more concentrated. In other words, the highest energy efficiency point is between the energy efficiency corresponding to 2.3 and 2.7. By limiting the above-mentioned parameter ranges in turn, the energy efficiency of the rotary compressor 100 can be maximized while reducing the installation costs of the rotor core 12 and the cylinder 23, which is beneficial to improving the energy efficiency of the rotary compressor 100.

[0076] In some embodiments, as Figure 3 As shown, the inner diameter of the cylinder 23 is D3 and satisfies: That is, the ratio of 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 to the inner diameter D3 of the cylinder 23 is between 0.59 and 3.11, so that the rotary compressor 100 has a greater working energy efficiency. Specifically, Settings include 0.6, 0.7, 1.35, 1.41, 1.52, 2.11, 2.67, 2.69, 3.11, etc.

[0077] Specifically, the maximum outer diameter D4 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 that can drive the rotor core 12 to rotate, the larger the achievable displacement, and the more conducive to achieving a larger volume of refrigerant compression. The larger the inner diameter D3 of the cylinder 23, the larger the volume inside the cylinder 23, the larger the volume of refrigerant that can be compressed, and the greater the achievable refrigerant compression. Therefore, Setting it to be greater than or equal to 0.59 can enable the stator core 11 to drive the cylinder 23 with a larger displacement to operate, thereby achieving a larger displacement of refrigerant compression, and Setting it to be less than or equal to 3.11 can prevent the stator core 11 from being too large in size, resulting in too high a cost, prevent the stator core 11 from occupying too much space in the rotary compressor 100, and avoid the cylinder 23 from being too large in size, resulting in excessive mechanical wear, reduce the current consumption of the motor 1 and the electronic control, and improve the energy efficiency of the entire machine.

[0078] In a further embodiment, it is satisfied that: That is, the ratio of 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 to the inner diameter D3 of the cylinder 23 is between 1.0 and 1.2, so that the rotary compressor 100 has a greater working energy efficiency. Settings include 1.02, 1.05, 1.11, 1.13, 1.15, 1.16, 1.17, 1.19, 1.2, etc.

[0079] Therefore, Setting it to be greater than or equal to 1.0 enables the stator core 11 to drive the cylinder 23 with a larger displacement to operate, thereby achieving a larger displacement of refrigerant compression, and Setting it to be less than or equal to 1.2 can prevent the stator core 11 from being too large in size, which leads to too high a cost, and prevent the stator core 11 from occupying too much space in the rotary compressor 100 .

[0080] It should be noted that, Figure 10 As shown in the figure, The relationship between the energy efficiency of the rotary compressor 100 and the energy efficiency of the rotary compressor 100 is shown to be normally distributed. When the parameter value is set to between 0.59 and 3.11, the energy efficiency of the rotary compressor 100 is greater than that corresponding to other values, especially When the energy efficiency of the rotary compressor 100 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 between the energy efficiency corresponding to 1.0 and 1.2. By limiting the above-mentioned parameter ranges in turn, the energy efficiency of the rotary compressor 100 can be maximized while reducing the installation costs of the rotor core 12 and the cylinder 23, which is beneficial to improving the energy efficiency of the rotary compressor 100.

[0081] In some embodiments, if the condition 20mm≤H3≤80mm is satisfied, the axial height H3 of the stator core 11 can be set to 20mm~80mm, such as setting H3 to 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 beneficial to improving the energy efficiency of the rotary compressor 100.

[0082] Specifically, the axial height H3 of the stator core 11 is set to be greater than or equal to 20 mm, so that the stator core 11 has a larger structural volume, which can form a larger range of rotational torque on the rotor core 12, which is conducive to compressing a larger volume of refrigerant, 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 80 mm, so as to avoid the stator core 11 occupying too much space in the rotary compressor 100 due to the excessive size, and reduce the setting cost of the stator core 11.

[0083] In other embodiments, 34mm≤D3≤71mm, that is, the inner diameter D3 of the cylinder 23 can be set to 34mm~71mm, such as setting D3 to 34mm, 41mm, 55mm, 67mm, 71mm, etc., thereby setting the inner diameter D3 of the cylinder 23 within the above range, which is beneficial to improving the energy efficiency of the rotary compressor 100.

[0084] Specifically, the inner diameter D3 of the cylinder 23 is set to be greater than or equal to 34 mm, so that the cylinder 23 has a larger volume, which is conducive to compressing a larger volume of refrigerant, 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 71 mm to avoid the cylinder 23 occupying too much space in the rotary compressor 100 due to the excessive size, and to reduce the setting cost of the cylinder 23.

