Rotary compressor and air conditioner having the same

Abstract

The utility model provides a kind of rotary compressor and the air conditioner with the rotary compressor of this utility model.The compressor includes: shell;Motor, including rotor;And compression assembly, including crankshaft, crankshaft is set to be fixedly connected with rotor, to make crankshaft rotate under the drive of motor;Wherein, crankshaft includes main body and, at least one eccentric portion is spacedly distributed along the axial direction of main body;And the axial end surface of rotor is provided with at least one lightening groove, to balance the eccentric force formed by at least one eccentric portion.This application can balance the eccentric force generated by eccentric portion rotation by setting lightening groove on rotor, while avoiding the weight of whole machine, so that the radial stress of crankshaft and roller and other transmission components under static and dynamic is greatly reduced, especially under dynamic, reduce the vibration and operating noise of whole machine caused by imbalance, reduce energy consumption while prolong the service life of core components.

Description

Technical Field

[0001] This utility model relates to the field of compressor technology, and in particular to a rotary compressor and an air conditioner having the rotary compressor. Background Technology

[0002] The rotating shaft system of a rotary rotor variable frequency twin-cylinder compressor generally consists of a crankshaft, a rotor of a variable frequency drive motor, and rollers. The shaft system uses a pair of main and auxiliary sliding bearings to support the rotation of the crankshaft. The upper and lower eccentric parts of the crankshaft are placed between the main and auxiliary sliding bearings, and a pair of rollers are nested in the two eccentric parts of the crankshaft respectively. The rotor is located on the long shaft part of the crankshaft outside the main and auxiliary bearing structure.

[0003] For rotary rotor variable frequency twin-cylinder compressors, reducing vibration and noise has always been a technical challenge in achieving high compressor speeds. Existing technologies typically use balance blocks at both ends of the rotor to balance the eccentric forces and moments generated during operation by the eccentric mass of the crankshaft's eccentric portion, thus reducing vibration and noise. However, while the double balance block structure has a certain vibration reduction effect at low speeds, under high-speed operating conditions, the rotational centrifugal force generated by the mass of the balance blocks at both ends of the rotor and the eccentric mass of the upper and lower eccentric portions (including rollers) of the crankshaft increases dramatically. This leads to increased crankshaft deflection, causing dynamic eccentricity in the rotating shaft system, disrupting the uniformity of the magnetic field between the stator and rotor, and thus worsening the vibration and noise of the compressor under high-speed operating conditions.

[0004] Taking all factors into consideration, the design needs to provide a rotary compressor with a novel shaft balancing structure and an air conditioner with the rotary compressor to reduce vibration and noise under high-speed operation conditions of the compressor. Utility Model Content

[0005] One objective of the first aspect of this application is to overcome at least one deficiency in the prior art and to provide a rotary compressor.

[0006] A further objective of the first aspect of this application is to balance the eccentric force formed by the eccentric portion.

[0007] Another further objective of the first aspect of this application is to reduce the weight of the rotating shaft system.

[0008] One objective of the second aspect of this application is to provide an air conditioner having the rotary compressor.

[0009] In particular, this application provides a rotary compressor, comprising:

[0010] case;

[0011] Electric motor, including rotor; and

[0012] A compression assembly includes a crankshaft, which is configured to be fixedly connected to a rotor so that the crankshaft rotates under the drive of an electric motor; wherein,

[0013] The crankshaft includes a main body and at least one eccentric portion spaced apart along the axial direction of the main body; and

[0014] At least one weight-reducing groove is provided on the axial end face of the rotor to balance the eccentric force formed by at least one eccentric part.

[0015] This application, by creating weight-reducing grooves on the rotor, can balance the eccentric force generated by the rotation of the eccentric part, significantly reducing the radial force on transmission components such as the crankshaft and rollers under both static and dynamic conditions. This reduces friction loss and heat generation, and particularly reduces overall machine vibration and operating noise caused by imbalance under dynamic conditions, thereby lowering energy consumption and extending the service life of core components. Moreover, this application achieves a balancing effect without increasing the overall weight of the machine, simplifying structural complexity and further improving the compressor's operational stability and energy efficiency.

