Rotary compressor and refrigeration device

Abstract

The utility model discloses a rotary compressor and a refrigerating plant, the rotary compressor comprises a shell, a rotary shaft, an air inlet pipe, an air outlet pipe, an air inlet pipe and an air outlet pipe, the motor and the compression component are both located in the shell, the motor divides the containing cavity into a first cavity body and a second cavity body, the exhaust pipe is communicated with the first cavity body, the compression component is located in the second cavity body, an exhaust silencer of the compression component is communicated with the second cavity body, and the motor is provided with a communicating channel communicating the first cavity body with the second cavity body; the rotary compressor meets the following conditions: 5 < = GCD (Q, P) < = 6; the first cavity and the communicating channel form a first resonant cavity, the first resonant cavity meets the requirement of # imgabs 0 #, the second cavity and the exhaust channel of the exhaust silencer form a second resonant cavity, and the second resonant cavity meets the requirement of # imgabs 1 #. According to the rotary compressor, the resonant frequency of the first resonant cavity and the resonant frequency of the second resonant cavity are improved, gas pulsation is reduced, and the gas pulsation is reduced. And the noise condition of the rotary compressor is improved.

Description

Technical Field

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

[0002] With the development of compressor technology, miniaturization and lightweighting of rotary compressors have gradually become the mainstream development trend. However, the miniaturization of rotary compressors will lead to a reduction in the space inside the shell, that is, the space inside the shell for gas flow is reduced, resulting in increased air flow pulsation and louder noise when the rotary compressor is working. Utility Model Content

[0003] The present invention aims to solve at least one of the technical problems existing in the prior art. To this end, the present invention proposes a rotary compressor, which increases the flow area S of the connecting channel by D , the inner diameter D of the shell, the length H1 of the first cavity, the thickness T of the stator core, the exhaust area S of the exhaust channel X The length H2 of the second cavity and the length H3 of the exhaust channel are set in a reasonable ratio, which improves the resonance frequency of the first resonance cavity and the second resonance cavity, reduces the pulsation of the gas, and improves the noise of the rotary compressor.

[0004] The utility model also provides a refrigeration device comprising the rotary compressor.

[0005] According to an embodiment of the present invention, a rotary compressor includes: a housing, the housing is provided with a housing cavity and an exhaust pipe; a motor and a compression component, the motor and the compression component are both located in the housing, the motor divides the housing cavity into a first cavity and a second cavity, the exhaust pipe is connected to the first cavity, the compression component is located in the second cavity, the exhaust muffler of the compression component is connected to the second cavity, and the motor is provided with a connecting channel connecting the first cavity and the second cavity; the rotary compressor satisfies: 5≤GCD(Q, P)≤6; the first cavity and the connecting channel form a first resonant cavity, and the first resonant cavity satisfies: 0.76≤ The second cavity and the exhaust passage of the exhaust muffler form a second resonance cavity, and the second resonance cavity satisfies: Wherein, Q is the number of slots of the motor, P is the number of poles of the motor, GCD(Q, P) is the greatest common divisor of P and Q, S D is the flow area of ​​the communication channel, D is the inner diameter of the housing, H1 is the length of the first cavity, T is the thickness of the stator core of the motor, S X is the exhaust area of ​​the exhaust channel, H2 is the length of the second cavity, and H3 is the length of the exhaust channel.

[0006] According to the rotary compressor of the embodiment of the present invention, the flow area S of the communication channel D , the inner diameter D of the shell, the length H1 of the first cavity, the thickness T of the stator core, the exhaust area S of the exhaust channel X , the length H2 of the second cavity and the length H3 of the exhaust channel, adopt the above reasonable ratio setting, the compressed gas passes through the second resonance cavity and the first resonance cavity in turn, and the resonance of the second resonance cavity and the first resonance cavity effectively reduces the sound wave energy of the gas, reduces the pulsation of the gas, and improves the noise of the rotary compressor.

