Rotary compressor and refrigeration equipment with same

Abstract

The utility model discloses a rotary compressor and refrigeration equipment with the rotary compressor, the rotary compressor comprises a plurality of cylinders, each cylinder is provided with a compression cavity and an air inlet channel communicated with the compression cavity; and the partition plates are arranged between the adjacent air cylinders, each partition plate is provided with a first buffer space, and at least one air inlet channel is communicated with the adjacent first buffer space. According to the rotary compressor, through the first buffer space on the partition plate, backflow gas can be contained, the gas backflow path is shortened, the flow loss of the gas is reduced, the unit suction capacity can be increased, the energy efficiency of the rotary compressor is effectively improved, and the refrigerating capacity of the rotary compressor is increased.

Description

Technical Field

[0001] The utility model relates to the technical field of compressors, in particular to a rotary compressor and a refrigeration device having the same. Background Art

[0002] The rotary compressor includes a compression component, which includes a compression chamber, an air inlet channel and an exhaust channel. A rotatable piston is provided in the compression chamber. When the rotary compressor is working, the piston rotates in the compression chamber to compress the gas in the compression chamber.

[0003] As the piston rotates, it periodically blocks the intake channel. When the piston avoids the intake channel, the gas in the intake channel enters the compression chamber. When the piston blocks the intake channel, the gas in the intake channel will flow back, resulting in a large gas flow loss, which affects the cooling capacity of the compressor. Utility Model Content

[0004] The utility model aims to solve at least one of the technical problems existing in the prior art. To this end, the utility model proposes a rotary compressor, which can accommodate the refluxed gas through the first buffer space on the partition, shorten the path of gas reflux, reduce the flow loss of gas, and increase the unit suction volume, thereby effectively improving the energy efficiency of the rotary compressor and increasing the refrigeration capacity of the rotary compressor.

[0005] The utility model also provides a refrigeration device comprising the rotary compressor.

[0006] According to the rotary compressor of the embodiment of the utility model, it includes: a plurality of cylinders, each of which is provided with a compression chamber and an air intake passage connected to the compression chamber; a partition plate, the partition plate is provided between adjacent cylinders, the partition plate is provided with a first buffer space, and at least one of the air intake passages is connected to the adjacent first buffer space.

[0007] According to the rotary compressor of the embodiment of the utility model, the gas is compressed by multiple cylinders, thereby increasing the refrigeration efficiency of the rotary compressor. A partition is provided between adjacent cylinders, and the partition is provided with a first buffer space. The first buffer space can accommodate the refluxed gas, shorten the path of the gas reflux, effectively reduce the flow loss of the gas, and increase the refrigeration capacity of the rotary compressor. In addition, the first buffer space can also increase the unit air intake volume of the cylinder, effectively improve the energy efficiency of the rotary compressor, and further increase the refrigeration capacity of the rotary compressor.

[0008] In some embodiments, the air inlet channels on both sides of the partition are connected to the first buffer space on the partition.

[0009] In some embodiments, the cylinder is provided with a first flow guiding channel, and the intake channel communicates with the first buffer space through the first flow guiding channel.

[0010] In some embodiments, there is an included angle A between the extending direction of the first flow guiding channel and the extending direction of the intake channel, and A satisfies: 45° ≤ A ≤ 90°.

[0011] In some embodiments, A further satisfies: 45° ≤ A ≤ 70°.

[0012] In some embodiments, the diameter of the first flow guiding channel is d, and the diameter of the intake channel is D, and d / D satisfies: 0.08 ≤ d / D ≤ 0.35.

[0013] In some embodiments, the value range of the diameter d of the first flow guiding channel is 1 mm ≤ d ≤ 4 mm.

[0014] In some embodiments, the rotary compressor further includes: a main bearing and a sub-bearing, the main bearing and the sub-bearing are arranged on both sides of the plurality of cylinders, and a second buffer space is formed between at least one of the main bearing and the sub-bearing and the adjacent cylinder, and the second buffer space communicates with the adjacent intake channel.

[0015] In some embodiments, the total volume of the first buffer space and the second buffer space is Vc, the displacement of the rotary compressor is Ve, and Vc / Ve satisfies: Vc / Ve ≥ 0.15.

[0016] The refrigeration device according to the embodiment of the present invention includes: the rotary compressor described in the above technical solution.