[0016] Optionally, the center of gravity of at least one eccentric portion is located on an imaginary plane, which extends along the axial direction of the main body and coincides with the rotation axis of the main body; and

[0017] The weight reduction groove is set to be mirror-symmetric about an imaginary plane.

[0018] This application uses a specific weight reduction groove layout to allow the balancing force formed by the weight reduction groove to cancel out the eccentric force of the eccentric part in opposite directions within the same plane, thus avoiding residual imbalance; at the same time, it ensures uniform rotor mass distribution, reduces additional centrifugal force or vibration, and lowers noise and resonance risks.

[0019] Optionally, the number of eccentric parts is two, including a first eccentric part and a second eccentric part sequentially disposed below the rotor; and

[0020] The first eccentric part and the second eccentric part are arranged opposite each other on the radial sides of the main body.

[0021] This application employs two eccentric sections that can adapt to a dual-cylinder compression structure, which helps to improve refrigerant displacement and compression efficiency, while avoiding crankshaft wear or deformation caused by excessive load on a single eccentric section. At the same time, by arranging the first and second eccentric sections relative to each other, the crankshaft force can be balanced, reducing bending deformation and bearing wear caused by excessive force on one side. Combined with the balancing design of the rotor weight-reducing slots, the overall dynamic and static balance accuracy can be further improved, ensuring the compressor operates efficiently, with low noise and a long service life.

[0022] Optionally, the number of weight-reducing grooves is one, and it is located on the opposite side of the second eccentric portion relative to the main body; and / or

[0023] The weight reduction groove is located on the axial end face of the rotor near the first eccentric part.

[0024] This application arranges the weight-reducing groove on the opposite side of the second eccentric part, on the lower end face of the rotor, which can better balance the overall mass distribution of the two eccentric parts, reduce the bending deformation of the crankshaft, and improve the compactness of the shaft system.

[0025] Optionally, the compression component further includes:

[0026] The first roller and the second roller are respectively fitted onto the first eccentric part and the second eccentric part;

[0027] The static balance ratio of the crankshaft is calculated using the following formula:

[0028]

[0029] Where A represents the static balance ratio, m1 represents the eccentric mass of the rotor, m2 represents the mass of the first eccentric part, m3 represents the mass of the first roller, m4 represents the mass of the second eccentric part, m5 represents the mass of the second roller, r1 represents the distance between the center of gravity of the rotor and the rotation axis of the main body, r2 represents the distance between the center of gravity of the second eccentric part and the rotation axis of the main body, r3 represents the distance between the center of gravity of the first roller and the rotation axis of the main body, r4 represents the distance between the center of gravity of the first eccentric part and the rotation axis of the main body, and r5 represents the distance between the center of gravity of the second roller and the rotation axis of the main body; and

[0030] The static balance ratio A is 80% to 120%.

[0031] This application sets the static balance rate to 80% to 120%, which can accurately compensate for the mass distribution deviation of the rotor, eccentric part and roller, reduce the wear and deformation caused by uneven crankshaft force, avoid the aggravation of vibration and noise caused by insufficient balance, and prevent excessive balance from increasing structural redundancy, thereby achieving a comprehensive improvement in the compressor's operational stability and lifespan.

[0032] Optionally, the compression component further includes:

[0033] The first roller and the second roller are respectively fitted onto the first eccentric part and the second eccentric part;

[0034] The dynamic balance ratio of the crankshaft is calculated according to the following formula:

[0035]