[0007] In some embodiments, the first resonant cavity further satisfies: The second resonant cavity further satisfies:

[0008] In some embodiments, the motor includes a stator and a rotor, and the communication channel includes: a flow hole provided in the rotor, a gap between the stator and the rotor, and a gap in the stator winding of the stator.

[0009] In some embodiments, a cross-sectional area of ​​the exhaust channel gradually decreases in a direction toward the second cavity.

[0010] In some embodiments, the exhaust passage is formed as a plurality of through holes on the exhaust muffler. X is the total area of ​​the plurality of through holes.

[0011] In some embodiments, the thickness T of the stator core of the motor satisfies: 20 mm ≤ T ≤ 80 mm.

[0012] In some embodiments, the number of poles P of the motor satisfies: 10≤P≤12; the number of slots Q of the motor satisfies: 15≤Q≤18.

[0013] In some embodiments, the rotary compressor satisfies: Wherein, m is the number of phases of the motor.

[0014] The refrigeration device according to the embodiment of the present invention includes the rotary compressor described in the above technical solution.

[0015] Additional aspects and advantages of the present invention will be given in part in the following description and will become apparent from the following description or learned through practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] The above and / or additional aspects and advantages of the present invention will become apparent and readily understood from the description of the embodiments in conjunction with the following drawings, in which:

[0017] Figure 1 is a schematic diagram of a rotary compressor according to an embodiment of the present utility model;

[0018] Figure 2 yes Schematic diagram of the curve change with gas pulsation;

[0019] Figure 3 yes Schematic diagram of the curve change with gas pulsation;

[0020] Figure 4 is an enlarged view of the exhaust muffler portion of the rotary compressor according to an embodiment of the present utility model;

[0021] Figure 5 is a top view of an exhaust muffler according to other embodiments of the present utility model;

[0022] Figure 6 yes Figure 5 Cross-sectional view of the exhaust muffler;

[0023] Figure 7 Schematic diagram of a motor according to an embodiment of the present invention.

[0024] Figure numerals: 100, rotary compressor; 1, shell; 11, accommodating chamber; 111, first cavity; 112, second cavity; 12, exhaust pipe; 2, motor; 21, stator; 211, stator core; 212, stator slot; 22, rotor; 221, rotor core; 222, permanent magnet; 223, flow hole; 224, winding gap; 3, compression component; 31, exhaust muffler; 311, muffler chamber; 312, exhaust channel; 313, avoidance hole; 314, flange; 315, through hole; 32, main bearing. DETAILED DESCRIPTION

[0025] The following describes embodiments of the present invention in detail. Examples of the embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are intended only to explain the present invention and are not to be construed as limiting the present invention.

[0026] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings. They are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present invention. In addition, features defined as "first" or "second" may explicitly or implicitly include one or more of such features. In the description of the present invention, unless otherwise specified, "multiple" means two or more.

[0027] In the description of this utility model, it should be noted that, unless otherwise expressly specified or limited, the terms "mounted," "connected," and "connected" should be understood in a broad sense. For example, they can refer to fixed connections, detachable connections, or integral connections; mechanical connections, electrical connections; direct connections, indirect connections through an intermediate medium, and internal communication between two components. Those skilled in the art will understand the specific meanings of the above terms in this utility model based on the specific circumstances.

[0028] Reference below Figure 1-Figure 7 A rotary compressor 100 according to an embodiment of the present invention will be described.

[0029] Reference Figure 1 、 Figure 2 and Figure 4 According to an embodiment of the present invention, a rotary compressor 100 includes: a shell 1, a motor 2 and a compression component 3, wherein the shell 1 is provided with a accommodating chamber 11 and an exhaust pipe 12, the motor 2 and the compression component 3 are both located in the shell 1, the motor 2 divides the accommodating chamber 11 into a first cavity 111 and a second cavity 112, the exhaust pipe 12 is connected to the first cavity 111, the compression component 3 is located in the second cavity 112, and the exhaust muffler 31 of the compression component 3 is connected to the second cavity 112, and the motor 2 is provided with a connecting channel connecting the first cavity 111 and the second cavity 112.

