Rotary compressor

Abstract

In the rotary compressor provided by the present invention, by controlling the volume and outer diameter size of the stator, the ratio of the eccentricity of the crankshaft to the outer diameter size of the stator, and the ratio of the height of the vane to the outer diameter size of the stator, the rotary compressor can reduce its size and weight while maintaining its refrigerating capacity, thus meeting the requirement of miniaturization.

Description

Technical Field

[0001] The present application relates to a compressor, and particularly to a rotary compressor. Background Art

[0002] Generally, a compressor converts electrical energy into kinetic energy and uses the kinetic energy to compress the refrigerant. According to the way of compressing the refrigerant, compressors can be divided into various types such as rotary compressors, scroll compressors, and reciprocal compressors.

[0003] In the development process of rotary compressors, miniaturization is a trend. However, compressors with a small shell diameter cannot reach the same level as those with a large shell diameter in terms of refrigeration capacity and COP (Coefficient of Performance) indicators. Therefore, high-power rotary compressors are generally developed with a large shell diameter. For example, the rotary fixed-speed compressor widely used in 5HP heat pump heating units and commercial heat pump water heater systems uses R410A as the refrigerant, has a displacement between 50.0 cc and 59.0 cc, and the outer diameter of the stator exceeds 150 mm. As is well known, the larger the outer diameter of the stator, the larger the volume and weight of the compressor, and correspondingly, the higher the manufacturing cost of the compressor. Currently, high-power rotary compressors generally have the problems of excessive volume and weight and too high manufacturing cost, and cannot meet the requirements of miniaturization.

[0004] Based on this, how to solve the problems of excessive volume and weight of existing high-power rotary compressors and inability to meet the requirements of miniaturization has become a technical problem that needs to be urgently solved by those skilled in the art. Summary of the Invention

[0005] Aiming at the defects in the prior art, the purpose of the present invention is to provide a rotary compressor, which overcomes the difficulties of the prior art, can effectively reduce the size and weight of the fixed-speed compressor while ensuring the refrigeration capacity, realizes the requirements of miniaturization, and greatly reduces the manufacturing cost of the compressor.

[0006] According to one aspect of the present invention, there is provided a rotary compressor, comprising: a motor assembly, a compression assembly, and a crankshaft;

[0007] The motor assembly includes a stator and a rotor, and the rotor is rotatably disposed within the stator;

[0008] The compression assembly includes a first cylinder and a second cylinder, and pistons and vanes are disposed within both the first cylinder and the second cylinder;

[0009] One end of the crankshaft is connected to the rotor of the motor assembly, and the other end of the crankshaft extends into the first cylinder and the second cylinder and is connected to the piston.

[0010] Among them, the displacement of the rotary compressor is between 50.0 cc and 59.0 cc, and the volume of the stator is between 110 cm 3 and 160 cm 3 and the outer diameter dimension of the stator is between 130 mm and 145 mm.

[0011] Optionally, the ratio of the eccentricity of the crankshaft to the outer diameter dimension of the stator is between 0.023 and 0.051, and the ratio of the height of the vane to the outer diameter dimension of the stator is between 0.15 and 0.269.

[0012] Optionally, in the rotary compressor, the outer diameter dimension of the stator is between 132 mm and 141 mm.

[0013] Optionally, in the rotary compressor, the outer diameter dimension of the stator is 132.3 mm, 135.0 mm or 140.1 mm.

[0014] Optionally, in the rotary compressor, the ratio of the eccentricity of the crankshaft to the outer diameter dimension of the stator is between 0.029 and 0.047.

[0015] Optionally, in the rotary compressor, the ratio of the eccentricity of the crankshaft to the outer diameter dimension of the stator is 0.029, 0.035 or 0.042.

[0016] Optionally, in the rotary compressor, the ratio of the height of the vane to the outer diameter dimension of the stator is between 0.19 and 0.263.