[0017] The additional aspects and advantages of the present invention will be partially given in the following description, partially become obvious from the following description, or be understood through the practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] The above and / or additional aspects and advantages of the present invention will become obvious and easy to understand from the description of the embodiments in conjunction with the following drawings, in which:

[0019] Figure 1 is a schematic diagram of a rotary compressor according to an embodiment of the present invention;

[0020] Figure 2 is a schematic diagram of a compression component according to some embodiments of the present invention;

[0021] Figure 3 is a schematic diagram of a partition according to some embodiments of the present invention;

[0022] Figure 4 Schematic diagram of a compression component according to some other embodiments of the present utility model;

[0023] Figure 5 Schematic diagram of a compression component according to still some other embodiments of the present utility model;

[0024] Figure 6 Schematic diagram of a main bearing according to some embodiments of the present utility model;

[0025] Figure 7 Schematic diagram of an electric motor according to some embodiments of the present utility model.

[0026] Reference numerals:

[0027] 100, rotary compressor; 1, housing; 2, electric motor; 21, stator; 211, stator core; 212, stator slot; 22, rotor; 221, rotor core; 222, permanent magnet; 3, compression component; 31, cylinder; 311, compression chamber; 312, intake passage; 313, first diversion passage; 314, first cylinder; 315, second cylinder; 316, second diversion passage; 32, partition; 321, first buffer space; 33, piston; 34, crankshaft; 35, main bearing; 36, auxiliary bearing; 37, second buffer space. Detailed description of the embodiments

[0028] The embodiments of the present utility model will be described in detail below. The examples of the embodiments are shown in the drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below by referring to the drawings are exemplary and are only used to explain the present utility model, and should not be construed as a limitation of the present utility model.

[0029] In the description of the present utility model, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc. indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, and are only for the convenience of describing the present utility model and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus should not be construed as a limitation of the present utility model. In addition, the features defined as "first" and "second" may explicitly or implicitly include one or more of such features. In the description of the present utility model, unless otherwise specified, the meaning of "a plurality" is two or more.

[0030] In the description of the present invention, it should be noted that, unless otherwise clearly specified and limited, the terms "installation", "connection" and "connection" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection, or it can be indirectly connected through an intermediate medium, or it can be the internal communication of two components. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0031] Reference below Figures 1-7 A rotary compressor 100 according to an embodiment of the present invention is described.

[0032] Reference Figure 1 , Figure 2 and Figure 3 According to the rotary compressor 100 of the embodiment of the utility model, the rotary compressor 100 comprises: a housing 1, a motor 2 and a compression component 3, wherein the motor 2 and the compression component 3 are both located in the housing 1, and the motor 2 is connected to the compression component 3 to drive the compression component 3 to compress gas. The compression component 3 comprises a plurality of cylinders 31, each cylinder 31 is provided with a compression chamber 311, an intake passage 312 and an exhaust passage, and the intake passage 312 and the exhaust passage are both connected to the compression chamber 311.

[0033] The compression component 3 also includes a partition 32, and a partition 32 is provided between adjacent cylinders 31. The partition 32 separates adjacent cylinders 31 so that each cylinder 31 can compress gas independently, avoiding mutual influence of gases in different compression chambers 311, thereby improving the compression efficiency of the compression component 3.

[0034] Each compression chamber 311 is provided with a piston 33 connected to the motor 2. The motor 2 is suitable for driving the piston 33 to rotate eccentrically in the corresponding compression chamber 311 to compress the gas in the compression chamber 311. As the piston 33 rotates, the piston 33 periodically blocks the intake channel 312. When the piston 33 avoids the intake channel 312, the gas in the intake channel 312 can enter the compression chamber 311. When the piston 33 blocks the intake channel 312, the gas flowing in the intake channel 312 collides with the piston 33 and then flows back.

[0035] In the embodiment of the utility model, the partition plate 32 is provided with a first buffer space 321 , and at least one air inlet channel 312 is communicated with an adjacent first buffer space 321 .

