Rotary compressor and refrigeration equipment

Abstract

The utility model discloses a rotary compressor and refrigeration equipment, relates to compressor technical field, rotary compressor includes shell and set up motor subassembly, crankshaft, support subassembly and oil-gas separation piece in the shell inner cavity, motor subassembly includes stator and rotor, stator and shell connection, rotor and crankshaft fixed connection, crankshaft protrudes upwards the rotor, and the oil-gas separation piece is located in the shell inner cavity. The supporting assembly is located above the motor assembly and comprises a support and a motor bearing, the support is fixedly connected with the shell, the motor bearing is installed on the support, the oil-gas separation part is fixedly installed on the rotor, and stirring plates of the oil-gas separation part are arranged around the crankshaft and extend towards the support. According to the rotary compressor, the oil-gas separation effect can be enhanced, the oil spitting amount is reduced, and the liquid level of the oil pool is stable.

Description

Technical Field

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

[0002] Refrigeration oil provides the necessary lubrication, sealing and heat dissipation functions for the stable operation of the compressor. During the operation of the compressor, the refrigeration oil in the oil pool at the bottom of the compressor is transported by the oil supply system and spread in the inner cavity of the compressor under the drive of the high-pressure refrigerant. Some of the refrigeration oil will be discharged from the compressor in the form of oil droplets along with the high-pressure refrigerant and enter the refrigeration system, resulting in oil spitting, which in turn causes the oil level in the oil pool to drop, affecting the lubrication, sealing and heat dissipation performance of the compressor, and inducing vibration and noise. In the related technology, the centrifugal force generated by the rotation of the crankshaft is used to make the cooling oil in the form of oil droplets hit the inner wall of the compressor to achieve oil-gas separation. The separation effect is poor and the amount of oil spitting is large. Utility Model Content

[0003] The utility model aims to solve at least one of the technical problems existing in the prior art. To this end, the utility model provides a rotary compressor that can enhance the oil-gas separation effect, reduce the oil discharge amount, and stabilize the liquid level of the oil pool.

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

[0005] The rotary compressor according to the first embodiment of the utility model comprises:

[0006] a housing having an inner cavity;

[0007] A motor assembly is disposed in the inner cavity, the motor assembly comprises a stator and a rotor, the stator is connected to the housing and is disposed around the outer circumference of the rotor;

[0008] A crankshaft, fixedly connected to the rotor and protruding upward from the rotor;

[0009] A support assembly is installed in the inner cavity and located above the motor assembly, the support assembly includes a bracket and a motor bearing, the bracket is fixedly connected to the inner wall of the shell, and the motor bearing is installed on the bracket and sleeved on the upper end of the crankshaft;

[0010] The oil-gas separator is fixedly mounted on the rotor and located between the rotor and the bracket. The oil-gas separator includes a stirring plate, which is arranged around the outer circumference of the crankshaft and extends toward the bracket.

[0011] The rotary compressor according to the first aspect of the utility model has at least the following beneficial effects: by installing an oil-gas separator on the rotor, the stirring plate of the oil-gas separator rotates with the rotor, and can stir the gaseous refrigerant and liquid refrigerant oil located above the rotor. Since the density of the refrigerant oil is greater than the density of the gaseous refrigerant, under the action of centrifugal force, the refrigerant oil is thrown to the inner wall of the shell and flows back to the oil pool at the bottom, and the gaseous refrigerant is further discharged upward from the compressor, thereby realizing oil and gas separation, enhancing the oil and gas separation effect, reducing the oil discharge amount, making the liquid level of the oil pool stable, and effectively ensuring the lubrication, sealing and heat dissipation performance of the compressor.

[0012] According to some embodiments of the utility model, the oil-gas separation component also includes a fixed plate, the stirring plate is connected to the outer periphery of the fixed plate, the fixed plate is provided with an avoidance hole, the fixed plate is fixedly connected to the upper end of the rotor, and the crankshaft is passed through the avoidance hole.

[0013] According to some embodiments of the utility model, the fixing plate is provided with a plurality of fixing holes, and the plurality of fixing holes are arranged at intervals along a direction around the central axis of the crankshaft, and a fastener is connected between the fixing plate and the rotor, and the fastener is passed through the fixing holes.