[0030] When the rotary compressor 100 is working, the motor 2 drives the compression component 3 to compress the gas. The compressed gas in the compression component 3 is discharged into the second cavity 112 through the exhaust muffler 31, then enters the first cavity 111 through the connecting channel of the motor 2, and finally is discharged from the rotary compressor 100 through the exhaust pipe 12.

[0031] The exhaust muffler 31 includes a muffler chamber 311 and an exhaust passage 312. The compressed gas in the compression component 3 first enters the muffler chamber 311 and then enters the second chamber 112 through the exhaust passage 312. The larger the volume of the muffler chamber 311 in the exhaust muffler 31, the better the muffler effect of the exhaust muffler 31; the smaller the flow area of ​​the exhaust passage 312 of the exhaust muffler 31, the better the muffler effect of the exhaust muffler 31.

[0032] The gas first passes through the exhaust channel 312 with a smaller flow area, and then passes through the second cavity 112 with a larger flow area, so that the exhaust channel 312 and the second cavity 112 form a resonance cavity; the gas passes through the connecting channel with a smaller flow area, and then passes through the first cavity 111 with a larger flow area, so that the connecting channel and the first cavity 111 form a resonance cavity.

[0033] When gas enters a channel with a larger flow area from a channel with a smaller flow area, the channel with a smaller flow area and the channel with a larger flow area form a resonance cavity. The air in the channel with a larger flow area is equivalent to a spring. When gas enters a channel with a larger flow area from a channel with a smaller flow area, it will impact the air in the channel with a larger flow area. The gas in the channel with a larger flow area will react on the gas in the channel with a smaller flow area, causing both the gas in the channel with a smaller flow area and the gas in the channel with a larger flow area to vibrate, consuming the sound wave energy of the gas and reducing the pulsation of the gas.

[0034] The closer the resonant frequency of the resonance cavity is to the sound wave frequency of the gas, the better the resonance effect of the resonance cavity and the better the effect of reducing gas pulsation. The length and flow area of ​​the channel with a smaller flow area and the volume of the channel with a larger flow area will all affect the resonant frequency of the resonance cavity.

[0035] The first cavity 111 and the communicating channel form a first resonant cavity, which satisfies:

[0036]

[0037] Among them, S D is the flow area of ​​the communication channel, T is the thickness of the stator core of the motor 2, the thickness of the stator core is equal to the length of the communication channel, D is the inner diameter of the housing 1, H1 is the length of the first cavity 111, D 2 *H1 is proportional to the volume of the first cavity 111, so it can be adjusted The resonant frequency of the first resonant cavity is adjusted by the value of

[0038] Reference Figure 2 It can be seen that when When the value is within the range of 0.76-2, the pulsation of the air flow is small and the noise improvement effect of the rotary compressor is better.

[0039] Specifically, It can be any point value among 0.76, 0.83, 0.88, 0.95, 1.3, 1.8, 2, or a range of values ​​between any two of them.

[0040] The second cavity 112 and the exhaust channel 312 form a second resonance cavity, and the second resonance cavity satisfies:

[0041]

[0042] Among them, S X is the exhaust area of ​​the exhaust channel 312, H2 is the length of the second cavity 112, H3 is the length of the exhaust channel, D 2 *H2 is proportional to the volume of the second cavity 112, so it can be adjusted The resonant frequency of the second resonant cavity is adjusted by the value of

[0043] Reference Figure 3 It can be seen that when When the value is within the range of 0.76-2, the pulsation of the air flow is small and the noise improvement effect of the rotary compressor is better.

[0044] Specifically, It can be any point value among 0.76, 0.83, 0.88, 0.95, 1.3, 1.8, 2, or a range of values ​​between any two of them.