[0036] Where B represents the dynamic balance ratio, m1 represents the eccentric mass of the rotor, m2 represents the mass of the first eccentric part, m3 represents the mass of the first roller, m4 represents the mass of the second eccentric part, m5 represents the mass of the second roller, r1 represents the distance between the center of gravity of the rotor and the rotation axis of the main body, r2 represents the distance between the center of gravity of the second eccentric part and the rotation axis of the main body, r3 represents the distance between the center of gravity of the first roller and the rotation axis of the main body, r4 represents the distance between the center of gravity of the first eccentric part and the rotation axis of the main body, r5 represents the distance between the center of gravity of the second roller and the rotation axis of the main body, L1 represents the distance between the center of gravity of the rotor and the bottom surface of the second eccentric part, L2 represents the distance between the center of gravity of the first eccentric part and the bottom surface of the second eccentric part, L3 represents the distance between the center of gravity of the first roller and the bottom surface of the second eccentric part, L4 represents the distance between the center of gravity of the second eccentric part and the bottom surface of the second eccentric part, and L5 represents the distance between the center of gravity of the second roller and the bottom surface of the second eccentric part.

[0037] The dynamic balance rate B is 70% to 130%.

[0038] This application sets the dynamic balance rate to 70% to 130%, which can improve the operating stability of the compressor across the entire speed range, reduce vibration and noise, and extend the life of core components.

[0039] Optionally, the dynamic balance rate B is greater than or equal to 110%.

[0040] This application specifically sets the dynamic balance ratio B to be greater than or equal to 110%, which can further improve the dynamic balance accuracy, reduce the crankshaft deflection at high speeds, and optimize the vibration reduction and noise reduction effect of the compressor.

[0041] Optionally, the compression component also includes:

[0042] At least one roller is respectively fitted onto the at least one eccentric portion; wherein...

[0043] The roller is made of at least one material selected from ceramic and aluminum alloy; and / or,

[0044] The density range of the roller is 2.7 g / mm². 3 Up to 2.8g / mm 3 .

[0045] This application reduces the stress on the crankshaft by selecting rollers with specific material densities, allowing for more flexible selection of the crankshaft's structure and material, thereby achieving overall weight reduction and reducing the production and transportation costs of the compressor.

[0046] Optionally, the rotary compressor rotates at a speed of less than or equal to 200 rpm; and / or

[0047] The rotary compressor operates at a frequency range of 30Hz to 200Hz.

[0048] The compressor of this application can flexibly adjust its speed and frequency within a wide range, and is compatible with different specifications of refrigeration systems and operating conditions without increasing the vibration and operating noise of the whole machine.

[0049] According to a second aspect of this application, an air conditioner is also provided, comprising: a rotary compressor as described in any of the above.

[0050] The air conditioner of this application can balance the eccentric force formed by the eccentric part by opening a weight-reducing groove on the axial end face of the rotor, while also reducing the radial load on the crankshaft, reducing friction loss and energy consumption, and extending the service life of the components.

[0051] The above and other objects, advantages and features of this application will become more apparent to those skilled in the art from the following detailed description of specific embodiments of this application in conjunction with the accompanying drawings. Attached Figure Description

[0052] The following sections will describe some specific embodiments of this application in detail by way of example and not limitation, with reference to the accompanying drawings. The same reference numerals in the drawings denote the same or similar parts or components. Those skilled in the art should understand that these drawings are not necessarily drawn to scale. In the drawings:

[0053] Figure 1 This is a schematic cross-sectional view of a rotary compressor according to an embodiment of this application;

[0054] Figure 2 yes Figure 1 A schematic three-dimensional view of the rotor in the image;

[0055] Figure 3 yes Figure 1 A schematic three-dimensional view of the crankshaft in the image;

[0056] Figure 4 yes Figure 1 A schematic cross-sectional view of the compression component in the diagram;

[0057] Figure 5 This is a comparison graph showing the degree of deformation at the end of the crankshaft long shaft of the present application and the comparative example as a function of the compressor operating frequency;

[0058] Figure 6 This is a schematic structural diagram of an air conditioner according to an embodiment of this application. Detailed Implementation

[0059] Figure 1This is a schematic cross-sectional view of a rotary compressor 100 according to an embodiment of this application; Figure 2 yes Figure 1 A schematic perspective view of rotor 121 in the figure; Figure 3 yes Figure 1 A schematic perspective view of crankshaft 131 in the figure; Figure 4 yes Figure 1 A schematic cross-sectional view of the compression component 130. See also... Figures 1 to 4 This application provides a rotary compressor 100, which may include a housing 110, a motor 120, and a compression assembly 130.

