Compressor and air conditioner having the same

Abstract

The present invention provides a compressor and an air conditioner having the same. The compressor includes a pump body structure, the pump body structure includes a crankshaft, the crankshaft includes at least one eccentric portion, the thrust surface area of ​​the eccentric portion is S, the eccentric torque received by the crankshaft is T, and the rated cooling capacity of the compressor is Q, wherein 30≤Q / (T×S)≤60. In combination with the rated cooling capacity of the compressor and the optimization of the structure of the eccentric portion on the crankshaft, the effect of the eccentric torque received by the crankshaft is improved, making the compressor more stable during operation and being able to effectively reduce the noise of the compressor. The compressor adopts this structure, which greatly reduces the fluctuation of the resistance torque of the compressor at ultra-high speed, improves the problems of increased noise, vibration and deflection of the compressor, and at the same time maximizes the energy efficiency of the compressor, fundamentally ensuring the application reliability of the miniaturized compressor.

Description

Technical Field

[0001] The present invention relates to the technical field of air conditioner equipment, and in particular to a compressor and an air conditioner having the same. Background Art

[0002] As a core component of variable-frequency air conditioners, variable-frequency rotor compressors have been widely promoted and applied in the market due to their simple structure, relatively low cost, and high energy efficiency. With the development of new materials and technologies, the demand for miniaturization and energy conservation in variable-frequency air conditioner systems is increasing. How to better achieve the miniaturization of compressors used in air conditioning systems is a common challenge facing technological development within the industry.

[0003] At present, the main technical direction for miniaturization of variable-frequency rotor compressors is to achieve the target cooling capacity by increasing the speed. When the compressor speed is greatly increased, the working environment of the shaft system during operation is seriously deteriorated, and the resistance torque fluctuation is greatly increased, which will increase the deflection of the crankshaft and intensify the noise and vibration of the compressor, and is very detrimental to the reliability of the compressor.

[0004] The solution to this problem is typically to increase structural rigidity, such as by increasing the crankshaft diameter. However, this significantly increases the friction area, reducing energy efficiency. Alternatively, reducing the bearing span can be a solution, but this is significantly limited by the compressor's inherent structural design, making compressors employing this structure less practical.

[0005] In summary, for variable-frequency compressors that use small and high-speed technology, how to solve the noise and reliability problems caused by resistance torque fluctuations on the shaft system without affecting compressor performance is one of the technical bottlenecks that needs to be solved urgently in this field. Summary of the Invention

[0006] The main purpose of the present invention is to provide a compressor and an air conditioner having the same, so as to solve the problem of high noise of the compressor in the prior art.

[0007] In order to achieve the above-mentioned object, according to one aspect of the present invention, a compressor is provided, comprising: a pump body structure, the pump body structure comprising a crankshaft, the crankshaft comprising at least one eccentric portion, the thrust surface area of ​​the eccentric portion being S, the eccentric torque applied to the crankshaft being T, and the rated cooling capacity of the compressor being Q, wherein 30≤Q / (T×S)≤60.

[0008] Furthermore, the pump body structure includes: a lower flange; an upper flange, the lower flange is arranged opposite to the upper flange, a plurality of cylinders are arranged between the lower flange and the upper flange, and the crankshaft passes through the upper flange, the plurality of cylinders and the lower flange in sequence; wherein, an eccentric portion is arranged in each cylinder, and the area of ​​the thrust surface of the eccentric portion arranged near the lower flange is S.

[0009] Furthermore, the eccentricity of the eccentric portion is e, the mass of the eccentric portion is M, and T=9.8×M×e.

[0010] Furthermore, the area of ​​the thrust surface of the eccentric portion disposed close to the lower flange is S.

[0011] Furthermore, a roller is provided on the outer peripheral side of the eccentric portion, the mass of the roller is M1, and the eccentric moment acting on the pump body structure is T1=9.8×(M+M1)×e.

[0012] Further, 10≤Q / (T1×S)≤30, or, 14≤Q / (T1×S)≤26, or, 17≤Q / (T1×S)≤19, or, Q / (T1×S)=18.7.

[0013] Further, 33≤Q / (T×S)≤55, or, 40≤Q / (T×S)≤50, or, Q / (T×S)=43.2.