[0036] When the rotary compressor 100 is working, the gas entering the rotary compressor 100 is divided into multiple intake channels 312. When the piston 33 avoids the intake channel 312, the gas in the intake channel 312 is sucked into the corresponding compression chamber 311. When the piston 33 blocks the intake channel 312, the gas flowing in the intake channel 312 collides with the piston 33 and then flows back. The gas in the intake channel 312 connected to the first buffer space 321 can flow back into the first buffer space 321, and the refluxed gas is temporarily stored in the first buffer space 321 to avoid The gas flows back to the outside of the rotary compressor 100, shortening the path of gas flow back and effectively reducing the flow loss of the gas. When the piston 33 avoids the intake channel 312 again, the gas in the intake channel 312 is sucked into the compression chamber 311, driving the gas in the first buffer space 321 to enter the compression chamber 311. The gas in the first buffer space 321 can increase the suction volume of the compression chamber 311, which plays a role in replenishing air, thereby increasing the unit suction volume, effectively improving the energy efficiency of the rotary compressor 100 and the refrigeration efficiency of the rotary compressor 100.

[0037] According to the rotary compressor 100 of the embodiment of the utility model, the gas is compressed by multiple cylinders 31, so that the refrigeration efficiency of the rotary compressor 100 is increased. A partition 32 is provided between adjacent cylinders 31, and the partition 32 is provided with a first buffer space 321. The first buffer space 321 can accommodate the refluxed gas, shorten the path of the gas reflux, effectively reduce the flow loss of the gas, and improve the refrigeration capacity of the rotary compressor 100. In addition, the first buffer space 321 can also increase the unit suction volume of the cylinder 31, effectively improve the energy efficiency of the rotary compressor 100, and further increase the refrigeration capacity of the rotary compressor 100.

[0038] In some specific embodiments, two cylinders 31 are provided and one partition plate 32 is provided. The double-cylinder compressor has a simpler structure, thereby reducing the cost of the rotary compressor 100 .

[0039] Reference Figure 4 In some embodiments, the air inlet channels 312 on both sides of the partition 32 are connected to the first buffer space 321 on the partition 32 .

[0040] That is to say, the gas in the air inlet channel 312 on both sides of the partition 32 can enter the first buffer space 321 when it refluxes, further reducing the flow path of the gas reflux, further reducing the flow loss of the gas, and effectively increasing the cooling capacity of the rotary compressor 100.

[0041] In some embodiments, the compression component 3 further includes a crankshaft 34 connected to the motor 2. The crankshaft 34 is provided with two eccentric parts, and the two eccentric parts are respectively arranged in two compression chambers 311. The eccentric parts are connected to the pistons 33 in the corresponding compression chambers 311.

[0042] When the rotary compressor 100 operates, the motor 2 drives the crankshaft 34 to rotate. The crankshaft 34 drives the two pistons 33 to rotate through the two eccentric parts so that the two cylinders 31 compress simultaneously.

[0043] In the circumferential direction of the crankshaft 34, the two eccentric parts are arranged in a staggered manner so that the two pistons 33 are arranged in a staggered manner, so that the time when the two pistons 33 block the intake passage 312 is staggered.

[0044] It can be seen from the above technical solutions that the gas reflux times in the two intake passages 312 are also staggered. The first buffer space 321 on the partition plate 32 can alternately accommodate the reflux gas in the two intake passages 312, effectively improving the utilization rate of the first buffer space 321 and effectively improving the refrigerating capacity of the rotary compressor 100.

[0045] Refer to Figure 3 and Figure 4 , in some specific embodiments, the first buffer space 321 is formed as a through hole on the partition plate 32.

[0046] In the embodiment of the present utility model, the structure of the first buffer space 321 is simple, easy to process, and reduces the cost of the rotary compressor 100.

[0047] The first buffer space 321 can be a round hole, a rectangular hole, a kidney-shaped hole or a through hole of other shapes. The present utility model does not limit the shape of the first buffer space 321.

[0048] Refer to Figure 2 , in some embodiments, the cylinder 31 is provided with a first diversion channel 313, and the intake passage 312 is communicated with the first buffer space 321 through the first diversion channel 313.

[0049] In the embodiment of the present utility model, when the gas in the intake passage 312 refluxes, it enters the first buffer space 321 through the first diversion channel 313. Under the diversion action of the first diversion channel 313, the smoothness of the gas entering the first buffer space 321 is improved, and the flow loss of the gas is further reduced.

[0050] And the internal space of the first diversion channel 313 can also be used to accommodate the reflux gas, increasing the accommodation space for the reflux gas, further reducing the flow loss of the gas, and improving the refrigerating capacity of the rotary compressor 100.

