Compressors and air conditioners

Abstract

The present application provides a compressor and an air conditioner. The compressor comprises a housing (1), the total displacement of the compressor is V, the sum of the cross-sectional areas of the exhaust holes of all pump body components of the compressor is S, the inner diameter of the housing (1) is D, wherein V, S and D satisfy the relationship: u = V / (S * D), 0.68 ≤ u ≤ 1.31. According to the compressor of the present application, the reliability of the air valve of the compressor during high-frequency operation can be ensured, and the pneumatic noise during high-frequency operation can be reduced.

Description

Technical Field

[0001] The present application relates to the technical field of air conditioning, and in particular to a compressor and an air conditioner. Background Art

[0002] The technical development of air-conditioning compressors tends to be miniaturized and high-speed. The size of compressors is getting smaller and smaller, and the operating frequency is getting higher and higher. The maximum operating frequency of conventional compressors is 110 Hz to 120 Hz, and the maximum operating frequency of high-speed compressors can reach more than 200 Hz. This puts higher requirements on the design of compressors. However, the modernization of compressors will also bring a series of problems. The reliability, noise and performance of small and large-displacement compressors at high speed are difficult design issues.

[0003] A compressor is disclosed in the prior art, in which the ratio of the total displacement of the compressor to the total cross-sectional area of ​​the exhaust holes mainly affects the performance of the compressor, and solves the problem of low performance in the design of high-speed compressors. However, the performance problem of high-speed compressors is only one difficult problem in the design. There are two other key difficult problems that need to be solved. The first is the reliability of the compressor's air valve during high-speed operation, and the second is the large aerodynamic noise generated by the sharp increase in gas pressure pulsation in the compressor casing due to high-speed operation. However, the disclosed compressor has not conducted research in this regard. Summary of the invention

[0004] Therefore, the technical problem to be solved by the present application is to provide a compressor and an air conditioner that can ensure the reliability of the air valve during high-frequency operation of the compressor and reduce the pneumatic noise during high-frequency operation.

[0005] In order to solve the above problems, the present application provides a compressor, which includes a shell. The total displacement of the compressor is V, the sum of the cross-sectional areas of the exhaust holes of all pump body components of the compressor is S, and the inner diameter of the shell is D, wherein V, S and D satisfy the relationship: u=V / (S﹡D), 0.68≤u≤1.31.

[0006] Preferably, 0.70≤u≤1.

[0007] Preferably, u=0.8.

[0008] Preferably, a pump body assembly is arranged in the shell, and the pump body assembly comprises a cylinder, an upper flange and a lower flange, and the cylinder is arranged between the upper flange and the lower flange.

[0009] Preferably, the exhaust holes of the pump body assembly include flange exhaust holes, cylinder exhaust holes and / or partition exhaust holes.

[0010] Preferably, the pump body assembly further comprises a crankshaft, the cylinder, the upper flange and the lower flange are all sleeved outside the crankshaft, and a roller is arranged between the crankshaft and the inner circumferential wall of the cylinder.

[0011] Preferably, a slide groove is provided on the cylinder, a slide plate is provided in the slide groove, an elastic device is provided at one end of the slide plate, and the other end of the slide plate abuts against the outer wall of the roller.

[0012] Preferably, a driving assembly is also provided in the housing, and the driving assembly includes a stator assembly and a rotor assembly. The stator assembly is fixedly provided on the housing, and the rotor assembly is drivingly connected to the crankshaft.

[0013] According to another aspect of the present application, an air conditioner includes a compressor, which is the above-mentioned compressor.

[0014] The compressor provided in the present application includes a housing, the total displacement of the compressor is V, the sum of the cross-sectional areas of the exhaust holes of all pump body components of the compressor is S, and the inner diameter of the housing is D, wherein V, S and D satisfy the relationship: u = V / (S * D), 0.68 ≤ u ≤ 1.31. By reasonably setting the relationship between the total displacement of the compressor, the sum of the cross-sectional areas of the exhaust holes of all pump body components and the inner diameter of the housing, the reliability of the air valve of the compressor during high-frequency operation can be ensured, the pneumatic noise during high-frequency operation can be reduced, and at the same time, the performance during high-frequency operation can be ensured to meet the design requirements. BRIEF DESCRIPTION OF THE DRAWINGS