[0014] Furthermore, there are two cylinders, which are arranged along the axial direction of the crankshaft.

[0015] Furthermore, the frequency of the compressor is greater than or equal to 120 rps.

[0016] According to another aspect of the present invention, an air conditioner is provided, comprising a compressor, which is the above-mentioned compressor.

[0017] By applying the technical solution of this invention, combined with the rated cooling capacity of the compressor and optimizing the structure of the eccentric portion on the crankshaft, the eccentric torque acting on the crankshaft is reduced, making the compressor more stable during operation and effectively reducing compressor noise. Compressors employing this structure significantly reduce resistance torque fluctuations at ultra-high speeds, addressing issues such as increased noise, vibration, and deflection, while maximizing compressor energy efficiency and fundamentally ensuring the reliability of miniaturized compressor applications. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] The accompanying drawings, which constitute part of this application, are intended to provide a further understanding of the present invention. The exemplary embodiments of the present invention and their descriptions are intended to explain the present invention and do not constitute an undue limitation of the present invention. In the accompanying drawings:

[0019] Figure 1 A schematic cross-sectional view of an embodiment of a pump body structure according to the present invention is shown;

[0020] Figure 2 A schematic structural diagram of a first embodiment of a crankshaft according to the present invention is shown;

[0021] Figure 3A schematic structural diagram of a second embodiment of a crankshaft according to the present invention is shown;

[0022] Figure 4 and Figure 5 The figure shows the total noise value of the compressor according to the present invention at a frequency of 180 rps.

[0023] The above drawings include the following reference numerals:

[0024] 10. Pump body structure; 11. Crankshaft; 111. Eccentric part;

[0025] 12. Lower flange;

[0026] 13. Upper flange; 14. Cylinder; 15. Roller. DETAILED DESCRIPTION

[0027] It should be noted that, in the absence of conflict, the embodiments and features of the embodiments in this application can be combined with each other. The present invention will be described in detail below with reference to the accompanying drawings and in combination with the embodiments.

[0028] It should be noted that the terms used herein are only for describing specific embodiments and are not intended to limit the exemplary embodiments according to the present application. As used herein, unless the context clearly indicates otherwise, the singular form is also intended to include the plural form. In addition, it should be understood that when the terms "comprise" and / or "include" are used in this specification, they indicate the presence of features, steps, operations, devices, components and / or combinations thereof.

[0029] It should be noted that the terms "first", "second", etc. in the specification and claims of the present application and the above-mentioned drawings are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence. It should be understood that the terms used in this way are interchangeable where appropriate, so that the embodiments of the present application described herein can, for example, be implemented in an order other than those illustrated or described herein. In addition, the terms "including" and "having" and any variations thereof are intended to cover non-exclusive inclusions, for example, a process, method, system, product or device that includes a series of steps or units is not necessarily limited to those steps or units clearly listed, but may include other steps or units that are not clearly listed or inherent to these processes, methods, products or devices.

[0030] Now, exemplary embodiments according to the present application will be described in more detail with reference to the accompanying drawings. However, these exemplary embodiments can be implemented in a variety of different forms and should not be interpreted as being limited to the embodiments described herein. It should be understood that these embodiments are provided to make the disclosure of this application thorough and complete, and to fully convey the concepts of these exemplary embodiments to those of ordinary skill in the art. In the accompanying drawings, for the sake of clarity, the thickness of layers and regions may be exaggerated, and the same reference numerals are used to represent the same devices, and thus their descriptions will be omitted.

[0031] Combine Figures 1 to 5 As shown, according to a specific embodiment of the present application, a compressor is provided.

[0032] Specifically, if Figure 1 As shown, the compressor includes a pump body structure 10. Pump body structure 10 includes a crankshaft 11. Crankshaft 11 includes at least one eccentric portion 111. The thrust surface area of ​​eccentric portion 111 is S, the eccentric torque applied to crankshaft 11 is T, and the rated cooling capacity of the compressor is Q, where 30 ≤ Q / (T×S) ≤ 60, and the unit of Q is W.