[0051] In some specific embodiments, the first diversion channel 313 is formed as a through hole in the cylinder 31. In the embodiments of the present utility model, the structure of the first diversion channel 313 is simple, reducing the processing difficulty of the cylinder 31 and the cost of the rotary compressor 100.

[0052] Referring to Figure 4 , in some embodiments, there is an included angle A between the extending direction of the first diversion channel 313 and the extending direction of the intake channel 312, and A satisfies: 45° ≤ A ≤ 90°.

[0053] If A is less than 45°, it will cause the gas far from the first diversion channel 313 in the intake channel 312 to be difficult to enter the first diversion channel 313, reducing the efficiency of the gas entering the first diversion channel 313; if A is greater than 90°, when the intake channel 312 is normally admitting gas, the gas is likely to enter the first buffer space 321, but it is difficult to enter the first buffer space 321 when the gas flows back, reducing the compression efficiency of the rotary compressor 100.

[0054] In the embodiments of the present utility model, the included angle A between the extending direction of the first diversion channel 313 and the extending direction of the intake channel 312 is limited to 45° ≤ A ≤ 90°, effectively improving the efficiency of the reflux gas entering the first buffer space 321 and further improving the refrigerating capacity of the rotary compressor 100.

[0055] In some specific embodiments, the included angle A between the extending direction of the first diversion channel 313 and the extending direction of the intake channel 312 can be any one of the point values of 45°, 47°, 53°, 60°, 70°, 80°, 90° or the range value between any two of them, effectively improving the efficiency of the reflux gas entering the first buffer space 321 and improving the refrigerating capacity of the rotary compressor 100.

[0056] In some embodiments, there is an included angle A between the extending direction of the first diversion channel 313 and the extending direction of the intake channel 312, and A satisfies: 45° ≤ A ≤ 70°.

[0057] The included angle A between the extending direction of the first diversion channel 313 and the extending direction of the intake channel 312 can be any one of the point values of 45°, 47°, 53°, 56°, 60°, 65°, 70° or the range value between any two of them, effectively improving the efficiency of the reflux gas entering the first buffer space 321 and improving the refrigerating capacity of the rotary compressor 100.

[0058] Referring to Figure 2 , in some embodiments, the diameter of the first diversion channel 313 is d, and the diameter of the intake channel 312 is D, and d / D satisfies: 0.08 ≤ d / D ≤ 0.35.

[0059] If d / D is less than 0.08, it will cause the diameter of the first diversion channel 313 to be too small, making it difficult to machine the first diversion channel 313, and the efficiency of the reflux gas passing through the first diversion channel 313 is too low. Most of the reflux gas is difficult to enter the first buffer space 321, reducing the utilization rate of the first buffer space 321, increasing the flow loss of the gas, and reducing the refrigerating capacity of the rotary compressor 100. If d / D is greater than 0.35, it will cause the diameter of the first diversion channel 313 to be too large, easily generating gas flow pulsation and making it easy for the compression component 3 to generate noise.

[0060] In the embodiment of the present utility model, d / D is limited to 0.08 ≤ d / D ≤ 0.35. d / D can be any point value among 0.08, 0.11, 0.15, 0.21, 0.26, 0.35 or the range value between any two of them. While improving the smoothness of the reflux gas entering the first buffer space 321, the noise of the compression component 3 is reduced.

[0061] In some embodiments, the value range of the diameter d of the first diversion channel 313 is 1 mm ≤ d ≤ 4 mm.

[0062] If d is less than 1 mm, that is, the diameter of the first diversion channel 313 is too small, it is not only difficult to machine the first diversion channel 313, but also causes the efficiency of the reflux gas passing through the first diversion channel 313 to be too low. Most of the reflux gas is difficult to enter the first buffer space 321, reducing the utilization rate of the first buffer space 321, increasing the flow loss of the gas, and reducing the refrigerating capacity of the rotary compressor 100. If d is greater than 4 mm, it will cause the diameter of the first diversion channel 313 to be too large, easily generating gas flow pulsation and making it easy for the compression component 3 to generate noise.

[0063] In the embodiment of the present utility model, d is limited to 1 mm ≤ d ≤ 4 mm. d can be any point value among 1 mm, 1.5 mm, 2 mm, 2.5 mm, 3 mm, 4 mm or the range value between any two of them. While improving the smoothness of the reflux gas entering the first buffer space 321, the noise of the compression component 3 is reduced.