[0015] Figure 1 It is a schematic cross-sectional structural diagram of a compressor according to an embodiment of the present application;

[0016] Figure 2 A schematic diagram of the cross-sectional structure of a compressor according to an embodiment of the present application;

[0017] Figure 3 The relationship curve between the maximum contact stress of the valve plate impacting the valve seat and V / (S*D) of the compressor of the embodiment of the present application;

[0018] Figure 4 The relationship curve between the total noise value and V / (S*D) of the compressor at different operating frequencies according to the embodiment of the present application;

[0019] Figure 5 1 is a relationship curve between APF energy efficiency and V / (S*D) at different operating frequencies of the compressor of the embodiment of the present application.

[0020] The reference numerals are:

[0021] 1. Housing; 2. Cylinder; 3. Upper flange; 4. Lower flange; 5. Crankshaft; 6. Slide; 7. Slide vane; 8. Roller; 9. Stator assembly; 10. Rotor assembly. DETAILED DESCRIPTION

[0022] There are many technical difficulties in designing high-speed compressors with a maximum operating frequency of more than 200 Hz. The main problems include poor reliability of air valves, high pneumatic noise and serious performance degradation during high-frequency operation.

[0023] The inventors conducted in-depth research on this issue and found that there is a certain functional relationship between the total displacement V of the compressor and the sum of the cross-sectional areas S of all the exhaust holes of the pump body assembly and the inner diameter D of the shell, which can enable the compressor to meet both the reliability requirements and the noise and performance requirements when operating at high frequency.

[0024] Based on this, the inventor conducted further research and experiments, and through a large number of compressor thermodynamic process fluid-solid coupling simulation analysis and experimental tests, it was determined that when the compressor is running at high frequency, under the condition of a certain total displacement of the compressor, the sum of the cross-sectional area of ​​the exhaust holes and the inner diameter of the shell have a limit design. When the limit value is exceeded, it will have a significant adverse effect on the energy efficiency and noise of the compressor, and easily lead to reliability problems of the compressor. For this reason, this application is specially proposed.

[0025] See also Figures 1 to 5 As shown, according to an embodiment of the present application, the compressor includes a shell 1, the total displacement of the compressor is V, the sum of the cross-sectional areas of the exhaust holes of all pump body components of the compressor is S, and the inner diameter of the shell 1 is D, wherein V, S and D satisfy the relationship: u=V / (S﹡D), 0.68≤u≤1.31.

[0026] The inventors have determined that when the u value exceeds 1.31, the stress of the air valve impacting the valve seat is large, exceeding the design requirements, and the compressor reliability problem is likely to occur. When the u value is less than 0.68, the exhaust port area and the inner diameter of the shell are too large. The increase in the exhaust port area will lead to an increase in the clearance volume, a decrease in volumetric efficiency, and a significant decrease in the energy efficiency of the compressor. At the same time, after the exhaust port is enlarged, the forces on both sides of the exhaust valve plate become greater, the impact force of the exhaust valve plate during movement becomes greater, and the reliability of the exhaust valve plate will also deteriorate. The excessive inner diameter of the shell will lead to an increase in the noise radiation surface of the compressor, which will also lead to an increase in noise.

[0027] When the compressor is running at high frequency, aerodynamic noise is the main contributor to the compressor noise. Through a large number of experiments and simulation analysis, it is known that under the condition of a certain total displacement V, the size of the compressor aerodynamic noise is directly related to the sum of the cross-sectional areas of all exhaust holes S and the inner diameter of the shell D. The higher the compressor operating frequency, the more gas is discharged per unit time, the gas pulsation speed increases significantly, and the gas pressure pulsation increases sharply, which will cause greater aerodynamic noise. The smaller the sum of the cross-sectional areas of all exhaust holes S, the greater the change in gas pulsation speed. The smaller the inner diameter D of the shell, the smaller the volume of the expansion cavity after the gas is discharged, and the pressure pulsation in the shell will also increase. The increase in pressure pulsation will cause the aerodynamic noise to increase.