[0060] The motor 120 can be housed within the housing 110 and includes a rotor 121 and a stator.

[0061] The compression assembly 130 may include a crankshaft 131, which may be fixedly connected to the rotor 121 so that the crankshaft 131 rotates under the drive of the motor 120.

[0062] The crankshaft 131 may include a main body 1311 and at least one eccentric portion 1312 spaced apart along the axial direction of the main body 1311. In this application, at least one may be one, two, or more than two.

[0063] exist Figure 1 In the embodiment shown, the rotary compressor 100 is a vertical compressor, that is, the axial direction of the main body 1311 is vertical.

[0064] In some embodiments, the number of eccentric portions may be one. The compression assembly 130 may also include a main bearing, a secondary bearing, a cylinder, and a roller.

[0065] The main bearing and the auxiliary bearing are used to support the crankshaft 131 and can be respectively located above and below the eccentric portion, forming a compression space with the cylinder. The cylinder can form an intake passage; the main bearing and / or the auxiliary bearing can form an exhaust passage.

[0066] The rollers can be fitted onto the eccentric part so that they can move in the compression space under the drive of the eccentric part, thereby realizing the intake and exhaust of the compressor.

[0067] In some other embodiments, there may be two eccentric portions, including a first eccentric portion 1312a and a second eccentric portion 1312b sequentially disposed below the rotor 121. That is, the first eccentric portion 1312a is closer to the rotor 121, and the second eccentric portion 1312b is relatively farther away from the rotor 121, with the first eccentric portion 1312a positioned above the second eccentric portion 1312b.

[0068] The compression assembly 130 may also include a main bearing, a secondary bearing, a first cylinder and a second cylinder, a partition, and a first roller 1321 and a second roller 1322.

[0069] The main bearing, the first cylinder, the partition, the second cylinder, and the auxiliary bearing can be arranged from top to bottom along the axial direction of the main body 1311.

[0070] The main bearing, together with the first cylinder and the partition, forms a first compression space; the auxiliary bearing, together with the second cylinder and the partition, forms a second compression space.

[0071] The first roller 1321 and the second roller 1322 are respectively fitted onto the first eccentric part 1312a and the second eccentric part 1312b, so that they move in the first compression space and the second compression space respectively under the drive of the first eccentric part 1312a and the second eccentric part 1312b, so as to realize the intake and exhaust of the first cylinder and the second cylinder respectively.

[0072] The technical solution of this application will be described below using two eccentric parts, namely the first eccentric part 1312a and the second eccentric part 1312b, as an example.

[0073] In particular, at least one weight-reducing groove 1211 may be provided on the axial end face of the rotor 121 to balance the eccentric force formed by the eccentric part.

[0074] This application achieves balance directly by removing end face material from rotor 121, significantly simplifying the structure, reducing the number of parts, material costs, and assembly processes, thereby lowering costs and assembly complexity. At the same time, the weight reduction groove 1211 reduces the overall mass of rotor 121, reducing the inertial load driven by motor 120, which helps to reduce energy consumption, improve motor 120 efficiency, and indirectly improve compressor energy efficiency. In addition, the weight reduction groove 1211 does not increase the size of rotor 121, avoiding spatial interference with surrounding components, and is more suitable for the lightweight and miniaturization requirements of compressors, comprehensively improving the stability, economy, and competitiveness of compressors.

[0075] In some embodiments, the centers of gravity of the first eccentric portion 1312a and the second eccentric portion 1312b may be located on an imaginary plane, which extends along the axial direction of the main body 1311 of the crankshaft 131 and coincides with the rotation axis of the main body 1311. That is, the rotation axis of the main body 1311 is located on the imaginary plane.