[0064] Referring to Figure 4 and Figure 5 In some embodiments, the compression component 3 further includes: a main bearing 35 and a sub-bearing 36. The main bearing 35 and the sub-bearing 36 are arranged on both sides of a plurality of cylinders 31. At least one of the main bearing 35 and the sub-bearing 36 forms a second buffer space 37 with the adjacent cylinder 31, and the second buffer space 37 communicates with the adjacent intake channel 312.

[0065] When gas reflux occurs in the intake channel 312 adjacent to the second buffer space 37, the refluxed gas can enter the second buffer space 37, and the refluxed gas can be temporarily stored in the second buffer space 37 to prevent the gas from flowing back to the outside of the rotary compressor 100, shortening the gas reflux path and effectively reducing the flow loss of the gas. When the piston 33 avoids the intake channel 312 again, the gas in the intake channel 312 is sucked into the compression chamber 311, driving the gas in the second buffer space 37 to enter the compression chamber 311 together. The gas in the second buffer space 37 can increase the suction volume of the compression chamber 311, which plays a role in replenishing air, thereby increasing the unit suction volume, effectively improving the energy efficiency of the rotary compressor 100 and the refrigeration efficiency of the rotary compressor 100.

[0066] In the embodiment of the utility model, both the first buffer space 321 and the second buffer space 37 can be used to accommodate the refluxed gas, which effectively reduces the flow loss of the gas and improves the refrigeration efficiency of the rotary compressor 100.

[0067] It should be noted that, refer to Figure 6 In some embodiments, a receiving groove is provided on the main bearing 35 , and the receiving groove on the main bearing 35 is formed as a second buffer space 37 .

[0068] In other embodiments, a receiving groove is provided on the side of the cylinder 31 adjacent to the main bearing 35 facing the main bearing 35, and the receiving groove on the cylinder 31 forms a second buffer space 37; in still other embodiments, a first receiving groove is provided on the main bearing 35, and a second receiving groove is provided on the side of the cylinder 31 adjacent to the main bearing 35 facing the main bearing 35, and the first receiving groove is connected to the second receiving groove to form a second buffer space 37.

[0069] In some embodiments, a receiving groove is provided on the secondary bearing 36, and the receiving groove on the secondary bearing 36 forms a second buffer space 37; in other embodiments, a receiving groove is provided on the side of the cylinder 31 adjacent to the secondary bearing 36 facing the secondary bearing 36, and the receiving groove on the cylinder 31 forms the second buffer space 37; in still other embodiments, a first receiving groove is provided on the secondary bearing 36, and a second receiving groove is provided on the side of the cylinder 31 adjacent to the secondary bearing 36 facing the secondary bearing 36, and the first receiving groove is connected to the second receiving groove to form a second buffer space 37.

[0070] Reference Figure 5 In some specific embodiments, two cylinders 31 are provided, and the two cylinders 31 are respectively a first cylinder 314 and a second cylinder 315. In the first direction, the main bearing 35, the first cylinder 314, the partition 32, the second cylinder 315 and the auxiliary bearing 36 are arranged in sequence.

[0071] A second buffer space 37 is provided between the main bearing 35 and the first cylinder 314, and the second buffer space 37 communicates with the intake passage 312 of the first cylinder 314; a first buffer space 321 is provided on the partition 32, and the first buffer space 321 communicates with the intake passage 312 of the second cylinder 315.

[0072] In the embodiment of the present invention, when the gas in the intake passage 312 of the first cylinder 314 flows back, the gas enters the second buffer space 37; when the gas in the intake passage 312 of the second cylinder 315 flows back, the gas enters the first buffer space 321.

[0073] In the embodiment of the present invention, the first buffer space 321 and the second buffer space 37 act on different intake passages 312 respectively, avoiding the mutual influence of the gases in different intake passages 312, reducing gas turbulence, and improving the smoothness of gas flow.

[0074] Refer to Figure 5 In some further embodiments, the main bearing 35 is located above the first cylinder 314, and the auxiliary bearing 36 is located below the second cylinder 315.