[0045] The rotary compressor 100 of the embodiment of the present utility model also meets the following requirements:

[0046] 5≤GCD(Q, P)≤6, where Q is the number of slots of the stator 21 (i.e., the number of stator slots 212), and P is the number of poles of the rotor 22. The rotor 22 is provided with a plurality of permanent magnets 222, each of which has its own south pole and north pole. However, each permanent magnet 222 has only one end face (south pole or north pole) facing the stator 21 and interacting with the stator 21. Therefore, the number of poles of the rotor 22 is equal to the number of permanent magnets 222, and GCD(Q, P) is the greatest common divisor of Q and P.

[0047] In the above technical solution, 5≤GCD(Q, P)≤6, that is, the number of slots Q of the stator 21 can be 15, 18, 20, 24, 54 and other values. Compared with the 9-slot 6-pole motor or the 12-slot 8-pole motor in the related art, in the rotary compressor 100 of the present application, the motor 2 increases the number of slots of the stator 21, so that the stator 21 can provide a more uniform magnetic field distribution, reduce the unevenness of the magnetic field, and is beneficial to improving the output power of the motor 2, thereby improving the operation stability of the rotary compressor 100; the number of poles P of the rotor 22 can be 10, 12, 20, 24 and other values. Compared with the 9-slot 6-pole motor or the 12-slot 8-pole motor in the related art, the motor 2 provided in the present application increases the number of poles of the rotor 22. The more poles the rotor 22 has, the lower the speed of the rotor 22, the greater the torque that can be provided, and the smoother the rotation of the rotor 22, which effectively improves the working stability of the motor 2, that is, improves the operation stability of the rotary compressor 100.

[0048] The flow area S of the communication channel of the motor 2 D Related to GCD (Q, P), if GCD (Q, P) changes, it means that the number of poles P and / or the number of slots Q of the motor 2 have changed, and the overall structure of the motor 2 has changed, resulting in the flow area S of the connecting channel. D Changes have occurred.

[0049] For example, refer to Figure 7 When the number of slots Q of the motor 2 increases, the area of ​​a single stator slot 212 will become smaller, and the winding gap 224 between adjacent stator windings will also become smaller. Although the number of slots increases, the total flow space of multiple winding gaps 224 will decrease, resulting in a flow area S of the connecting channel. D The communication channel refers to a channel for gas to enter the first cavity 11 from the second cavity 112 , and the winding gap 224 is also a part of the communication channel.

[0050] For example, when the number of poles of the motor 2 increases and the outer diameter of the rotor 22 increases, the gap between the rotor and the stator will also change. The gap between the rotor and the stator is also part of the communication channel.

[0051] The two ends of the communication channel are connected to the first cavity and the second cavity respectively. When the flow area of ​​the communication channel changes, the resonance effects of the first resonant cavity and the second resonant cavity will also change. As mentioned above, the embodiment of the present invention can limit the flow area S of the communication channel by limiting the range of GCD (Q, P). D range, thereby ensuring the resonance effect of the first resonance cavity and the second resonance cavity.

[0052] According to the rotary compressor 100 of the embodiment of the present invention, the greatest common divisor GCD (Q, P) of the number of poles and slots of the motor 2, the flow area S of the communication channel D , the inner diameter D of the shell, the length H1 of the first cavity, the thickness T of the stator core, the exhaust area S of the exhaust channel X , the length H2 of the second cavity and the length H3 of the exhaust channel, adopt the above reasonable ratio setting, the compressed gas passes through the second resonance cavity and the first resonance cavity in turn, and the resonance of the second resonance cavity and the first resonance cavity effectively reduces the sound wave energy of the gas, reduces the pulsation of the gas, and improves the noise of the rotary compressor.

[0053] In some embodiments, the first resonant cavity further satisfies:

[0054] Reference Figure 2 It can be seen that when When the value is within the range of 0.8-1.5, the pulsation of the air flow is smaller and the noise improvement effect of the rotary compressor is better.