[0076] The weight-reducing groove 1211 can be configured to be mirror-symmetric about an imaginary plane. In other words, when the first eccentric portion 1312a and the second eccentric portion 1312b are homogeneous, the rotation axis of the main body 1311, the axial central axis of the first eccentric portion 1312a, and the axial central axis of the second eccentric portion 1312b are all located in the same plane, and the cross section of the weight-reducing groove 1211 opened on the rotor 121 along the direction perpendicular to the center line of the central shaft hole of the rotor 121 is symmetric about the plane where the aforementioned three axes coexist.

[0077] This application places the center of gravity of the eccentric part on an imaginary axial plane that coincides with the rotation axis, and makes the weight-reducing groove 1211 symmetrical about this imaginary plane, which can effectively optimize dynamic balance. This allows for a uniform mass distribution of the rotor 121, thereby optimizing dynamic and static balance, reducing additional centrifugal force or vibration noise, and making the centrifugal force more evenly distributed, reducing peak bearing load, reducing wear, and ensuring smooth operation and durability while reducing weight and energy consumption, thus improving the overall performance of the engine.

[0078] In some embodiments, the weight-reducing groove 1211 can be disposed on the side of the rotor 121 near the eccentric portion of the crankshaft 131 to shorten the distance between the eccentric mass of the rotor 121 and the eccentric portion of the crankshaft 131, thereby reducing the lever arm generated by the eccentric mass. This not only reduces the unbalanced torque during rotation, thus reducing vibration and noise, but also reduces the additional load on components such as bearings, reducing wear and improving operational stability and durability. Furthermore, the compact mass distribution reduces structural redundancy, optimizes space utilization while ensuring a balanced effect, and enhances the overall operating efficiency of the compressor.

[0079] In some embodiments, the first eccentric portion 1312a and the second eccentric portion 1312b are disposed opposite to each other on the radial sides of the main body 1311. That is, when the dimensional parameters of the first eccentric portion 1312a and the second eccentric portion 1312b are the same, the projections of the first eccentric portion 1312a and the second eccentric portion 1312b on the horizontal plane are mirror-symmetrical with respect to the central axis of the main body 1311.

[0080] This application, by arranging two eccentric portions in a relatively opposite manner, can significantly reduce the unbalanced torque during overall rotation, reduce vibration and noise during high-speed operation, avoid excessive load concentration on the bearing, alleviate bearing wear problems, and improve operational stability. In some embodiments, the number of weight-reducing grooves 1211 can be one, located on the opposite side of the second eccentric portion 1312b relative to the main body 1311, so as to precisely balance the mass distribution of the first eccentric portion 1312a and the second eccentric portion 1312b.

[0081] In some embodiments, the static balance ratio of crankshaft 131 can be calculated according to the following formula:

[0082]

[0083] Where A represents the static balance ratio, m1 represents the eccentric mass of rotor 121, m2 represents the mass of the first eccentric part 1312a, m3 represents the mass of the first roller 1321, m4 represents the mass of the second eccentric part 1312b, m5 represents the mass of the second roller 1322, r1 represents the distance between the center of gravity of rotor 121 and the rotation axis of main body 1311, r2 represents the distance between the center of gravity of second eccentric part 1312b and the rotation axis of main body 1311, r3 represents the distance between the center of gravity of first roller 1321 and the rotation axis of main body 1311, r4 represents the distance between the center of gravity of first eccentric part 1312a and the rotation axis of main body 1311, and r5 represents the distance between the center of gravity of second roller 1322 and the rotation axis of main body 1311. The static balance ratio A of crankshaft 131 can be set from 80% to 120% to accurately compensate for the mass distribution deviation of rotor 121, eccentric part and rollers, reduce wear and deformation caused by uneven stress on crankshaft 131, avoid increased vibration and noise due to insufficient balance, and prevent excessive balance from increasing structural redundancy, thereby achieving a comprehensive improvement in the compressor's operational stability and lifespan. For example, the static balance ratio can be 80%, 90%, 100%, 110% or 120%.