[0075] In the embodiment of the present invention, the second buffer space 37 is located above the intake passage 312 of the first cylinder 314, and the first buffer space 321 is located above the intake passage 312 of the second cylinder 315. The lubricating oil entering the first buffer space 321 and the second buffer space 37 can be discharged under the action of gravity, avoiding the accumulation of oil in the first buffer space 321 and the second buffer space 37, and ensuring the reliability of the use of the first buffer space 321 and the second buffer space 37.

[0076] Refer to Figure 4 In still some other embodiments, there are two cylinders 31, which are the first cylinder 314 and the second cylinder 315 respectively. In the first direction, the main bearing 35, the first cylinder 314, the partition 32, the second cylinder 315, and the auxiliary bearing 36 are arranged in sequence.

[0077] A second buffer space 37 is provided between the main bearing 35 and the first cylinder 314, a second buffer space 37 is provided between the auxiliary bearing 36 and the second cylinder 315, and a first buffer space 321 is provided on the partition 32. The intake passage 312 of the first cylinder 314 communicates with the first buffer space 321 and the adjacent second buffer space 37 respectively, and the intake passage 312 of the second cylinder 315 communicates with the first buffer space 321 and the adjacent second buffer space 37 respectively.

[0078] In the embodiments of the present utility model, when the gas in the intake passage 312 of the first cylinder 314 flows back, part of the gas enters the adjacent second buffer space 37, and part of the gas enters the first buffer space 321, further reducing the gas flow-back path, reducing the gas flow loss, and improving the refrigeration efficiency of the rotary compressor 100; when the gas in the intake passage 312 of the second cylinder 315 flows back, part of the gas enters the adjacent second buffer space 37, and part of the gas enters the first buffer space 321, further reducing the gas flow-back path, reducing the gas flow loss, and improving the refrigeration efficiency of the rotary compressor 100.

[0079] Referring Figure 4 and Figure 5 , in some embodiments, the cylinder 31 is provided with a second diversion channel 316, and the intake passage 312 communicates with the second buffer space 37 through the second diversion channel 316.

[0080] In the embodiments of the present utility model, when the gas in the intake passage 312 flows back, at least part of the gas enters the second buffer space 37 through the second diversion channel 316. Under the diversion effect of the second diversion channel 316, the smoothness of the gas entering the second buffer space 37 is improved, and the gas flow loss is further reduced.

[0081] Moreover, the internal space of the second diversion channel 316 can also be used to accommodate the flowing-back gas, increasing the accommodation space for the flowing-back gas, further reducing the gas flow loss, and improving the refrigerating capacity of the rotary compressor 100.

[0082] In some specific embodiments, the second diversion channel 316 is formed as a through hole in the cylinder 31. In the embodiments of the present utility model, the structure of the second diversion channel 316 is simple, reducing the processing difficulty of the cylinder 31 and the cost of the rotary compressor 100.

[0083] Referring Figure 4 , in some embodiments, there is an included angle B between the extending direction of the second diversion channel 316 and the extending direction of the intake passage 312, and B satisfies: 45° ≤ B ≤ 90°.

[0084] If B is less than 45°, the efficiency of the gas entering the second diversion channel 316 will be reduced; if B is greater than 90°, when the gas normally enters the intake passage 312, the gas is likely to enter the second buffer space 37, but it is difficult for the gas to enter the second buffer space 37 when the gas flows back, reducing the compression efficiency of the rotary compressor 100.

[0085] In the embodiment of the present utility model, the angle B between the extending direction of the second diversion channel 316 and the extending direction of the intake channel 312 is limited to 45° ≤ B ≤ 90°, effectively improving the efficiency of the reflux gas entering the second buffer space 37 and further improving the refrigerating capacity of the rotary compressor 100.

[0086] In some specific embodiments, the angle B between the extending direction of the second diversion channel 316 and the extending direction of the intake channel 312 can be any one of the point values of 45°, 47°, 53°, 60°, 70°, 80°, 90° or the range value between any two of them, effectively improving the efficiency of the reflux gas entering the second buffer space 37 and improving the refrigerating capacity of the rotary compressor 100.

[0087] In some embodiments, there is an angle B between the extending direction of the second diversion channel 316 and the extending direction of the intake channel 312, and B satisfies: 45° ≤ B ≤ 70°.