[0085] In some other embodiments, 12mm≤H1≤32mm, that is, the axial height H1 of the cylinder 23 can be set to 12mm~32mm, such as setting H1 to 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 beneficial to improving the energy efficiency of the rotary compressor 100.

[0086] 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, which is conducive to compressing a larger volume of refrigerant, thereby enhancing the compression efficiency. At the same time, the axial height H1 of the cylinder 23 is set to be less than or equal to 32 mm to avoid the cylinder 23 occupying too much space in the rotary compressor 100 due to the excessive size, and to reduce the setting cost of the cylinder 23.

[0087] In some embodiments, if the condition 15≤Q≤18 is satisfied, the number Q of the stator slots 113 can be set between 15 and 18. For example, Q can be set to 15, 16, 17 or 18, and the number Q of the stator slots 113 can be set to be greater than or equal to 15, so that the number of stator windings 114 is large, so as to drive the rotor core 12 to effectively output power and realize a powerful drive of the eccentric part 231. At the same time, the number Q of the stator slots 113 is set to be less than or equal to 18, so as to avoid the stator core 11 being too large in size, resulting in too high a setting cost, and to facilitate the reasonable arrangement of the stator core 11 in the rotary compressor 100.

[0088] And / or, 10≤P≤12, the number of rotor poles P can be set between 10 and 12, such as setting P to 10, 11, or 12, and setting the number of rotor poles P to be greater than or equal to 10, so that the power output by the rotor core 12 is greater, and the eccentric part 231 is driven powerfully, which is beneficial to increase the compression amount of the refrigerant. At the same time, the number of rotor poles P is set to be less than or equal to 12, so as to avoid the rotor size being too large, resulting in excessively high setting costs, and is beneficial to the reasonable arrangement of the rotor in the rotary compressor 100.

[0089] In some embodiments, the number of slots per pole and per phase of the motor 1 is q, the number of phases of the motor 1 is m, And if it satisfies: 0<q<1, the number of slots per pole per phase can be set to be greater than 0 and less than 1, such as q is set to 0.1, 0.3, 0.4, 0.7, 0.8, etc., that is, the number of slots per pole per phase of the motor 1 in the present invention is a non-integer. Therefore, the design of the fractional slot winding can improve the running stability and thrust density characteristics of the motor 1, which is beneficial to improving the energy efficiency of the rotary compressor 100.

[0090] In some embodiments, 23mm≤R1≤39mm, that is, the radius R1 of the rotor core 12 can be set between 23mm and 39mm, such as setting R1 to 23mm, 27mm, 29mm, 31mm, 32mm, 33mm, 37mm, 39mm, etc., thereby setting the radius R1 of the rotor core 12 within the above range, which is beneficial to improving the energy efficiency of the rotary compressor 100.

[0091] 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, achieving a wider range of rotational torque output, which is conducive to compressing a larger volume of refrigerant, thereby enhancing 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 to avoid the excessive size causing the rotor core 12 to generate excessive rotational inertia when the rotary compressor 100 operates at high frequency, resulting in excessive vibration noise and friction resistance, reducing losses, and helping to improve overall energy efficiency.

[0092] In other embodiments, 45mm≤R2≤70mm, that is, the radius R2 of the stator core 11 can be set between 45mm and 70mm, such as setting R2 to 45mm, 47mm, 49mm, 51mm, 52mm, 63mm, 67mm, 70mm, etc. Thus, setting the radius R2 of the stator core 11 within the above range is beneficial to improving the energy efficiency of the rotary compressor 100.

[0093] 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, thereby outputting a larger rotational torque to the rotor core 12, which is conducive to compressing a larger volume of refrigerant, thereby enhancing 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 to avoid the excessive size causing the rotary compressor 100 to drive the rotor core 12 to generate excessive rotational inertia when operating at high frequency, resulting in excessive vibration noise and friction resistance, reducing losses, and helping to improve overall energy efficiency.

[0094] In other embodiments, if the following condition is satisfied: 12mm≤D2≤25mm, the outer diameter D2 of one end of the crankshaft 21 can be set to between 12mm and 25mm, such as setting D2 to 12mm, 13mm, 15mm, 16mm, 18mm, 21mm, 23mm, 25mm, etc., thereby setting the outer diameter D2 of the crankshaft 21 within the above range, which is beneficial to improving the energy efficiency of the rotary compressor 100.

