Compressor and air conditioner

Abstract

The present invention provides a compressor and an air conditioner. The compressor comprises a shell and a crankshaft, a roller and a cylinder arranged in the shell. The crankshaft comprises a long shaft, an eccentric part and a short shaft connected in sequence. The roller is sleeved on the eccentric part and the roller is located in a compression chamber of the cylinder. The diameter of the long shaft is d1, the diameter of the short shaft is d2, the inner diameter of the shell is D1, the inner diameter of the cylinder is D2, and the outer diameter of the roller is D3. After a lot of research and experimental verification, the scheme limits the size relationship of the shell, the cylinder, the roller and the long shaft and the short shaft of the crankshaft within the above range, which can effectively reduce the deflection of the crankshaft at high speed, thereby reducing the wear and noise of the crankshaft and improving the reliability and performance of the compressor.

Description

Technical Field

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

[0002] As the core component of variable frequency air conditioners, variable frequency rotary compressors have developed rapidly in the past decade. They use variable frequency control to change the compressor volume with the load, which can significantly improve the seasonal energy efficiency ratio of the air conditioning system and the thermal comfort at low ambient temperatures. With the development of new materials and new technologies, the demand for miniaturization, energy saving and environmental protection of variable frequency air conditioning systems is increasing. How to better realize the miniaturization of compressors used in air conditioning systems is a common problem faced by the development of technology in the industry.

[0003] At present, the main bottleneck of the miniaturization of variable frequency rotary compressors lies in the speed limitation, which is mainly due to the adverse impact on reliability. From the perspective of the compressor body, after the speed is increased, the shaft stress during the operation of the compressor is seriously deteriorated, and the crankshaft deflection increases significantly, which is very unfavorable to the reliability of the compressor.

[0004] To solve the above problems, structural stiffness enhancement measures are generally adopted, including but not limited to: increasing the crankshaft diameter, reducing the bearing span, etc. However, the former will significantly increase the mechanical friction loss while increasing the structural stiffness, seriously affecting the energy efficiency of the compressor; the latter is difficult to apply in practice because the overall design of the pump system is greatly restricted.

[0005] Therefore, for variable frequency compressors under the conditions of wideband technology application, how to solve the reliability problem caused by the influence of shaft stress while ensuring the performance of the compressor is one of the technical bottlenecks that needs to be solved urgently in this field. Summary of the invention

[0006] The present invention provides a compressor and an air conditioner to solve the reliability problem of the compressor caused by force and ensure the performance of the compressor.

[0007] In order to achieve the above-mentioned object, according to one aspect of the present invention, a compressor is provided, characterized in that it comprises a housing and a crankshaft, a roller and a cylinder arranged in the housing, the crankshaft comprises a long shaft, an eccentric part and a short shaft connected in sequence, the roller is sleeved on the eccentric part, and the roller is located in the compression chamber of the cylinder; wherein the diameter of the long shaft is d1, the diameter of the short shaft is d2, the inner diameter of the housing is D1, the inner diameter of the cylinder is D2, the outer diameter of the roller is D3,

[0008] Further,

[0009] Furthermore, the compressor further comprises an upper flange and a lower flange, the long axis is inserted into the upper flange, and the short axis is inserted into the lower flange; wherein the axial dimension of the upper flange is H1, the axial dimension of the cylinder is H2, and the axial dimension of the lower flange is H3,

[0010] Further,

[0011] Furthermore, the diameters of the major axis and the minor axis are equal.

[0012] Furthermore, the eccentric portion, the roller and the cylinder are all multiple, the multiple eccentric portions and the multiple rollers are arranged in a one-to-one correspondence, and the multiple rollers and the multiple cylinders are arranged in a one-to-one correspondence.

[0013] Furthermore, the compressor also includes a stator and a rotor, the stator is arranged in the shell, the rotor is arranged in the stator, and the rotor is connected to the long shaft.

[0014] According to another aspect of the present invention, an air conditioner is provided, comprising the above-mentioned compressor.