[0033] In this embodiment, the eccentric portion of the crankshaft is optimized to minimize the effect of eccentric torque on the crankshaft, taking into account the compressor's rated cooling capacity. This improves the compressor's stability during operation and effectively reduces compressor noise. This compressor significantly reduces resistance torque fluctuations at ultra-high speeds, improves compressor noise, vibration, and deflection, and maximizes compressor energy efficiency, fundamentally ensuring the reliability of miniaturized compressor applications. In this application, the compressor frequency is greater than or equal to 120 rps.

[0034] The pump body structure 10 includes a lower flange 12 and an upper flange 13. The lower flange 12 is arranged opposite to the upper flange 13, and a plurality of cylinders 14 are arranged between the lower flange 12 and the upper flange 13. The crankshaft 11 passes through the upper flange 13, the plurality of cylinders 14 and the lower flange 12 in sequence. Each cylinder 14 is provided with an eccentric portion 111, such as Figure 2 As shown at A in the middle, the area of ​​the thrust surface of the eccentric portion 111 arranged close to the lower flange 12 is S.

[0035] Preferably, there are two cylinders 14, arranged axially along the crankshaft 11. A partition may be provided between the two cylinders 14. The eccentricity of each eccentric portion 111 is e, and the mass of each eccentric portion 111 is M, where T = 9.8 × M × e. The thrust surface area of ​​the eccentric portion 111 located near the lower flange 12 is S. This arrangement can effectively improve the energy efficiency of the compressor.

[0036] like Figure 1 As shown, rollers 15 are provided on the outer periphery of the eccentric portion 111. The mass of each roller 15 is M1, and the eccentric moment acting on the pump structure 10 is T1 = 9.8 × (M + M1) × e. Here, 10 ≤ Q / (T1 × S) ≤ 30, or 14 ≤ Q / (T1 × S) ≤ 26, or 17 ≤ Q / (T1 × S) ≤ 19, or Q / (T1 × S) = 18.7.

[0037] In order to further improve the energy efficiency of the compressor, the eccentric torque T applied to the crankshaft 11, the rated cooling capacity Q of the compressor, and the area S of the thrust surface of the eccentric portion 111 can be set to 33≤Q / (T×S)≤55, or 40≤Q / (T×S)≤50, or Q / (T×S)=43.2.

[0038] The compressor in the above embodiment can also be used in the technical field of air-conditioning equipment. That is, according to another aspect of the present invention, an air-conditioner is provided, comprising a compressor, which is the compressor in the above embodiment.

[0039] Specifically, the air conditioner also includes a compressor distributor, a motor stator, a motor rotor, a housing assembly, an air conditioning circulation system, and the like.

[0040] This compressor is a rotary compressor, primarily composed of a pump body assembly, a motor rotor, a motor stator, and a housing assembly. The pump body assembly primarily consists of an upper flange, a crankshaft, a middle diaphragm, a cylinder, rollers, and a lower flange. The upper flange is located on the upper end face of the upper cylinder, while the lower flange is located on the lower end face of the lower cylinder. The major and minor ends of the crankshaft pass through the upper and lower flange bearing necks, respectively. The upper and lower eccentric portions of the crankshaft are located within the cylinder, respectively. Rollers are located outside the upper and lower eccentric portions of the crankshaft and contact the sliding vanes within the cylinder, dividing the cylinder into an intake chamber and a compression chamber. The motor rotor drives the crankshaft to rotate, and the upper and lower eccentric portions of the crankshaft drive the rollers in a circular motion, as well as the rollers themselves. When low-temperature, low-pressure refrigerant vapor flows from the cylinder intake port into the intake chamber, the crankshaft drives the rollers in a circular motion, compressing the refrigerant. The compressed, high-temperature, high-pressure refrigerant gas is discharged from the exhaust port, completing the refrigerant compression process.

[0041] The application of miniaturization and broadband technologies to compressors generally achieves the same cooling capacity by increasing the speed. However, when the compressor operates at ultra-high speeds (especially 120 rps and above), the working environment of the internal shafting system deteriorates significantly. The resistance torque fluctuations experienced by the crankshaft and pump assembly increase significantly, which in turn increases crankshaft deflection, exacerbating compressor noise and vibration, severely affecting the user experience. It also causes wear on the compressor, which is very detrimental to its reliability.