[0095] Specifically, the outer diameter D2 of the crankshaft 21 is set to be greater than or equal to 12 mm, so that the crankshaft 21 can output a wider range of rotational torque, which is conducive to compressing a larger volume of refrigerant, thereby enhancing the compression efficiency. At the same time, the outer diameter D2 of the crankshaft 21 is set to be less than or equal to 25 mm to avoid the excessive size causing the rotary compressor 100 to generate excessive rotational inertia when operating at high frequency, resulting in excessive vibration noise and friction resistance, reducing losses, and helping to improve overall energy efficiency.

[0096] Among them, Figure 6 As shown, the compressor 100 further includes a liquid reservoir 200, which can be connected to the cylinder 23 of the rotary compressor 100 through a pipeline, so that the refrigerant in the liquid reservoir 200 can enter the cylinder 23 through the pipeline for compression.

[0097] The utility model also provides a refrigeration device.

[0098] According to the refrigeration equipment of the embodiment of the present invention, including the rotary compressor 100 of any of the above-mentioned embodiments, by limiting the sizes of the stator core 11, the rotor core 12 and the pump body component 2 within the above-mentioned range, the stator can generate a sufficiently large driving force on the rotor core 12, thereby realizing a powerful drive of the rotor core 12. The rotor core 12 and the crankshaft 21 can output an effective driving force to compress a larger volume of refrigerant. At the same time, it can also avoid the structural dimensions of the rotor core 12 and the stator core 11 being too large, and the reasonable cost of the structural component setting can be controlled. In addition, when the rotary compressor 100 is operated at high frequency or low frequency, good operating energy efficiency can be guaranteed, thereby reducing the power consumption of the rotary compressor 100.

[0099] Throughout this specification, reference to terms such as "one embodiment," "some embodiments," "illustrative embodiments," "examples," "specific examples," or "some examples" means that the specific features, structures, materials, or characteristics described in conjunction with that embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the illustrative use of the above terms does not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.

[0100] Although the embodiments of the present invention have been shown and described, those skilled in the art will appreciate that various changes, modifications, substitutions and variations may be made to the embodiments without departing from the principles and purpose of the present invention, and that the scope of the present invention is defined by the claims and their equivalents.

Claims

1. A rotary compressor, characterized in that: include: 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 an annular yoke and a plurality of teeth disposed within the yoke, the plurality of teeth being spaced apart along the circumference of the yoke, with stator slots being formed between adjacent two teeth, the stator winding being wound within the stator slots, and the rotor comprising a rotor core; A pump body component, comprising 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; The number of stator slots is Q, the number of rotor poles is P, the maximum outer circle radius of the rotor core is R1 and the maximum outer circle outer diameter is D1, D1=2*R1, the outer diameter of the crankshaft and the upper bearing matching portion is D2, GCD(Q, P) is the greatest common divisor of Q and P, and satisfies: 5≤GCD(Q,P)≤6.

2. The rotary compressor according to claim 1, wherein satisfy:

3. The rotary compressor according to claim 2, wherein: satisfy:

4. The rotary compressor according to any one of claims 1 to 3, characterized in that: An eccentric portion is provided on the other end of the crankshaft, and the eccentric portion is located in the cylinder and rotates eccentrically in the cylinder; The axial height of the rotor core is H2, the distance between the centerline of the eccentric portion and the centerline of the crankshaft is e, and the following conditions are satisfied:

5. The rotary compressor according to claim 4, characterized in that satisfy:

6. The rotary compressor according to any one of claims 1 to 3, characterized in that: The maximum outer circle radius of the stator core is R2 and the maximum outer circle outer diameter is D4. The axial height of the stator core is H3. The axial height of the cylinder is H1. The following conditions are met: D4=2R2. The following conditions are met:

7. The rotary compressor according to claim 6, characterized in that satisfy:

8. The rotary compressor according to claim 6, wherein The inner diameter of the cylinder is D3 and satisfies:

9. The rotary compressor according to claim 8, characterized in that satisfy:

10. The rotary compressor according to claim 8, wherein Meet: 34mm≤D3≤71mm; And / or, satisfying: 12mm≤H1≤32mm.

11. The rotary compressor according to claim 6, wherein Meet: 23mm≤R1≤39mm; And / or, satisfy: 45mm≤R2≤70mm.

12. The rotary compressor according to any one of claims 1 to 3, characterized in that: Satisfy: 15≤Q≤18; And / or, 10≤P≤12.

13. The rotary compressor according to any one of claims 1 to 3, characterized in that: The number of slots per pole and per phase of the motor is q, and the number of phases of the motor is m. And it satisfies: 0<q<1.

14. A refrigeration device, characterized in that: A rotary compressor comprising the rotary compressor described in any one of claims 1-13.

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