[0017] Optionally, in the rotary compressor, the ratio of the height of the vane to the outer diameter dimension of the stator is 0.19, 0.227 or 0.25.

[0018] Optionally, in the rotary compressor, the volume of the stator is between 110 cm 3 and 150 cm 3 between.

[0019] Optionally, in the rotary compressor, the rotary compressor has three feet, and the three feet are evenly spaced.

[0020] In the rotary compressor provided by the present invention, by controlling the volume and outer diameter size of the stator, the ratio of the eccentricity of the crankshaft to the outer diameter size of the stator, and the ratio of the height of the vane to the outer diameter size of the stator, the rotary compressor can maintain its refrigeration capacity while reducing its size and weight, thereby meeting the requirement of miniaturization. Description of the Drawings

[0021] The technical solutions of the present invention will be described in detail below in conjunction with the drawings and specific embodiments, so that the characteristics and advantages of the present invention will be more obvious.

[0022] Figure 1 Cross-sectional view of the rotary compressor according to an embodiment of the present invention;

[0023] Figure 2 Schematic structural diagram of the crankshaft according to an embodiment of the present invention;

[0024] Figure 3 Schematic structural diagram of the eccentric part of the crankshaft according to an embodiment of the present invention;

[0025] Figure 4 Graph showing the relationship between the motor efficiency of the rotary compressor according to an embodiment of the present invention and the volume of the stator;

[0026] Figure 5 Graph showing the relationship between the coefficient of performance of the rotary compressor according to an embodiment of the present invention and the ratio of the height of the vane to the outer diameter size of the stator;

[0027] Figure 6 Graph showing the relationship between the coefficient of performance of the rotary compressor according to an embodiment of the present invention and the ratio of the eccentricity of the crankshaft to the outer diameter size of the stator. Detailed Description of the Embodiments

[0028] The embodiments of the present invention will be described in detail below. Although the present invention will be described and explained in conjunction with some specific embodiments, it should be noted that the present invention is not limited to these embodiments. On the contrary, any modifications or equivalent substitutions made to the present invention should be covered within the scope of the claims of the present invention.

[0029] In addition, in order to better illustrate the present invention, numerous specific details are given in the following detailed description of the embodiments. Those skilled in the art will understand that the present invention can be implemented without these specific details. In other instances, well-known structures and components are not described in detail in order to highlight the gist of the present invention.

[0030] The technical solutions of the present invention will be described in detail below in conjunction with the drawings and specific embodiments, so that the characteristics and advantages of the present invention will be more obvious.

[0031] Please refer to Figure 1 , which is a sectional view of a rotary compressor according to an embodiment of the present invention. As Figure 1 shown, the rotary compressor 100 includes: a motor assembly 10, a compression assembly 20, and a crankshaft 30; the motor assembly 10 includes a stator 11 and a rotor 12, and the rotor 12 is rotatably disposed within the stator 11; the compression assembly 20 includes a first cylinder 21 and a second cylinder 22, and pistons and vanes are disposed within both the first cylinder 21 and the second cylinder 22; one end of the crankshaft 30 is connected to the rotor 12 of the motor assembly 10, and the other end of the crankshaft 30 extends into the first cylinder 21 and the second cylinder 22 and is connected to the piston; wherein, the displacement of the rotary compressor 100 is between 50.0 cc and 59.0 cc, and the volume of the stator 11 is between 110 cm 3 and 160 cm 3 , and the outer diameter dimension of the stator 11 is between 130 mm and 145 mm.

[0032] Specifically, the rotary compressor 100 includes a motor assembly 10, a compression assembly 20, a crankshaft 30, a housing 4, an upper housing cover 5, a lower housing cover 6, a liquid reservoir assembly 7, an intake pipe 8, and an exhaust pipe 9. Among them, the housing 4 is cylindrical, the upper housing cover 1 and the lower housing cover 6 are respectively fixed to the upper and lower ends of the housing 4, the exhaust pipe 9 is provided on the upper housing cover 1, the liquid reservoir assembly 7 is disposed outside the housing 4 and is connected to the housing 4, and the intake pipe 8 is provided on the liquid reservoir assembly 7. The motor assembly 10, the compression assembly 20, and the crankshaft 30 are all accommodated inside the housing 4.