[0015] The technical solution of the present invention is applied to provide a compressor, which includes a housing, a crankshaft, a roller, and a cylinder arranged in the housing, wherein the crankshaft includes a long shaft, an eccentric portion, and a short shaft connected in sequence, the roller is sleeved on the eccentric portion, and the roller is located in the compression chamber of the cylinder; wherein the diameter of the long shaft is d1, the diameter of the short shaft is d2, the inner diameter of the housing is D1, the inner diameter of the cylinder is D2, and the outer diameter of the roller is D3. After extensive research and experimental verification, this solution limits the dimensional relationship of the casing, cylinder, rollers, and the major and minor axes of the crankshaft within the above range, which can effectively reduce the deflection of the crankshaft at high speeds, thereby reducing crankshaft wear and noise, and improving the reliability and performance of the compressor. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] The drawings constituting a part of the present application are used to provide a further understanding of the present invention. The exemplary embodiments of the present invention and their descriptions are used to explain the present invention and do not constitute an improper limitation of the present invention. In the drawings:

[0017] Figure 1 A schematic structural diagram of a compressor provided by an embodiment of the present invention is shown;

[0018] Figure 2 The graph shows the change of noise and performance of the compressor with the ratio of the crankshaft diameter to the radial ratio of the compression system;

[0019] Figure 3The graph shows how the noise and performance of the compressor change with the ratio of the crankshaft diameter to the axial direction of the compression system.

[0020] The above drawings include the following reference numerals:

[0021] 10. Housing; 20. Crankshaft; 21. Long shaft; 22. Eccentric part; 23. Short shaft; 30. Roller; 40. Cylinder; 50. Upper flange; 60. Lower flange; 70. Stator; 80. Rotor. DETAILED DESCRIPTION

[0022] The technical solutions in the embodiments of the present invention will be described clearly and completely below in conjunction with the accompanying drawings in the embodiments of the present invention. Obviously, the described embodiments are only a part of the embodiments of the present invention, rather than all of the embodiments. The following description of at least one exemplary embodiment is actually only illustrative and is by no means intended to limit the present invention and its application or use. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0023] like Figure 1 As shown, an embodiment of the present invention provides a compressor, including a housing 10 and a crankshaft 20, a roller 30, and a cylinder 40 arranged in the housing 10, wherein the crankshaft 20 includes a long shaft 21, an eccentric portion 22, and a short shaft 23 connected in sequence, the roller 30 is sleeved on the eccentric portion 22, and the roller 30 is located in a compression chamber of the cylinder 40; wherein the diameter of the long shaft 21 is d1, the diameter of the short shaft 23 is d2, the inner diameter of the housing 10 is D1, the inner diameter of the cylinder 40 is D2, and the outer diameter of the roller 30 is D3,

[0024] From the working process of the rotary compressor crankshaft structure, it can be known that the rotor cooperates with the long axis end of the crankshaft, and the rotor drives the crankshaft to operate stably, which is a necessary condition to ensure the normal operation of the compressor. However, with the development trend of miniaturization of compressors, the main bottleneck lies in the speed limitation. After the crankshaft speed increases, the stress on the compressor shaft system is seriously deteriorated, the crankshaft deflection increases significantly, and the vibration intensifies, which not only increases friction loss and power consumption, causing the compressor performance to decline, but also leads to many problems such as reliability and noise, which greatly affects the user experience.

[0025] In this scheme, after a lot of research and experimental verification, the size relationship of the housing 10, cylinder 40, roller 30, and the long axis 21 and short axis 23 of the crankshaft 20 is limited to the above range, which can effectively reduce the deflection of the crankshaft 20 at high speed, thereby reducing the wear and noise of the crankshaft 20 and improving the reliability and performance of the compressor. This scheme greatly reduces the stress deformation of the shaft system after the compressor speed is increased, and can significantly improve the vibration and deflection problems of the compressor after the speed is increased. The impact on energy efficiency at high frequencies is controllable, which fundamentally ensures the feasibility of the application of miniaturized compressors.