[0028] Figure 3 This is the relationship curve between the maximum contact stress of the compressor exhaust valve plate impacting the valve seat and V / (S﹡D) in the embodiment of the present application. Through experimental testing and simulation analysis, it is found that when the maximum impact stress of the exhaust valve plate exceeds 123Mpa when the exhaust valve plate runs at high speed, the exhaust valve plate will break after long-term reliability testing. When the sum of the cross-sectional areas of the exhaust holes and the product of the inner diameter of the shell decrease, the exhaust speed increases, and the exhaust process and the pressure pulsation in the shell will also increase significantly accordingly. After reaching a certain limit, the valve breaks and the compressor has reliability problems. According to the reliability requirements, the maximum limit value of V / (S﹡D) is 1.31.

[0029] Figure 4 The relationship curve between the total noise value and V / (S﹡D) of the compressor at different operating frequencies of the embodiment of the present application is shown. The noise of the compressor will increase significantly when running at high speed. The change of the inner diameter of the shell affects the pressure pulsation in the compressor and also affects the noise radiation surface of the compressor. The area size of the exhaust hole will affect the exhaust airflow pulsation, and then affect the exhaust pneumatic noise. When the displacement is constant, the product of the sum of the cross-sectional areas S of the exhaust holes of the pump body assembly and the inner diameter D of the shell increases, the exhaust speed decreases, the pressure pulsation in the compressor decreases, and the noise also decreases. After increasing to a certain extent, the pressure pulsation decreases. Due to the increase in the noise radiation surface of the compressor, the compressor noise begins to rise, so V / (S﹡D) will have a minimum value, and the embodiment of the present invention takes the minimum value of 0.68. The product of the sum of the cross-sectional areas S of the exhaust holes of the pump body assembly and the inner diameter D of the shell decreases, the exhaust port area decreases, the exhaust flow rate increases, the exhaust pressure pulsation increases, the inner diameter of the shell decreases, the pressure pulsation in the shell increases, and the compressor noise rises rapidly. The upper limit value of the embodiment of the present invention is 1.31.

[0030] Figure 5 The relationship curve between the APF energy efficiency and V / (S﹡D) of the compressor at different operating frequencies of the embodiment of the present application is as follows. When the total displacement V of the compressor is constant, the larger the product of the total cross-sectional area S of the exhaust holes and the inner diameter D of the shell, the compressor energy efficiency will first increase and then decrease, the clearance volume will increase accordingly, and the volumetric efficiency will decrease accordingly. After reaching a certain ratio, the compressor energy efficiency will decrease rapidly. When the total displacement V of the compressor is constant, the smaller the product of the total cross-sectional area S of the exhaust holes and the inner diameter D of the shell, the faster the exhaust flow rate increases, and the exhaust loss increases significantly. The higher the frequency, the greater the increase in exhaust loss. After reaching a certain ratio, the compressor energy efficiency decreases rapidly.

[0031] Based on the above analysis, this application reasonably sets the u value so that 0.68≤u≤1.31, which can reasonably set the relationship between the total displacement of the compressor, the sum of the cross-sectional areas of the exhaust holes of all pump body components, and the inner diameter of the shell, thereby ensuring the reliability of the air valve during high-frequency operation of the compressor, reducing the pneumatic noise during high-frequency operation, and ensuring that the performance during high-frequency operation meets the design requirements.

[0032] However, for existing low-frequency operating compressors, u≥1.4, so the existing compressors obviously cannot meet the design requirements for high-frequency operation.

[0033] Preferably, 0.70≤u≤1.

[0034] Combination Figures 3 to 5 As shown in the figure, when 0.70≤u≤1, the maximum contact stress of the exhaust valve plate impacting the valve seat can be controlled within a smaller range. At the same time, the total noise value and the APF energy efficiency can also be balanced, so that the compressor as a whole operates within a better energy efficiency range, further improving the working performance of the compressor.

[0035] Preferably, u=0.8, which can comprehensively consider the correlation between the contact stress of the exhaust valve plate impacting the valve seat, the total noise value and the APF energy efficiency, so that a balance can be formed among the three, and all aspects can meet the better design requirements, ensuring that the comprehensive performance of the compressor can reach the best.