[0084] In some embodiments, the dynamic balance ratio of crankshaft 131 can be calculated according to the following formula:

[0085]

[0086] Where B represents the dynamic balance ratio, m1 represents the eccentric mass of rotor 121, m2 represents the mass of the first eccentric part 1312a, m3 represents the mass of the first roller 1321, m4 represents the mass of the second eccentric part 1312b, m5 represents the mass of the second roller 1322, r1 represents the distance between the center of gravity of rotor 121 and the rotation axis of main body 1311, r2 represents the distance between the center of gravity of second eccentric part 1312b and the rotation axis of main body 1311, r3 represents the distance between the center of gravity of first roller 1321 and the rotation axis of main body 1311, and r4 represents the distance between the center of gravity of first eccentric part 1312a and the rotation axis of main body 1311. The distances between the rotating axes are as follows: r5 represents the distance between the center of gravity of the second roller 1322 and the rotation axis of the main body 1311; L1 represents the distance between the center of gravity of the rotor 121 and the bottom surface of the second eccentric part 1312b; L2 represents the distance between the center of gravity of the first eccentric part 1312a and the bottom surface of the second eccentric part 1312b; L3 represents the distance between the center of gravity of the first roller 1321 and the bottom surface of the second eccentric part 1312b; L4 represents the distance between the center of gravity of the second eccentric part 1312b and the bottom surface of the second eccentric part 1312b; and L5 represents the distance between the center of gravity of the second roller 1322 and the bottom surface of the second eccentric part 1312b. The dynamic balance ratio B of the crankshaft 131 can be set from 70% to 130% to improve the operating stability of the compressor across the entire speed range, reduce vibration noise, and extend the life of core components. For example, the dynamic balance rate can be 70%, 80%, 90%, 100%, 110%, 120%, or 130%.

[0087] Compared to static balancing, which only focuses on radial mass distribution, dynamic balancing (i.e., quantitative control of the axial center distance of rotor 121, double eccentric part and roller) enhances the ability to compensate for axial additional torque during high-speed rotation. It can accurately compensate for the dynamic unbalanced force caused by the difference in axial position of rotor 121, double eccentric part and corresponding roller during rotation, and avoid overturning vibration caused by axial imbalance during high-speed operation.

[0088] The dynamic balancing settings in this application complement the static balancing settings, together improving the operating stability of the compressor across the entire speed range, reducing vibration and noise, and extending the life of core components.

[0089] In some further embodiments, the dynamic balance rate of crankshaft 131 can be set to greater than or equal to 110% to further improve the dynamic balance accuracy, reduce the flexural deformation of crankshaft 131 at high speeds, and optimize the vibration reduction and noise reduction effect of compressor.

[0090] In some embodiments, the roller can be made of ceramic, aluminum alloy, or titanium alloy; the density of the roller can be in the range of 2.7 g / mm³.3 Up to 2.8g / mm 3 Compared to traditional iron-based materials (density approximately 7 g / mm³), 3 Up to 7.9 g / mm 3 Under the same specifications, the mass of the rollers can be reduced by 60 to 65.8%, reducing the centrifugal force when the rollers rotate, thereby reducing the dynamic impact on the crankshaft 131 and rotor 121, reducing the load on the balance design, and allowing the structure and material of the crankshaft 131 itself to be selected more flexibly, thus achieving overall weight reduction.

[0091] The lightweight and compact design of the rotor 121 and rollers in this application, combined with a specific range of dynamic and static balance rates, can effectively reduce the flexural deformation of the crankshaft 131. Especially under high-speed operating conditions, it can improve operational stability, reduce component wear, extend service life, reduce energy consumption and noise caused by vibration, and enhance product energy efficiency and reliability.

[0092] The rotary compressor 100 can operate at a speed of less than or equal to 200 rpm.

[0093] The rotary compressor 100 can operate at frequencies ranging from 30 Hz to 200 Hz.