[0042] In order to solve the problems existing in the prior art, another embodiment of the present application provides a rotor compressor crankshaft, which is composed of a long shaft end, an upper eccentric portion, a connecting portion, a lower eccentric portion and a short shaft end connected in sequence, wherein the distance between the outer center line of the upper and lower eccentric portions and the center line of the long shaft is called the eccentricity e (unit: mm), and the side of the lower eccentric portion in contact with the lower flange is called the thrust surface, and its area is S (unit: mm). 2 The product of the eccentric mass M (in kg) and the eccentricity e is called the crankshaft eccentric moment T, where T = 9.8 × M × e. When the system cooling capacity is constant, if the crankshaft eccentric moment T is too large, the deflection of the compressor will increase significantly when operating at ultra-high speeds (120 rps and above). The eccentric torque on the crankshaft from the eccentric moment fluctuates violently, causing the compressor to experience increased noise and vibration. Furthermore, due to the increased friction pair area, friction noise and power consumption increase, adversely affecting compressor performance and reliability. If the crankshaft eccentric moment T is too low—that is, the eccentricity e is too small or the eccentric mass M is too small—the compressor displacement and reliability will be adversely affected, reducing the compressor coefficient of performance (COP) and crankshaft operating stability, which is detrimental to compressor reliability. While maintaining the remaining compressor structure, appropriately increasing the crankshaft thrust surface area S can improve the crankshaft's load-bearing capacity and slightly reduce crankshaft deflection. In addition to the above factors, as the system's rated cooling capacity (Q) increases, the compressor speed increases, and the exhaust volume increases, the torque fluctuations on the crankshaft increase, affecting the noise, vibration, and reliability of the compressor. To address this technical issue, extensive experimental research has revealed that when the ratio of the system's rated cooling capacity (Q) to the eccentric torque T on the crankshaft and the crankshaft's thrust area (S) is controlled within a certain range, the eccentric torque on the crankshaft is kept within an optimal range, effectively reducing the compressor's resistance torque fluctuations, noise, vibration, and increased deflection at high speeds. This, in turn, maximizes compressor energy efficiency and ensures compressor reliability.

[0043] It should be explained that the rated cooling capacity of the compressor is Q, which can be the rated cooling capacity of the air-conditioning system, wherein Q / (T×S) represents the crankshaft force under unit cooling capacity.

[0044] According to the rotary compressor provided by the present application, by setting the ratio Q / (T×S) of the cooling capacity of the air-conditioning system to the eccentric torque T on the crankshaft and the crankshaft thrust area S within the following range, that is, when 30≤Q / (T×S)≤60, the resistance torque fluctuation during the operation of the compressor is small, the noise and vibration level is excellent, and the crankshaft deflection is small, which can ensure the reliability of the compressor in high-speed operation. When 33≤Q / (T×S)≤55, the total noise value is significantly reduced. Further, when 40≤Q / (T×S)≤50, the total noise value reaches the optimal level. Figure 5 As shown in the figure, the noise effect is best when Q / (T×S)=43.2.

[0045] like Figure 1 As shown, the mass of the roller is M1 (in kg). When the ratio of the cooling capacity of the air conditioning system to the eccentric mass of the pump structure (M+M1) and the crankshaft thrust area S is controlled within a certain range, the above technical effects can also be achieved. In this case, the eccentric torque T1 on the pump structure is 9.8×(M+M1)×e. The formula Q / (T1×S) represents the eccentric torque of the pump structure per unit cooling capacity. T1 and S should satisfy the relationship: when 10≤Q / (T1×S)≤30, the compressor noise level is optimal; when 14≤Q / (T1×S)≤26, the noise reduction effect is further improved, and the noise level is optimized when 17≤Q / (T1×S)≤19. In this embodiment, the total noise value is lowest when Q / (T1×S)=18.7.

[0046] Since the cooling capacity of the compressor is greatly improved at ultra-high speed, the drastic resistance torque fluctuations are resisted by controlling the size of the eccentric mass and the crankshaft thrust area. If the eccentric mass M is appropriate and the crankshaft thrust area S matches the working load, that is, the shaft system itself has sufficient rigidity, the crankshaft deflection is reduced at high speed, and the balance system and operating stability of the crankshaft at high speed are improved, so that the unit radial force of the crankshaft under unit cooling capacity is improved, thereby reducing the crankshaft deflection at high speed and maximizing the total noise value of vibration noise and friction noise; at the same time, the power consumption of the compressor at high speed is greatly reduced, thereby maximizing the compressor performance coefficient COP and ensuring the reliability of the compressor operation.