[0036] A pump body assembly is arranged in the housing 1 , and the pump body assembly includes a cylinder 2 , an upper flange 3 and a lower flange 4 , and the cylinder 2 is arranged between the upper flange 3 and the lower flange 4 .

[0037] The exhaust holes of the pump body assembly include flange exhaust holes, cylinder exhaust holes and / or partition exhaust holes.

[0038] The pump body assembly further includes a crankshaft 5 , the cylinder 2 , the upper flange 3 and the lower flange 4 are all sleeved outside the crankshaft 5 , and a roller 8 is arranged between the crankshaft 5 and the inner circumferential wall of the cylinder 2 .

[0039] The pump assembly includes at least one cylinder 2, and an eccentrically rotating roller 8 is correspondingly arranged in the cavity of each cylinder 2. The roller 8 is assembled on the eccentric part of the crankshaft 5. The cylinder 2, the roller 8 and the crankshaft 5 are supported by the main and auxiliary bearings. Each cylinder 2 corresponds to at least two exhaust holes, and the two exhaust holes can be arranged on both sides of the cylinder 2, or on the same side of the cylinder 2, or one exhaust hole is arranged on one side of the cylinder 2 and the other is arranged on the side of the cylinder 2.

[0040] Exhaust ports may be provided on the upper flange 3 and the lower flange 4 , and exhaust valve plates are provided at the exhaust ports of the upper flange 3 and the lower flange 4 .

[0041] The cylinder 2 is provided with a slide groove 6 , a slide plate 7 is provided in the slide groove 6 , an elastic device is provided at one end of the slide plate 7 , and the other end of the slide plate 7 abuts against the outer wall of the roller 8 .

[0042] A driving assembly is also disposed in the housing 1 , and the driving assembly includes a stator assembly 9 and a rotor assembly 10 . The stator assembly 9 is fixedly disposed on the housing 1 , and the rotor assembly 10 is drivingly connected to the crankshaft 5 .

[0043] According to an embodiment of the present application, an air conditioner includes a compressor, which is the above-mentioned compressor.

[0044] It is easy for those skilled in the art to understand that, under the premise of no conflict, the above-mentioned advantageous methods can be freely combined and superimposed.

[0045] The above are only preferred embodiments of the present application and are not intended to limit the present application. Any modifications, equivalent replacements and improvements made within the spirit and principles of the present application shall be included in the protection scope of the present application. The above are only preferred implementations of the present application. It should be pointed out that for ordinary technicians in this technical field, several improvements and variations can be made without departing from the technical principles of the present application, and these improvements and variations should also be regarded as the protection scope of the present application.

Claims

1. A compressor, characterized in that: The compressor comprises a housing (1), the total displacement of the compressor is V, the sum of the cross-sectional areas of the exhaust holes of all pump body components of the compressor is S, and the inner diameter of the housing (1) is D, wherein V, S and D satisfy the relationship: u=V / (S﹡D), 0.70≤u≤0.

8.

2. The compressor according to claim 1, characterized in that A pump body assembly is arranged in the housing (1), the pump body assembly comprising a cylinder (2), an upper flange (3) and a lower flange (4), the cylinder (2) being arranged between the upper flange (3) and the lower flange (4).

3. The compressor according to claim 2, characterized in that The exhaust hole of the pump body assembly includes a flange exhaust hole, a cylinder exhaust hole or a partition exhaust hole.

4. The compressor according to claim 2, characterized in that The pump body assembly further comprises a crankshaft (5), the cylinder (2), the upper flange (3) and the lower flange (4) are all sleeved outside the crankshaft (5), and a roller (8) is provided between the crankshaft (5) and the inner circumferential wall of the cylinder (2).

5. The compressor according to claim 4, characterized in that The cylinder (2) is provided with a slide groove (6), a slide plate (7) is provided in the slide groove (6), an elastic device is provided at one end of the slide plate (7), and the other end of the slide plate (7) abuts against the outer wall of the roller (8).

6. The compressor according to claim 4, characterized in that A drive assembly is also provided in the housing (1), the drive assembly comprising a stator assembly (9) and a rotor assembly (10), the stator assembly (9) being fixedly provided on the housing (1), and the rotor assembly (10) being drivingly connected to the crankshaft (5).

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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