[0094] The compressor of this application can flexibly adjust its speed and frequency within a wide range, and is compatible with different specifications of refrigeration systems and operating conditions without increasing the vibration and operating noise of the whole machine.

[0095] Tests show that, for the twin-cylinder rotary compressor 100 with the structure of this application, the shaft system structure formed according to the preferred embodiment of this application can better reduce the flexural deformation of the crankshaft 131 compared with other shaft systems in the prior art.

[0096] Example: Only the lower end of the rotor 121 is provided with a weight reduction groove 1211, and the weight of the weight reduction groove 1211 is 4.0g; each roller is made of ceramic material and weighs 21.5g; the static balance rate is 80% and the dynamic balance rate is 116%.

[0097] Comparative example: The upper balance block at the top of rotor 121 weighs 10.4g; the lower balance block at the bottom of rotor 121 weighs 7.8g; each roller is made of iron-based material and weighs 54.4g; the static balance rate is 97.5%; the dynamic balance rate is 98.5%.

[0098] The other structural parameters are the same for the embodiments and comparative examples.

[0099] Figure 5This is a comparison graph showing the deformation degree of the long shaft end of the crankshaft 131 in the embodiments and comparative examples of this application as a function of the compressor operating frequency. The results of calculating the flexural deformation of the crankshaft 131 in the embodiment and comparative examples within the operating frequency range of 30Hz to 200Hz are as follows. Figure 5 As shown, the flexural deformation of crankshaft 131 in both the embodiment and the comparative example increases with the increase of compressor operating frequency. However, the flexural deformation of crankshaft 131 in the embodiment of this application is reduced by about 25% compared with the comparative example at different speeds. In other words, this application can better reduce the flexural deformation of crankshaft 131.

[0100] The technical solutions of any of the above embodiments can be applied to a rotary rotor 121 variable frequency twin-cylinder compressor or a rotary rotor 121 fixed frequency twin-cylinder compressor. Those skilled in the art can specifically select the type of compressor according to the actual application scenario.

[0101] This application also provides an air conditioner 200, Figure 6 This is a schematic structural diagram of an air conditioner 200 according to one embodiment of this application. Figure 6 As shown, the air conditioner 200 includes a rotary compressor 100 of any of the above embodiments for regulating indoor air, such as cooling / heating, dehumidifying, introducing fresh air, etc.

[0102] Therefore, those skilled in the art should recognize that although many exemplary embodiments of this application have been shown and described in detail herein, many other variations or modifications conforming to the principles of this application can be directly determined or derived from the disclosure of this application without departing from the spirit and scope of this application. Thus, the scope of this application should be understood and construed as covering all such other variations or modifications.

[0103] In the description of this disclosure, it should be understood that the terms "front", "rear", "left", "right", "inner", "outer", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this application.

[0104] Unless otherwise expressly specified and limited, the terms "installation," "connection," "linking," "fixing," and "setting," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components, unless otherwise expressly limited. Those skilled in the art should be able to understand the specific meaning of the above terms in this application based on the specific circumstances.

[0105] Unless otherwise specified, all terms used in the description of this disclosure (including technical and scientific terms) have the same meaning as commonly understood by one of ordinary skill in the art to which this application pertains.

[0106] In the description of this disclosure, references to terms such as "one embodiment," "some embodiments," "illustrative embodiment," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of this application. In this specification, the illustrative expressions of the above terms do 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 one or more embodiments or examples.

[0107] Those skilled in the art should understand that the embodiments described below are merely a part of the embodiments of this application, and not all of the embodiments of this application. These partial embodiments are intended to explain the technical principles of this application and are not intended to limit the scope of protection of this application. Based on the embodiments provided in this application, all other embodiments obtained by those skilled in the art without creative effort should still fall within the scope of protection of this application.

Claims

1. A rotary compressor, characterized in that, include: case; Electric motor, including rotor; and A compression assembly includes a crankshaft configured to be fixedly connected to the rotor, such that the crankshaft rotates under the drive of the motor; wherein, The crankshaft includes a main body and at least one eccentric portion spaced apart along the axial direction of the main body; and At least one weight-reducing groove is provided on the axial end face of the rotor to balance the eccentric force formed by the at least one eccentric part.