[0026] Further, Through the above arrangement, the performance and reliability of the compressor can be further improved.

[0027] In this embodiment, the compressor further includes an upper flange 50 and a lower flange 60, the long axis 21 is disposed in the upper flange 50, and the short axis 23 is disposed in the lower flange 60; wherein the axial dimension of the upper flange 50 is H1, the axial dimension of the cylinder 40 is H2, and the axial dimension of the lower flange 60 is H3.

[0028] Through research, this solution found that the axial ratio of the crankshaft 20 diameter to the compression system (shell 10, cylinder 40, roller 30, upper flange 50, lower flange 60 and other structures) also has a great influence on the compressor performance, noise vibration and reliability, because the axial ratio of the crankshaft diameter to the compression system represents the crankshaft stiffness per unit width-to-diameter ratio. This solution limits the height of the shell 10, cylinder 40, roller 30, and the radial dimensions of the major axis 21 and minor axis 23 of the crankshaft 20 to the above ranges, which can reduce the wear and noise of the compressor and improve the reliability and performance of the compressor.

[0029] Preferably, Through the above arrangement, the performance and reliability of the compressor can be further improved.

[0030] In this embodiment, the diameters of the major axis 21 and the minor axis 23 can be set to be equal, that is, d1 is equal to d2. Of course, d1 and d2 can also be set to different values ​​as needed.

[0031] In this embodiment, the eccentric part 22, the roller 30 and the cylinder 40 are all multiple, and the multiple eccentric parts 22 and the multiple rollers 30 are arranged in a one-to-one correspondence, and the multiple rollers 30 and the multiple cylinders 40 are arranged in a one-to-one correspondence. That is, the compressor can be set as a multi-cylinder compressor. Of course, the compressor can also be set as one cylinder 40, that is, a single-cylinder compressor. This solution can be applicable to single-cylinder compressors and multi-cylinder compressors, and has a wide range of applications.

[0032] Furthermore, the compressor further includes a stator 70 and a rotor 80, wherein the stator 70 is disposed in the housing 10, the rotor 80 is disposed in the stator 70, and the rotor 80 is connected to the long shaft 21. Through the cooperation between the stator 70 and the rotor 80, the rotor 80 can be rotated, and the rotor 80 drives the crankshaft 20 to rotate when rotating.

[0033] Another embodiment of the present invention provides an air conditioner, which includes the above-mentioned compressor. With this solution, the reliability and performance of the compressor are improved, and the reliability and performance of the air conditioner are also improved accordingly.

[0034] To facilitate understanding of this solution, further explanation is given below.

[0035] It can be seen from the working process of the rotary compressor crankshaft 20 structure that the rotor 80 cooperates with the end of the long axis 21 of the crankshaft 20, and the rotor 80 drives the crankshaft 20 to operate stably, which is a necessary condition to ensure the normal operation of the compressor. However, with the development trend of miniaturization of compressors, its main bottleneck lies in the speed limitation. After the speed of the crankshaft 20 is increased, the stress on the compressor shaft system is seriously deteriorated, the deflection of the crankshaft 20 is significantly increased, and the vibration is intensified, which not only increases friction loss and power consumption, causing the compressor performance to decline, but also leads to many problems such as reliability and noise, which greatly affects the user experience.

[0036] In response to the above problems, structural stiffness enhancement measures are generally taken to solve them, such as increasing the diameter of the crankshaft 20, reducing the span of the bearings (i.e., the upper and lower flanges), and so on. However, increasing the diameter of the shaft will increase the structural stiffness while causing a significant increase in mechanical friction loss, seriously affecting the energy efficiency of the compressor; reducing the bearing span will be difficult to apply in practice because the overall design of the pump system is subject to great restrictions. This patent proposes an optimization design method for the structural stiffness of the shaft system of a rotor compressor, which greatly reduces the stress deformation of the shaft system after the compressor speed is increased, and can significantly improve the vibration and deflection problems of the compressor after the speed is increased, and the impact on energy efficiency at high frequencies is controllable, fundamentally ensuring the feasibility of miniaturized compressor applications.