[0055] Specifically, It can be any point value among 0.8, 0.83, 0.88, 0.95, 1.3, 1.5, or a range of values ​​between any two of them.

[0056] In some embodiments, the second resonant cavity further satisfies:

[0057] Reference Figure 3 It can be seen that when When the value is within the range of 0.8-1.5, the pulsation of the air flow is smaller and the noise improvement effect of the rotary compressor is better.

[0058] Specifically, It can be any point value among 0.8, 0.83, 0.88, 0.95, 1.3, 1.5, or a range of values ​​between any two of them.

[0059] Reference Figure 1 and Figure 7 In some embodiments, the motor 2 includes a stator 21 and a rotor 22. The communication passage includes: a flow hole 223 provided in the rotor 22, a gap between the stator 21 and the rotor 22, and a winding gap 224 of the stator winding of the stator 21. The flow hole 223, the gap between the stator 21 and the rotor 22, and the winding gap 224 are all gas-permeable.

[0060] The rotor 22 is provided with a plurality of flow holes 223 , the total area of ​​the plurality of flow holes 223 is S1 , the area of ​​the gap between the stator 21 and the rotor 22 is S2 , each stator slot 212 has a winding gap 224 , the total area of ​​the plurality of winding gaps 224 is S3 .

[0061] In the embodiment of the present invention, the flow area S of the communication channel is D =S1+S2+S3.

[0062] S3 =Q×L×W, where W is the slot width of the stator slot 212 , and L is the length of an extension line extending from the edge of the slot opening of the stator slot 212 to the slot bottom of the stator slot 212 .

[0063] In other embodiments, a first through hole is provided on the stator core, and the connecting channel also includes the area of ​​the first through hole. Other situations are also possible. As long as the channel in the motor 2 can allow gas to pass through, it is part of the connecting channel.

[0064] Reference Figure 1 and Figure 4 In some embodiments, the exhaust muffler 31 is arranged on the main bearing 32 of the compression component 3, and a muffler chamber 311 is defined between the exhaust muffler 31 and the main bearing 32. A avoidance hole 313 is provided in the middle position of the exhaust muffler 31, and the hub of the main bearing 32 is penetrated by the avoidance hole 313. The gap between the inner wall of the avoidance hole 313 and the hub of the main bearing 32 defines an exhaust channel 312.

[0065] In the embodiment of the present invention, the inner diameter of the avoidance hole 313 is D1, the outer diameter of the portion where the hub of the main bearing 32 fits in the avoidance hole 313 is D2, and the exhaust area of ​​the exhaust passage 312 is The length H3 of the exhaust passage 312 is the extended length of the avoidance hole 313 .

[0066] In the embodiment of the present invention, the exhaust muffler 31 has a simple structure, which reduces the cost of the rotary compressor 100 .

[0067] In some further embodiments, the cross-sectional area of ​​the exhaust passage 312 gradually decreases in the direction toward the second cavity 112 , thereby effectively increasing the silencing effect of the exhaust muffler 31 .

[0068] In some embodiments, the exhaust muffler 31 is provided with an annular flange 314, the inner diameter of which gradually decreases in the direction of the second cavity 112, and the flange 314 defines an escape hole 313. In the embodiment of the present invention, the length H3 of the exhaust channel 312 is the height of the flange.

[0069] In the embodiment of the present invention, the exhaust muffler 31 has a simple structure, which reduces the cost of the rotary compressor 100 .

[0070] Reference Figure 5 and Figure 6 In other embodiments, the exhaust muffler 31 is provided on the main bearing 32 of the compression component 3, and a muffler cavity 311 is defined between the exhaust muffler 31 and the main bearing 32. A plurality of through holes 315 are formed on the exhaust channel 312, and the exhaust area S of the exhaust channel 312 is X is the total area of ​​the plurality of through holes 315. In the embodiment of the present invention, the exhaust muffler 31 has a simple structure, which reduces the cost of the rotary compressor.