[0047] The cylinder of the pump body structure of the compressor in this application can be a single-cylinder, double-cylinder, triple-cylinder or multi-cylinder compressor structure.

[0048] For ease of description, spatially relative terms such as "above," "above," "on the upper surface of," and "upper" may be used herein to describe the spatial positional relationship of a device or feature to other devices or features as shown in the figures. It should be understood that spatially relative terms are intended to encompass different orientations of the device in use or operation in addition to the orientation depicted in the figures. For example, if a device in a drawing is inverted, a device described as "above" or "on top of" another device or structure would then be positioned as "below" or "below" the other device or structure. Thus, the exemplary term "above" can include both the "above" and "below" orientations. The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatially relative descriptions used herein should be interpreted accordingly.

[0049] In addition to the above, it should be noted that references to "one embodiment," "another embodiment," "an embodiment," and the like in this specification refer to specific features, structures, or characteristics described in conjunction with that embodiment as included in at least one embodiment generally described in this application. The appearance of the same expression in multiple places in the specification does not necessarily refer to the same embodiment. Furthermore, when a specific feature, structure, or characteristic is described in conjunction with any embodiment, it is intended that such feature, structure, or characteristic, when implemented in conjunction with other embodiments, also falls within the scope of the present invention.

[0050] In the above embodiments, the description of each embodiment has its own focus. For parts that are not described in detail in a certain embodiment, reference can be made to the relevant descriptions of other embodiments.

[0051] The foregoing description is merely a preferred embodiment of the present invention and is not intended to limit the present invention. Those skilled in the art will readily appreciate that various modifications and variations of the present invention are possible. Any modifications, equivalent substitutions, or improvements made within the spirit and principles of the present invention are intended to be within the scope of protection of the present invention.

Claims

1. A compressor, characterized in that: include: A pump body structure (10), the pump body structure (10) includes a crankshaft (11), the crankshaft (11) includes at least one eccentric portion (111), the thrust surface area of ​​the eccentric portion (111) is S, the eccentric torque applied to the crankshaft (11) is T, and the rated cooling capacity of the compressor is Q, wherein 30≤Q / (T×S)≤60, the unit of S is mm², and the unit of Q is W; The eccentricity of the eccentric portion (111) is e, the mass of the eccentric portion (111) is M, and T=9.8×M×e; A roller (15) is provided on the outer peripheral side of the eccentric portion (111), the mass of the roller (15) is M1, and the eccentric moment applied to the pump body structure (10) is T1=9.8×(M+M1)×e; Among them, the unit of M is kg, the unit of e is mm, and the unit of M1 is kg.

2. The compressor according to claim 1, characterized in that The pump body structure (10) comprises: Lower flange (12); An upper flange (13), the lower flange (12) being arranged opposite to the upper flange (13), a plurality of cylinders (14) being arranged between the lower flange (12) and the upper flange (13), and the crankshaft (11) being arranged to pass through the upper flange (13), the plurality of cylinders (14) and the lower flange (12) in sequence; Wherein, an eccentric portion (111) is provided in each of the cylinders (14), and the thrust surface of the eccentric portion (111) provided close to the lower flange (12) has an area of ​​S.

3. The compressor according to claim 2, characterized in that 10≤Q / (T1×S)≤30, or, 14≤Q / (T1×S)≤26, or, 17≤Q / (T1×S)≤19, or, Q / (T1×S)=18.

7.

4. The compressor according to claim 1, characterized in that 33≤Q / (T×S)≤55, or, 40≤Q / (T×S)≤50, or, Q / (T×S)=43.

2.

5. The compressor according to claim 2, characterized in that There are two cylinders (14), and the two cylinders (14) are arranged along the axial direction of the crankshaft (11).

6. The compressor according to claim 1, characterized in that The frequency of the compressor is greater than or equal to 120 rps.

7. An air conditioner comprising a compressor, characterized in that: The compressor is the compressor according to any one of claims 1 to 6.

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