[0033] Among them, the motor assembly 10 includes a stator 11 and a rotor 12, the stator 11 is fixed to the inner wall of the housing 4, and the rotor 12 is rotatably disposed within the stator 11. The crankshaft 30 is connected to the rotor 12 and rotates under the drive of the rotor 12.

[0034] The calculation formula for the volume V of the stator 11 is:

[0035]

[0036] Among them, D1 is the outer diameter dimension of the stator 11, D2 is the inner diameter dimension of the stator 11, and H is the height of the stator 11.

[0037] The compression assembly 20 adopts a double-cylinder design, and the two cylinders are arranged up and down and pistons and vanes are arranged within both cylinders. As Figure 1As shown, the compression assembly 20 includes a first cylinder 21 and a second cylinder 22. An intermediate partition 23 is provided between the first cylinder 21 and the second cylinder 22. A first piston (omitted in the figure) is provided in the first cylinder 21, and a second piston (omitted in the figure) is provided in the second cylinder 22. A crescent-shaped space is formed between the first piston and the inner wall of the first cylinder 21, and between the second piston and the inner wall of the second cylinder 22. Both ends of the crescent-shaped space are closed to form the working chamber of the compressor. First blades and second blades (omitted in the figure) are respectively provided in the blade grooves (omitted in the figure) of the first cylinder 21 and the second cylinder 22.

[0038] Wherein, one end of the first blade contacts the outer surface of the first piston, and the other end of the first blade contacts the inner wall of the first cylinder 21 through a spring. The first blade divides the crescent-shaped space formed by the first cylinder 21 and the first piston into a suction chamber and a compression chamber. One end of the second blade contacts the outer surface of the second piston, and the other end of the second blade contacts the inner wall of the second cylinder 22 through a spring. The second blade divides the crescent-shaped space formed by the second cylinder 22 and the second piston into a suction chamber and a compression chamber.

[0039] In this embodiment, the shapes and sizes of the first piston and the second piston are the same, and the shapes and sizes of the first blade and the second blade are the same. Among them, the heights of the first blade and the second blade are both h.

[0040] Preferably, the displacements (i.e., exhaust volumes) of the first cylinder 21 and the second cylinder 22 are the same. In this way, the operation of the rotary compressor 100 is more stable.

[0041] Please refer to Figures 1 to 3 , the crankshaft 30 extends along the axial direction of the housing 4. The crankshaft 30 includes a long shaft 31, a short shaft 32, and an eccentric portion 33 provided between the long shaft 31 and the short shaft 32. The long shaft 31 is used to connect with the rotor 12 of the motor assembly 10. The eccentric portion 33 extends into the first cylinder 21 and the second cylinder 22. The first piston in the first cylinder 21 and the second piston in the second cylinder 22 are respectively sleeved on the eccentric portion 33 of the crankshaft 30. Among them, the central axes of the long shaft 31 and the short shaft 32 coincide, and this central axis is defined as the central axis of the crankshaft 30. The central axis of the crankshaft 30 coincides with the central axes of the first cylinder 21 and the second cylinder 22. The distance between the central axis of the eccentric portion 33 and the central axis of the crankshaft 30 is defined as the eccentricity e of the crankshaft 30.

[0042] When the motor assembly 10 is powered on, the rotor 12 rotates relative to the stator 11, and then drives the crankshaft 30 to transmit the rotational force of the motor assembly 10 to the first piston and the second piston. The first piston and the second piston respectively perform eccentric rotational motions in the first cylinder 21 and the second cylinder 22, so that the volumes of the compression chambers of the first cylinder 21 and the second cylinder 22 are continuously reduced, and the volumes of the suction chambers are continuously increased, thereby realizing a continuous suction and compression process.