[0071] Reference Figure 1 In some embodiments, the thickness T of the stator core of the motor 2 satisfies: 20 mm ≤ T ≤ 80 mm.

[0072] The greater the thickness T of the stator core, the greater the thickness of the rotor core, and the greater the rotational inertia of the rotor 22. When the rotary compressor 100 operates at a low frequency, the rotor 22 is more likely to drive the piston of the compression component 3 to overcome the gas resistance torque of the pump body. The energy efficiency of the rotary compressor 100 is higher when it operates at a low frequency. However, if the thickness T of the stator core is too large, the motor 2 will occupy too much space inside the rotary compressor 100, which is not conducive to the miniaturization of the rotary compressor 100.

[0073] The thickness of the stator core of the motor 2 is also equal to the length of the connecting channel. In the embodiment of the present invention, the thickness T of the stator core is limited to 20mm≤T≤80mm. While meeting the miniaturization design of the rotary compressor 100, the energy efficiency of the rotary compressor 100 during low-frequency operation is improved, and the resonance effect of the first resonance cavity and the second resonance cavity is also ensured.

[0074] Specifically, the thickness T of the stator core may be any one of 20 mm, 30 mm, 45 mm, 50 mm, 70 mm, and 80 mm, or a range of values ​​between any two of them.

[0075] Reference Figure 1 and Figure 7 In some embodiments, the motor 2 includes a stator 21 and a rotor 22. The stator 21 can be mounted on the outer periphery of the rotor 22. The crankshaft of the compression component 3 can be connected to the rotor 22. The rotor 22 includes a rotor core 221 and a permanent magnet 222. The permanent magnet 222 can be arranged in the rotor core 221 to generate a permanent magnetic field in the rotor 22. The stator 21 includes a stator core 211. The stator core 211 has a plurality of stator slots 212 for placing stator windings. After the stator winding is energized, the stator winding 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, thereby driving the crankshaft to rotate, and ensuring the normal operation of the motor 2.

[0076] Among them, 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 electromagnetic force order of the motor 2. If the electromagnetic force order of the motor 2 is too small, the vibration of the motor 2 is too large, which affects the stability of the operation of the motor 2 and is prone to generate large noise. If the electromagnetic force order of the motor 2 is too large, it is easy to increase the complexity of the electronic control of the motor 2, affecting the reliability of the operation of the motor 2.

[0077] Therefore, Q, P and GCD(Q, P) can be determined according to actual design requirements. For example, GCD(Q, P) can be limited to the range between 5 and 6, that is, GCD(Q, P) can be 5 or 6, and 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, which is beneficial to reducing the vibration level of the motor 2, reducing the noise of the motor 2, and improving the working stability of the motor 2. At the same time, it is beneficial to simplify the electronic control of the motor 2 and improve the working reliability of the motor 2.

[0078] 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 pole is By limiting Motor 2 can use fractional slots, which is beneficial to saving energy, improving work efficiency, and reducing noise. The fractional slots can adopt centralized windings, which is beneficial to improving the regularity of automated winding, improving the utilization rate of the space in the stator slot 212, and making the variable loss and constant loss of motor 2 at a relatively average level, thereby improving the work efficiency of motor 2 and improving the power density of motor 2.

[0079] In some examples, the number of stator slots 212 is Q, the number of poles of the rotor 22 is P, the vibration degree 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 to between 10-12, and the designer can limit Q to between 15-18, that is, P can be any value of 10, 11, and 12, and Q can be any value of 15, 16, 17, and 18.

[0080] Moreover, it can be ensured that the motor 2 adopts the form of fractional slot concentrated winding, that is, in order to simplify the electronic control and to make the winding of the stator 21 winding 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. In this way, the vibration and noise of the motor 2 can be reduced, and the electronic control of the motor 2 can be simplified, so that the winding of the winding is more regular and easy to manufacture.