[0014] According to some embodiments of the present invention, the fixing plate is further provided with a through hole, the rotor is provided with a rotor channel, the rotor channel passes through both ends of the rotor along the direction of the central axis of the crankshaft, and the through hole is communicated with the rotor channel.

[0015] According to some embodiments of the present invention, the maximum outer diameter of the oil-gas separation element is greater than twice the maximum distance between the inner wall of the rotor channel and the central axis of the crankshaft, and is less than or equal to the maximum outer diameter of the rotor.

[0016] According to some embodiments of the present invention, the stator includes a first iron core and a winding package, the winding package is wound around the first iron core and protrudes from the upper end of the first iron core, and along the direction of the central axis of the crankshaft, the upper end of the winding package is higher than the upper end of the stirring plate.

[0017] According to some embodiments of the present invention, along the direction of the central axis of the crankshaft, the minimum distance between the bracket and the first core is H 1 , the minimum distance between the support and the stirring plate is H 2 , satisfying: 0.51≤H 2 / H 1 ≤0.72.

[0018] According to some embodiments of the present invention, along the direction of the central axis of the crankshaft, the minimum distance between the bracket and the first core is H 1The maximum distance between the upper end of the coil and the first core is H 3 , satisfying: 0.8≤H 3 / H 1 ≤0.95.

[0019] According to some embodiments of the present invention, the minimum distance H between the bracket and the first core is 1 and the maximum distance H between the upper end of the coil and the first core 3 Satisfaction: H 1 -H 3 ≥2mm.

[0020] The refrigeration device according to the second embodiment of the utility model includes the rotary compressor of the first embodiment of the utility model.

[0021] The refrigeration equipment according to the embodiment of the second aspect of the utility model has at least the following beneficial effects: since the refrigeration equipment adopts the above-mentioned rotary compressor, by installing an oil-gas separator on the rotor, the stirring plate of the oil-gas separator rotates with the rotor, and can stir the gaseous refrigerant and liquid refrigerant oil located above the rotor. Since the density of the refrigerant oil is greater than the density of the gaseous refrigerant, under the action of centrifugal force, the refrigerant oil is thrown to the inner circumferential wall of the shell and flows back to the oil pool at the bottom, and the gaseous refrigerant is further discharged upward from the compressor, thereby realizing oil and gas separation, enhancing the oil and gas separation effect, reducing the oil discharge amount, making the liquid level of the oil pool stable, and effectively ensuring the lubrication, sealing and heat dissipation performance of the compressor.

[0022] Additional aspects and advantages of the present invention will be given in part in the following description, and in part will become apparent from the following description, or will be learned through the practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] The present invention is further described below with reference to the accompanying drawings and embodiments, wherein:

[0024] Figure 1 is a cross-sectional view of a rotary compressor in an embodiment of the utility model;

[0025] Figure 2 It is a partial cross-sectional view of a rotary compressor in an embodiment of the utility model;

[0026] Figure 3 yes Figure 2 A in the enlarged view;

[0027] Figure 4 It is a structural schematic diagram of the oil-gas separation component in the embodiment of the utility model;

[0028] Figure 5 In the embodiment of the utility model, the relative height of the oil level changes with H2 / H 1 A graph of changes;

[0029] Figure 6 In the embodiment of the utility model, the relative height of the oil level changes with H 3 / H 1 Change graph.

[0030] Reference numerals:

[0031] Shell 100, inner cavity 110, oil pool 120, exhaust pipe 130;

[0032] Motor assembly 200, stator 210, first iron core 211, first wall 2111, coil 212, second wall 2121, rotor 220, rotor channel 221;

[0033] Pump body assembly 300, first cylinder 310, second cylinder 320, crankshaft 330, eccentric portion 331, central oil hole 332, upper bearing 340, lower bearing 350, piston 360, partition plate 370, muffler 380;

[0034] Support assembly 400, bracket 410, third wall surface 411, motor bearing 420;

[0035] The oil-gas separation element 500, the stirring plate 510, the fourth wall surface 511, the fixing plate 520, the avoidance hole 521, the fixing hole 522, and the through hole 523;

[0036] Liquid reservoir 600. DETAILED DESCRIPTION

[0037] The embodiments of the present invention are described in detail below, and 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 only used to explain the present invention, and cannot be understood as limiting the present invention.