[0043] In this embodiment, the rotary compressor 100 is a constant-speed compressor (with a fixed operating speed and power). The displacement of the constant-speed compressor is between 50.0 cc and 59.0 cc, and the refrigerant used is R410A.

[0044] As is well known, the coefficient of performance of a compressor is mainly related to the pump efficiency and the motor efficiency. The higher the pump efficiency and the motor efficiency, the higher the coefficient of performance of the compressor. Conversely, the lower the pump efficiency and the motor efficiency, the lower the coefficient of performance of the compressor.

[0045] For a compressor with a certain displacement, the required output power is fixed. If the volume of the stator is too large, it will lead to an excessive output power, resulting in material waste. If the volume of the stator is too small, it will cause a large amount of heat generation in the motor, low motor efficiency, and inability to meet the design requirements. Therefore, high-power compressors generally adopt a large shell diameter design, and low-power compressors generally adopt a small shell diameter design. However, compressors with a large shell diameter design generally have problems of excessive volume and weight. The larger the volume and weight of the compressor, the higher the manufacturing cost.

[0046] The applicant has found through years of research that when the output power of the motor is fixed, the motor efficiency and the volume of the stator are basically in a positive relationship, that is, the larger the volume of the stator, the higher the motor efficiency. However, when the volume of the stator reaches a certain value, the increase in motor efficiency will tend to be slow. If the same motor efficiency needs to be improved, the volume of the stator needs to increase exponentially. In order to ensure that both the coefficient of performance and the weight of the compressor are within the preferred range, it is necessary to control the volume of the stator.

[0047] It has been experimentally verified that for a constant-speed compressor with a displacement of 50.0 cc to 59.0 cc and using R410A as the refrigerant, when the volume of the stator is less than 110 cm 3 the decrease in motor efficiency is very obvious and cannot meet the design requirements. When the volume of the stator is greater than 160 cm 3 the motor efficiency tends to be stable. If the volume of the stator continues to increase, the increase in motor efficiency is very small, but the weight of the compressor will increase sharply.

[0048] In this embodiment, the volume V of the stator 11 is between 110 cm 3 and 160 cm3 Between. Further, the volume V of the stator 11 is between 110 cm 3 and 150 cm 3 Between. For example, the volume V of the stator 11 is 117.5 cm 3 , 143.5 cm 3 or 150 cm 3 .

[0049] Please refer to Figure 4 , which is a graph showing the relationship between the motor efficiency of the rotary compressor according to the embodiment of the present invention and the volume of the stator. As Figure 4 shown, the horizontal axis is the volume V of the stator, and the vertical axis is the motor efficiency E of the rotary compressor. By taking the volume V of the stator as a parameter and varying it, it can be found that the motor efficiency E increases as the volume V of the stator increases. The larger the volume V of the stator, the slower the motor efficiency E rises. When the volume V of the stator is between 110 cm 3 and 160 cm 3 , the motor efficiency E is in a relatively preferred range. When the volume V of the stator is between 110 cm 3 and 150 cm 3 , the motor efficiency E is in a more preferred range.

[0050] As Figure 4 shown, when the volume V of the stator is 117.5 cm 3 , the motor efficiency E is relatively low, but the weight of the compressor is relatively light at this time; when the volume V of the stator is 143.5 cm 3 , the motor efficiency E is at an intermediate value, and both the motor efficiency E and the weight of the compressor are at an intermediate level; when the volume V of the stator is 150 cm 3 , the motor efficiency E is relatively high, but the weight of the compressor is relatively heavy at this time.

[0051] Further, the applicant found that the outer diameter dimension D1 of the stator not only affects the volume V of the stator, but also affects the size of the pump body compression structure, and thus affects the weight of the compressor. Generally, the larger the outer diameter dimension D1 of the stator, the larger the pump body compression structure, and the heavier the weight of the compressor. Conversely, the smaller the outer diameter dimension D1 of the stator, the smaller the pump body compression structure, and the lighter the weight of the compressor.