[0037] The rotary compressor is mainly composed of a housing 10, a motor, and a pump assembly, wherein the pump assembly is mainly composed of a crankshaft 20, a rolling piston, a cylinder 40, a vane, a spring, and upper and lower bearings, and the motor is mainly composed of a stator 70, a rotor 80, and a main balance block. The crankshaft 20 passes through the upper bearing (i.e., the upper flange), the rolling piston in the inner cavity of the cylinder 40, the lower bearing (i.e., the lower flange), etc. in sequence. The rotor 80 cooperates with the end of the long axis 21 of the crankshaft 20, thereby driving the crankshaft 20 to operate stably, and then the eccentric part 22 cooperates with the vane, etc. in the inner cavity of the cylinder 40 to complete the process of suction, compression, and exhaust.

[0038] As the operating frequency increases, the forces on the long axis 21 and the short axis 23 of the crankshaft 20 will increase significantly, aggravating the flexural deformation of the crankshaft 20. The friction loss and vibration of the compressor will also increase significantly, seriously affecting the performance and noise of the compressor.

[0039] After a large number of experiments and studies, the present application has found that when the ratio of the diameter of the crankshaft 20 to the diameter of the housing 10, the cylinder 40, and the roller 30, that is, the radial ratio of the crankshaft 20 to the compressor system is controlled within a certain range, the deflection of the crankshaft 20 at high speed can be effectively reduced. If the radial ratio of the crankshaft 20 diameter to the compression system is too small, then either the crankshaft 20 diameter is too small, or the cylinder 40 and the roller 30 diameter are too large. If the crankshaft 20 diameter is too small, the stress on the crankshaft 20 will seriously deteriorate with the increase of the speed, and the bending deformation of the crankshaft 20 will be aggravated, affecting the noise, performance and reliability of the compressor; if the cylinder 40 and the roller 30 diameter are too large, the eccentric portion 22 and the thrust surface area of ​​the crankshaft 20 will increase, and the eccentric mass will increase, the centrifugal force will also increase linearly, the eccentric torque will increase significantly, the bending deformation of the crankshaft 20 will be aggravated, and the vibration will be aggravated, which will seriously affect the user experience and the reliability of the compressor. If the radial ratio of the crankshaft 20 to the compression system is too large, the stiffness of the crankshaft 20 per unit radial direction increases, so the bending deformation of the crankshaft 20 decreases, but the friction loss increases significantly, seriously affecting the performance of the compressor. Therefore, considering the performance, noise, vibration and reliability, the radial ratio of the crankshaft 20 to the compression system is in the range of 0.03 to 0.05.

[0040] Further research in this patent application has found that the axial ratio of the crankshaft 20 diameter to the compression system also has a great influence on the compressor performance, noise vibration and reliability, because the axial ratio of the crankshaft 20 diameter to the compression system represents the stiffness of the crankshaft 20 per unit width-to-diameter ratio. If the axial ratio of the crankshaft 20 diameter to the compression system is too small, it may be that the crankshaft 20 diameter is too small or the height of the bearing and the cylinder 40 is too large. In the former, the eccentric part 22 and the thrust surface area increase, the eccentric part 22 has a large mass, and the eccentric torque also increases significantly, resulting in aggravated bending deformation of the crankshaft 20 and aggravated vibration, which seriously affects the user experience and the reliability of the compressor; the latter will increase the height of the compressor, affect the overall design of the pump system, and is not conducive to the efficiency improvement of the compressor, nor is it conducive to the miniaturization of the variable frequency rotor 80 compressor. The axial ratio of the crankshaft 20 to the compression system is too large, which may be due to the crankshaft 20 diameter being too large or the bearing height and the cylinder 40 height being too small. If the crankshaft 20 diameter is too large, the contact area between the crankshaft 20 and the bearing will be too large, and the friction loss will increase, affecting the performance of the compressor; if the bearing height and the cylinder 40 height are too small, the contact stress between the crankshaft 20 and the bearing will be too large, increasing the local stress and affecting the reliability of the compressor. Therefore, considering the compressor performance, noise vibration and reliability, the axial ratio of the crankshaft 20 to the compression system should be in the range of 0.30 to 0.34.