[0081] Other structures and operations of the rotary compressor 100 according to the embodiment of the present invention are known to those skilled in the art and will not be described in detail here.

[0082] The refrigeration equipment according to the embodiment of the present invention includes: the rotary compressor in the above technical solution.

[0083] According to the refrigeration equipment of the embodiment of the present invention, the flow area S of the communication channel of the rotary compressor is D , the inner diameter D of the shell, the length H1 of the first cavity, the thickness T of the stator core, the exhaust area S of the exhaust channel X The length H2 of the second cavity and the length H3 of the exhaust channel are set with the above-mentioned reasonable ratios. The compressed gas passes through the second resonance cavity and the first resonance cavity in turn. Through the resonance of the second resonance cavity and the first resonance cavity, the sound wave energy of the gas is effectively reduced, the pulsation of the gas is reduced, the noise of the rotary compressor is improved, and the noise of the refrigeration equipment is improved.

[0084] Throughout this specification, reference to terms such as "one embodiment," "some embodiments," "illustrative embodiments," "examples," "specific examples," or "some examples" means that the specific features, structures, materials, or characteristics described in conjunction with that embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the illustrative use of the above terms does not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.

[0085] Although the embodiments of the present invention have been shown and described, those skilled in the art will appreciate that various changes, modifications, substitutions and variations may be made to the embodiments without departing from the principles and purpose of the present invention, and that the scope of the present invention is defined by the claims and their equivalents.

Claims

1. A rotary compressor, characterized in that: include: a housing, wherein the housing is provided with a receiving cavity and an exhaust pipe; A motor and a compression component, both of which are located within the housing; the motor divides the accommodating chamber into a first cavity and a second cavity; the exhaust pipe is in communication with the first cavity; the compression component is located in the second cavity; the exhaust muffler of the compression component is in communication with the second cavity; and the motor is provided with a communication channel connecting the first cavity and the second cavity; the rotary compressor satisfies the following requirements: 5≤GCD(Q,P)≤6; The first cavity and the communicating channel form a first resonant cavity, and the first resonant cavity satisfies: The second cavity and the exhaust passage of the exhaust muffler form a second resonance cavity, and the second resonance cavity satisfies: Wherein, Q is the number of slots of the motor, P is the number of poles of the motor, GCD(Q, P) is the greatest common divisor of P and Q, S D is the flow area of ​​the communication channel, D is the inner diameter of the housing, H1 is the length of the first cavity, T is the thickness of the stator core of the motor, S X is the exhaust area of ​​the exhaust channel, H2 is the length of the second cavity, and H3 is the length of the exhaust channel.

2. The rotary compressor according to claim 1, wherein The first resonant cavity further satisfies: The second resonant cavity further satisfies:

3. The rotary compressor according to claim 1, wherein The motor includes a stator and a rotor, and the communication channel includes: a flow hole provided in the rotor, a gap between the stator and the rotor, and a gap in the stator winding of the stator.

4. The rotary compressor according to claim 1, wherein The cross-sectional area of ​​the exhaust channel gradually decreases in a direction toward the second cavity.

5. The rotary compressor according to claim 1, wherein The exhaust passage is formed as a plurality of through holes on the exhaust muffler. X is the total area of ​​the plurality of through holes.

6. The rotary compressor according to claim 1, wherein The thickness T of the stator core of the motor satisfies: 20 mm ≤ T ≤ 80 mm.

7. The rotary compressor according to any one of claims 1 to 6, characterized in that: The number of poles P of the motor satisfies: 10≤P≤12; the number of slots Q of the motor satisfies: 15≤Q≤18.

8. The rotary compressor according to claim 7, wherein: The rotary compressor satisfies: <1, where m is the number of phases of the motor.

9. A refrigeration device, characterized in that: include: A rotary compressor according to any one of claims 1 to 8.

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