[0052] The applicant considered that the outer diameter dimension of the stator would affect the motor efficiency and weight of the compressor. Therefore, on the premise that the volume V of the stator remains unchanged, the outer diameter dimension D1 of the stator 11 was controlled.

[0053] In this embodiment, the outer diameter dimension D1 of the stator 11 is between 130 mm and 145 mm. Preferably, the outer diameter dimension D1 of the stator is between 132 mm and 141 mm. For example, the outer diameter dimension D1 of the stator 11 is 132.3 mm, 135.0 mm or 140.1 mm.

[0054] Verified by experiments: when the outer diameter dimension D1 of the stator 11 is between 130 mm and 145 mm, the coefficient of performance COP of the compressor is relatively high, and at the same time, the weight W of the compressor is relatively low; when the outer diameter dimension D1 of the stator is greater than 145 mm, the weight W starts to increase sharply, while the increase in the coefficient of performance COP is not obvious; when the outer diameter dimension D1 of the stator is less than 130 mm, the coefficient of performance COP drops rapidly and cannot meet the displacement requirements (between 50.0 cc and 59.0 cc).

[0055] In summary, when the outer diameter dimension D1 of the stator is greater than 145 mm or the outer diameter dimension D1 of the stator is less than 130 mm, the requirements of high power and small shell diameter cannot be met simultaneously. When the outer diameter dimension D1 of the stator is less than 145 mm and greater than 130 mm, the requirements of high power and small shell diameter can be met simultaneously. In particular, when the outer diameter dimension D1 of the stator is between 132 mm and 141 mm, both the coefficient of performance and the weight of the compressor are in a better range.

[0056] In addition, the outer diameter dimension D1 of the stator also affects the pump efficiency of the compressor. The pump efficiency of the compressor is mainly determined by the volumetric efficiency and mechanical efficiency of the pump body. Among them, the mechanical efficiency is mainly affected by the frictional losses caused by the friction pairs, including the frictional losses between the outer surface of the piston and the end of the vane, between the inner surface of the piston and the outer surface of the crankshaft, and between the side surface of the vane and the vane groove. The larger the outer diameter dimension D1 of the stator, the larger the pump compression structure, and correspondingly, the larger the contact area of the friction pairs. Therefore, the leakage is less and the volumetric efficiency is higher. However, at the same time, the increase in the contact area of the friction pairs will increase the frictional losses, thereby reducing the mechanical efficiency; vice versa.

[0057] Therefore, by reasonably designing the ratios of h / D1 and e / D1, the present invention further reduces the mechanical friction loss on the basis of reducing the mechanical friction loss of a small shell diameter, improves the mechanical efficiency, and thus makes up for the deficiency of the volumetric efficiency when the shell diameter is small. In this way, even if the outer diameter of the stator is reduced, the pump efficiency of the compressor can reach the same level as that of a large outer diameter, and the performance coefficient of the whole compressor will not fluctuate greatly. When the ratio of the height h of the vane to the outer diameter D1 of the stator 11 (h / D1) and the ratio of the eccentricity e of the crankshaft to the outer diameter D1 of the stator 11 (e / D1) are too large, the forces on the outer surface of the piston and the end of the sliding vane are very large. At the same time, due to the excessive height of the sliding vane, the lubrication effect of this friction pair is poor, thereby increasing the friction loss. When the ratio of the height h of the vane to the outer diameter D1 of the stator 11 (h / D1) and the ratio of the eccentricity e of the crankshaft to the outer diameter D1 of the stator 11 (e / D1) are too small, although the force and contact area of the friction pair are reduced, and the friction loss is reduced, but the resulting increase in the piston thickness and the increase in the inner diameter of the cylinder are not conducive to the improvement of the volumetric efficiency.