[0088] The angle B between the extending direction of the second diversion channel 316 and the extending direction of the intake channel 312 can be any one of the point values of 45°, 47°, 53°, 56°, 60°, 65°, 70° or the range value between any two of them, effectively improving the efficiency of the reflux gas entering the second buffer space 37 and improving the refrigerating capacity of the rotary compressor 100.

[0089] It should be understood that the angle A and the angle B can be equal or not equal, and the present application does not limit this.

[0090] In some embodiments, the total volume of the first buffer space 321 and the second buffer space 37 is Vc, and the displacement of the rotary compressor 100 is Ve. Vc / Ve satisfies: Vc / Ve ≥ 0.15.

[0091] If the ratio of Vc / Ve is too small, the total volume of the first buffer space 321 and the second buffer space 37 will be too small, and the first buffer space 321 and the second buffer space 37 can accommodate less reflux gas. The effect of improving the cooling capacity of the rotary compressor 100 is weak, and it is difficult to effectively improve the energy efficiency.

[0092] In the embodiment of the present utility model, the ratio of Vc / Ve is limited to Vc / Ve ≥ 0.15, ensuring the total volume of the first buffer space 321 and the second buffer space 37, enabling the first buffer space 321 and the second buffer space 37 to accommodate more gas, effectively improving the refrigerating capacity of the rotary compressor 100 and improving the energy efficiency of the rotary compressor 100.

[0093] Refer to Figure 1 and Figure 7, in some embodiments, the motor 2 includes a stator 21 and a rotor 22. The stator 21 can be sleeved on the outer periphery of the rotor 22. The crankshaft 34 can be connected to the rotor 22. The rotor 22 includes a rotor core 221 and permanent magnets 222. The permanent magnets 222 can be arranged within the rotor core 221 to generate a permanent magnetic field in the rotor 22. The stator 21 includes a stator core 211 which has a plurality of stator slots 212 for placing the stator 21 windings. After the stator 21 windings are energized, the stator 21 windings can generate a rotating magnetic field in the stator 21. The rotating magnetic field of the stator 21 can drive the permanent magnetic field of the rotor 22 to rotate, thereby driving the rotor 22 to rotate relative to the stator 21 to drive the crankshaft 34 to rotate, ensuring the normal operation of the motor 2.

[0094] Wherein, the number of poles of the rotor 22 is P, the number of stator slots 212 is Q, GCD(Q, P) is the greatest common divisor of the number of stator slots 212 and the number of poles of the rotor 22, and GCD(Q, P) can represent the order of the minimum electromagnetic force generated by the motor 2. The vibration of the motor 2 is approximately inversely proportional to the fourth power of the order of the electromagnetic force of the motor 2. If the order of the electromagnetic force of the motor 2 is too small, the vibration of the motor 2 is too large, affecting the stability of the operation of the motor 2 and easily generating a large amount of noise. If the order of the electromagnetic force of the motor 2 is too large, it is easy to increase the complexity of the motor 2's electronic control, affecting the reliability of the operation of the motor 2.

[0095] Therefore, Q, P, and GCD(Q, P) can be determined according to actual design requirements. For example, GCD(Q, P) can be limited within the range of 5 - 6, that is, GCD(Q, P) can be 5 or 6. When GCD(Q, P) = 5, the number of poles of the rotor 22 can be 10, and the number of stator slots 212 can be 15. When GCD(Q, P) = 6, the number of poles of the rotor 22 can be 12, and the number of stator slots 212 can be 18. This is beneficial to reducing the vibration level of the motor 2, beneficial to reducing the noise of the motor 2, improving the stability of the operation of the motor 2, and at the same time beneficial to simplifying the electronic control of the motor 2 and improving the reliability of the operation of the motor 2.

[0096] In some examples, the number of phases of the motor 2 is m, and the number of slots occupied by each phase winding under each magnetic pole is By limiting the motor 2 can use fractional slots, which is beneficial to saving energy, improving work efficiency, and reducing noise. And the fractional slots can adopt concentrated windings, which is beneficial to improving the regularity of automatic winding, can improve the utilization rate of the space in the stator slots 212, can make the variable losses and constant losses of the motor 2 at a relatively average level, thereby improving the work efficiency of the motor 2 and increasing the power density of the motor 2.