[0041] In order to illustrate the application effect of this solution, this embodiment has done a lot of research and experiments to verify the improvement of compressor noise and performance. The following embodiment will specifically illustrate the compressor and its corresponding research and experimental results. Figure 2 The changes of compressor noise and performance with different ratios of crankshaft diameter to compression system radial are given. Figure 3 The variation of compressor noise and performance with different ratios of crankshaft diameter to compression system axial length is given. Among them, performance (COP) refers to the cooling capacity / power consumed by the compressor.

[0042] Through research and test results, it can be seen that as the radial ratio of the crankshaft 20 diameter to the compression system increases, the noise shows a trend of first decreasing to the lowest point and then continuing to rise, and the noise level is better when the ratio is 0.03-0.05; COP first slowly rises to the highest point and then drops sharply. The axial ratio of the crankshaft 20 diameter to the compression system also shows the same trend of change. As the axial and radial ratios of the crankshaft 20 diameter to the compression system increase, the stiffness of the crankshaft 20 also increases, and the reliability of the compressor is effectively improved.

[0043] It should be noted that the inner diameter of the shell 10 of the test compressor is the same, the compressor displacement is also the same, and in order to ensure the accuracy of the test results, the working conditions during the test are set to be the same.

[0044] This solution has the following technical effects: by limiting the axial and radial ratios of the crankshaft diameter and the compression system, it solves the problem that the variable frequency compressor is greatly deteriorated due to the stress deformation of the shaft system at high speed, and the noise and vibration of the compressor cannot be solved by conventional means, thereby optimizing the noise experience; it reduces the friction power loss caused by the deflection of the crankshaft at high speed, and ensures the performance and reliability of the compressor.

[0045] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. For those skilled in the art, the present invention may have various modifications and variations. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention shall be included in the protection scope of the present invention.

Claims

1. A compressor, characterized in that: The invention comprises a housing (10), and a crankshaft (20), a roller (30), and a cylinder (40) arranged in the housing (10); the crankshaft (20) comprises a long shaft (21), an eccentric portion (22), and a short shaft (23) connected in sequence; the roller (30) is sleeved on the eccentric portion (22), and the roller (30) is located in a compression chamber of the cylinder (40); wherein the diameter of the long shaft (21) is d1, the diameter of the short shaft (23) is d2, the inner diameter of the housing (10) is D1, the inner diameter of the cylinder (40) is D2, and the outer diameter of the roller (30) is D3.

2. The compressor according to claim 1, characterized in that 3. The compressor according to claim 1, characterized in that The compressor further comprises an upper flange (50) and a lower flange (60), the long shaft (21) being inserted into the upper flange (50), and the short shaft (23) being inserted into the lower flange (60); wherein the axial dimension of the upper flange (50) is H1, the axial dimension of the cylinder (40) is H2, and the axial dimension of the lower flange (60) is H3.

4. The compressor according to claim 3, characterized in that 5. The compressor according to claim 1, characterized in that The diameters of the major axis (21) and the minor axis (23) are equal.

6. The compressor according to claim 1, characterized in that The eccentric portion (22), the roller (30) and the cylinder (40) are all multiple, and the multiple eccentric portions (22) and the multiple rollers (30) are arranged in a one-to-one correspondence, and the multiple rollers (30) and the multiple cylinders (40) are arranged in a one-to-one correspondence.

7. The compressor according to claim 1, characterized in that The compressor further comprises a stator (70) and a rotor (80), wherein the stator (70) is arranged in the housing (10), the rotor (80) is arranged in the stator (70), and the rotor (80) is connected to the long shaft (21).

8. An air conditioner, characterized in that: The air conditioner comprises the compressor according to any one of claims 1 to 7.

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