[0058] Based on this, the applicant reasonably controls h / D1 and e / D1 respectively to effectively reduce the friction loss and improve the mechanical efficiency, thereby making up for the deficiency of the volumetric efficiency. In this way, even if the outer diameter D1 of the stator is reduced to 130 mm - 145 mm, the pump efficiency of the compressor can reach the original level (i.e., the level when the outer diameter is not reduced, such as 150 mm - 165 mm), thereby ensuring that the performance coefficient of the compressor can maintain the original level.

[0059] In this embodiment, the ratio of the height h of the vane to the outer diameter D1 of the stator 11 (h / D1) is between 0.15 and 0.269, and the ratio of the eccentricity e of the crankshaft 30 to the outer diameter D1 of the stator 11 (e / D1) is between 0.023 and 0.051.

[0060] Further, the ratio of the height h of the vane to the outer diameter D1 of the stator 11 (h / D1) is between 0.19 and 0.263, and the ratio of the eccentricity e of the crankshaft 30 to the outer diameter D1 of the stator 11 (e / D1) is between 0.029 and 0.047. For example, the ratio of the height h of the vane to the outer diameter D1 of the stator 11 (h / D1) is 0.19, 0.227 or 0.25, and the ratio of the eccentricity e of the crankshaft 30 to the outer diameter D1 of the stator 11 (e / D1) is 0.029, 0.035 or 0.042.

[0061] Please refer to Figure 5 and Figure 6 , Figure 5 which is the relationship diagram of the performance coefficient of the rotary compressor according to the embodiment of the present invention changing with the ratio of the height of the vane to the outer diameter of the stator, Figure 6This is a graph showing the relationship between the coefficient of performance of the rotary compressor according to the embodiments of the present invention and the ratio of the eccentricity of the crankshaft to the outer diameter dimension of the stator. As Figure 5 and Figure 6 shown, the ratio of the height h of the vane to the outer diameter dimension D1 of the stator 11 (h / D1) and the ratio of the eccentricity e of the crankshaft to the outer diameter dimension D1 of the stator 11 (e / D1) and the coefficient of performance of the compressor are roughly in a parabolic trend. When 0.15 < h / D1 < 0.269 and 0.023 < e / D1 < 0.051, the coefficient of performance of the compressor is in the optimal range. When h / D1 is greater than 0.269 or e / D1 is greater than 0.047, the coefficient of performance of the compressor decreases significantly.

[0062] It should be noted that the coefficient of performance of the rotary compressor is jointly determined by h / D1 and e / D1. Figure 5 and Figure 6 The coefficient of performance curves are the same curve. When e / D1 is greater than 0.047 or h / D1 is greater than 0.269, the frictional losses are relatively large, resulting in a reduction in the performance of the compressor. When 0.15 < h / D1 < 0.269 and 0.023 < e / D1 < 0.051, the frictional losses are relatively small, so the performance of the compressor is relatively good.

[0063] It should be noted that in the field of compressor technology, there are many component structures and complex structural parameters. Without a large number of experiments, it is impossible to predict the feasibility of the technical solution, nor can the technical effects of the technical solution be anticipated. The selection of technical parameters is crucial. Any slight change in parameters may bring completely different technical effects. The optimized technical parameters can only be determined through a large number of exploratory experiments and cannot be obtained through simple prediction.

[0064] In this embodiment, the rotary compressor 100 adopts a small shell diameter design, so it can effectively meet the requirements of small volume and light weight of the compressor. Comparing the rotary compressor 100 with a traditional fixed-speed compressor, it can be found that the refrigeration capacity of the rotary compressor 100 is the same as that of the traditional fixed-speed compressor, both being 1; the COP indexes of the rotary compressor 100 and the traditional fixed-speed compressor are basically the same, being 0.98 and 1 respectively; however, the weight of the rotary compressor 100 has decreased significantly, and the weight of the rotary compressor 100 is about 70% of that of the traditional fixed-speed compressor. See the following table for details:

[0065]

[0066]

[0067] It can be seen that the refrigeration capacity and COP index of the rotary compressor 100 are basically the same as those of a traditional 5HP constant-speed compressor. Compared with the traditional 5HP constant-speed compressor, the rotary compressor 100 is smaller in volume and lighter in weight. Thus, the cold-weight ratio of the rotary compressor 100 has been greatly improved.