[0097] In some examples, the number of stator slots 212 is Q, the number of poles of the rotor 22 is P, the degree of vibration of the motor 2 is inversely proportional to the order of the minimum electromagnetic force generated by the motor 2, and GCD(Q, P) can represent the order of the minimum electromagnetic force generated by the motor 2. The designer can limit P between 10 and 12, and the designer can limit Q between 15 and 18, that is, P can be any value among 10, 11, and 12, and Q can be any value among 15, 16, 17, and 18.

[0098] Moreover, it can be ensured that the motor 2 adopts the form of a fractional-slot concentrated winding. That is, in order to simplify the electronic control and make the winding of the stator 21 more regular, the designer can choose the number of stator slots 212 to be 15 and the number of poles of the rotor 22 to be 10. Or, the designer can choose the number of stator slots 212 to be 18 and the number of poles of the rotor 22 to be 12. Thus, the vibration and noise of the motor 2 can be reduced, the electronic control of the motor 2 can be simplified, the winding of the winding can be made more regular, and it is convenient for manufacturing.

[0099] The other configurations and operations of the rotary compressor 100 according to the embodiments of the present invention are known to those of ordinary skill in the art and will not be described in detail here.

[0100] The refrigeration device according to the embodiment of the present invention includes the rotary compressor 100 in the above technical solution.

[0101] In the refrigeration device according to the embodiment of the present invention, the rotary compressor 100 compresses gas through a plurality of cylinders 31, increasing the refrigeration efficiency of the rotary compressor 100. A partition 32 is provided between adjacent cylinders 31. The partition 32 is provided with a first buffer space 321. The first buffer space 321 can accommodate the reflux gas, shortening the path of the gas reflux, effectively reducing the flow loss of the gas, improving the refrigerating capacity of the rotary compressor 100. In addition, the first buffer space 321 can also increase the unit suction volume of the cylinder 31, effectively improving the energy efficiency of the rotary compressor 100 and further increasing the refrigerating capacity of the rotary compressor 100.

[0102] In the description of this specification, the descriptions with reference to the terms "one embodiment", "some embodiments", "illustrative embodiments", "examples", "specific examples", or "some examples", etc. mean that the specific features, structures, materials, or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic representations of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials, or characteristics described can be combined in any one or more embodiments or examples in a suitable manner.

[0103] Although embodiments of the present invention have been shown and described, those of ordinary skill in the art can understand that various changes, modifications, substitutions, and variations can be made to these embodiments without departing from the principles and spirit of the present invention. The scope of the present invention is defined by the claims and their equivalents.

Claims

1. A rotary compressor, characterized in that: include: A plurality of cylinders, each of which is provided with a compression chamber and an air intake passage communicating with the compression chamber; A partition is provided between adjacent cylinders, the partition is provided with a first buffer space, and at least one of the intake passages is communicated with the adjacent first buffer space.

2. The rotary compressor according to claim 1, characterized in that: The air inlet passages on both sides of the partition are communicated with the first buffer space on the partition.

3. The rotary compressor according to claim 1, characterized in that: The cylinder is provided with a first flow guiding channel, and the air intake channel is communicated with the first buffer space through the first flow guiding channel.

4. The rotary compressor according to claim 3, characterized in that: An angle A is formed between an extension direction of the first flow guiding channel and an extension direction of the air intake channel, and A satisfies: 45°≤A≤90°.

5. The rotary compressor according to claim 4, characterized in that: A further satisfies: 45°≤A≤70°.

6. The rotary compressor according to claim 3, characterized in that: The diameter of the first flow guide channel is d, the diameter of the air intake channel is D, and d / D satisfies: 0.08≤d / D≤0.

35.

7. The rotary compressor according to claim 3, characterized in that: The diameter d of the first guide channel is in the range of 1 mm≤d≤4 mm.

8. The rotary compressor according to any one of claims 1 to 7, characterized in that: Also includes: A main bearing and a secondary bearing, wherein the main bearing and the secondary bearing are arranged on both sides of the plurality of cylinders, a second buffer space is formed between at least one of the main bearing and the secondary bearing and an adjacent cylinder, and the second buffer space is communicated with the adjacent intake passage.

9. The rotary compressor according to claim 8, characterized in that: The total volume of the first buffer space and the second buffer space is Vc, the displacement of the rotary compressor is Ve, and Vc / Ve satisfies: Vc / Ve≥0.

15.

10. A refrigeration device, characterized in that: include: A rotary compressor according to any one of claims 1 to 9.

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