2. The rotary compressor according to claim 1, characterized in that, The center of gravity of at least one eccentric portion is located on an imaginary plane, which extends along the axial direction of the main body and coincides with the rotation axis of the main body; and The weight-reducing groove is configured to be mirror-symmetric about the imaginary plane.

3. The rotary compressor according to claim 1, characterized in that, The number of eccentric portions is two, including a first eccentric portion and a second eccentric portion sequentially disposed below the rotor; and The first eccentric portion and the second eccentric portion are disposed on opposite radial sides of the main body.

4. The rotary compressor according to claim 3, characterized in that, The number of weight-reducing grooves is one, and it is located on the opposite side of the second eccentric portion relative to the main body; and / or The weight reduction groove is disposed on the axial end face of the rotor near the first eccentric part.

5. The rotary compressor of claim 4, wherein The compression component further includes: The first roller and the second roller are respectively fitted onto the first eccentric part and the second eccentric part; The static balance ratio of the crankshaft is calculated using the following formula: Where A represents the static balance ratio, m1 represents the eccentric mass of the rotor, m2 represents the mass of the first eccentric part, m3 represents the mass of the first roller, m4 represents the mass of the second eccentric part, m5 represents the mass of the second roller, r1 represents the distance between the center of gravity of the rotor and the rotation axis of the main body, r2 represents the distance between the center of gravity of the second eccentric part and the rotation axis of the main body, r3 represents the distance between the center of gravity of the first roller and the rotation axis of the main body, r4 represents the distance between the center of gravity of the first eccentric part and the rotation axis of the main body, and r5 represents the distance between the center of gravity of the second roller and the rotation axis of the main body; and The static balance ratio A is 80% to 120%.

6. The rotary compressor of claim 4, wherein The compression component further includes: The first roller and the second roller are respectively fitted onto the first eccentric part and the second eccentric part; The dynamic balance ratio of the crankshaft is calculated according to the following formula: Where B represents the dynamic balance ratio, m1 represents the eccentric mass of the rotor, m2 represents the mass of the first eccentric part, m3 represents the mass of the first roller, m4 represents the mass of the second eccentric part, m5 represents the mass of the second roller, r1 represents the distance between the center of gravity of the rotor and the rotation axis of the main body, r2 represents the distance between the center of gravity of the second eccentric part and the rotation axis of the main body, r3 represents the distance between the center of gravity of the first roller and the rotation axis of the main body, r4 represents the distance between the center of gravity of the first eccentric part and the rotation axis of the main body, r5 represents the distance between the center of gravity of the second roller and the rotation axis of the main body, L1 represents the distance between the center of gravity of the rotor and the bottom surface of the second eccentric part, L2 represents the distance between the center of gravity of the first eccentric part and the bottom surface of the second eccentric part, L3 represents the distance between the center of gravity of the first roller and the bottom surface of the second eccentric part, L4 represents the distance between the center of gravity of the second eccentric part and the bottom surface of the second eccentric part, and L5 represents the distance between the center of gravity of the second roller and the bottom surface of the second eccentric part. The dynamic balance rate B is 70% to 130%.

7. The rotary compressor according to claim 6, characterized in that, The dynamic balance rate B is greater than or equal to 110%.

8. The rotary compressor of claim 1, wherein, The compression component further includes: At least one roller is respectively fitted onto the at least one eccentric portion; wherein... The roller is made of at least one material selected from ceramic and aluminum alloy; and / or, The density range of the roller is 2.7 g / mm². 3 Up to 2.8g / mm 3 .

9. The rotary compressor according to claim 1, characterized in that, The rotary compressor operates at a speed of less than or equal to 200 rpm; and / or The rotary compressor operates at a frequency range of 30Hz to 200Hz.

10. An air conditioner characterized by comprising: Includes the rotary compressor as described in any one of claims 1-9.

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