[0068] For a compressor, the cold-weight ratio is one of the key performance indicators. The cold-weight ratio refers to the ratio of the rated refrigeration capacity of the compressor to its weight. In the process of researching and manufacturing compressors, it is necessary to maximize the refrigeration capacity while minimizing the size and weight of the compressor in order to improve the competitiveness of the product and obtain the best economic benefits.

[0069] At the same time, since the rotary compressor 100 is lighter in weight, a three-foot design can be adopted, and the three-foot design is sufficient to support the entire weight of the compressor. In this embodiment, the rotary compressor 100 includes three feet (not shown in the figure), and the three feet are evenly spaced and fixedly connected to the bottom of the lower housing cover 6 by welding.

[0070] In summary, by controlling the volume and outer diameter size of the stator, the ratio of the eccentricity of the crankshaft to the outer diameter size of the stator, and the ratio of the height of the vane to the outer diameter size of the stator, the rotary compressor of the present invention can maintain its refrigeration capacity while reducing its size and weight, thereby meeting the requirements of miniaturization.

[0071] The above content is a further detailed description of the present application in combination with specific preferred embodiments, and it cannot be determined that the specific implementation of the present application is only limited to these descriptions. For those of ordinary skill in the technical field to which the present application belongs, without departing from the concept of the present application, several simple deductions or substitutions can still be made, and all should be regarded as belonging to the protection scope of the present application.

Claims

1. A rotary compressor, characterized in that, comprising: a motor assembly, a compression assembly and a crankshaft; the motor assembly includes a stator and a rotor, and the rotor is rotatably arranged inside the stator; the compression assembly includes a first cylinder and a second cylinder, and pistons and vanes are arranged inside both the first cylinder and the second cylinder; one end of the crankshaft is connected to the rotor of the motor assembly, and the other end of the crankshaft extends into the first cylinder and the second cylinder and is connected to the pistons; Among them, the displacement of the rotary compressor is between 50.0 cc and 59.0 cc, and the volume of the stator is between 110 cm 3 and 160 cm 3 . The outer diameter dimension of the stator is between 130 mm and 145 mm, and the ratio of the eccentricity of the crankshaft to the outer diameter dimension of the stator is between 0.023 and 0.

051.

2. The rotary compressor according to claim 1, characterized in that, the ratio of the height of the vane to the outer diameter dimension of the stator is between 0.15 and 0.

269.

3. The rotary compressor according to claim 1 or 2, characterized in that, the outer diameter dimension of the stator is between 132 mm and 141 mm.

4. The rotary compressor according to claim 3, characterized in that, the outer diameter dimension of the stator is 132.3 mm, 135.0 mm or 140.1 mm.

5. The rotary compressor according to claim 2, characterized in that, the ratio of the eccentricity of the crankshaft to the outer diameter dimension of the stator is between 0.029 and 0.

047.

6. The rotary compressor according to claim 5, characterized in that, the ratio of the eccentricity of the crankshaft to the outer diameter dimension of the stator is 0.029, 0.035 or 0.

042.

7. The rotary compressor according to claim 2, characterized in that, the ratio of the height of the vane to the outer diameter dimension of the stator is between 0.19 and 0.

263.

8. The rotary compressor according to claim 7, characterized in that, the ratio of the height of the vane to the outer diameter dimension of the stator is 0.19, 0.227 or 0.

25.

9. The rotary compressor according to claim 1 or 2, characterized in that, The volume of the stator is between 110 cm 3 and 150 cm 3 .

10. The rotary compressor according to claim 1, characterized in that, the rotary compressor has three feet, and the three feet are evenly spaced.

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