[0038] In the description of the present invention, it should be understood that descriptions involving orientation, such as up, down, front, back, left, right, etc., indicating orientations or positional relationships, are based on the orientations or positional relationships shown in the accompanying drawings, and 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.

[0039] In the description of the present utility model, "several" means one or more, "more" means more than two, "greater than", "less than", "exceed" etc. are understood to exclude the number itself, and "above", "below", "within" etc. are understood to include the number itself. If there is a description of "first" or "second", it is only used for the purpose of distinguishing the technical features, and cannot be understood as indicating or implying the relative importance or implicitly indicating the number of the indicated technical features or implicitly indicating the order of the indicated technical features.

[0040] In the description of the present utility model, unless otherwise clearly defined, terms such as setting, installing, connecting, assembling, and matching should be understood in a broad sense, and technicians in the relevant technical field can reasonably determine the specific meanings of the above terms in the present utility model based on the specific content of the technical solution.

[0041] During the operation of the compressor, the refrigerant oil in the oil pool at the bottom of the compressor is transported by the oil supply system and spread in the inner cavity of the compressor under the drive of the high-pressure refrigerant. The refrigerant oil in the oil drop state and the gaseous refrigerant form an oil-gas mixture. In the related technology, the centrifugal force generated by the rotation of the crankshaft of the rotary compressor causes the oil droplets to hit the inner wall of the compressor housing, and the gaseous refrigerant is discharged from the compressor into the refrigeration system under the action of the high pressure of the compressor. However, the separation of oil and gas is not achieved by relying solely on the centrifugal force generated by the rotation of the crankshaft. A large amount of oil droplets still follow the gaseous refrigerant out of the compressor into the refrigeration system. The large amount of oil discharge causes the oil level in the oil pool to drop, affecting the lubrication, sealing and heat dissipation performance of the compressor.

[0042] For this purpose, refer to Figures 1 to 6 As shown, the first embodiment of the utility model provides a rotary compressor, which is applied to refrigeration equipment, and the refrigeration equipment can be an air conditioner, a refrigerator, a freezer, a water dispenser or an air-energy water heater, etc. As the core power component of the refrigeration equipment, the rotary compressor is mainly used to compress the refrigerant to achieve the purpose of heat exchange through the circulation of the refrigerant.

[0043] Reference Figure 1 and Figure 2 As shown, it can be understood that the rotary compressor includes a housing 100, a motor assembly 200, a crankshaft 330, a support assembly 400 and an oil-gas separator 500. The housing 100 is roughly cylindrical in structure, and an inner cavity 110 is formed inside the housing 100. The motor assembly 200, the crankshaft 330, the support assembly 400 and the oil-gas separator 500 are all installed in the inner cavity 110 of the housing 100. The bottom of the inner cavity 110 of the housing 100 is formed with a space for storing refrigeration oil, that is, an oil pool 120. A liquid reservoir 600 is installed on the side of the housing of the rotary compressor, and the liquid reservoir 600 is used to store liquid refrigerant. An exhaust pipe 130 is also provided on the top of the housing 100, and the exhaust pipe 130 is used to discharge the refrigerant to the outside of the compressor.

[0044] Reference Figure 1 and Figure 2 As shown, it can be understood that the motor assembly 200 is located on the side near the upper part of the middle part of the inner cavity of the housing 100 and is located above the oil pool 120. The motor assembly 200 includes a stator 210 and a rotor 220. The stator 210 is fixedly connected to the inner peripheral wall of the housing 100. Generally speaking, the stator 210 can be fixed to the inner peripheral wall of the housing 100 by welding or interference fit. The stator 210 is annular in structure and has a cavity penetrating in the middle along the up and down direction. The rotor 220 is arranged in the cavity in the middle of the stator 210 and rotates with the stator 210, that is, the stator 210 is arranged around the outer periphery of the rotor 220. The crankshaft 330 is fixedly connected to the rotor 220, and the crankshaft 330 is penetrated in the rotor 220 and the upper end of the crankshaft 330 protrudes from the upper end surface of the rotor 220, so the crankshaft 330 can rotate with the rotor 220.

[0045] Reference Figure 1 and Figure 2 As shown, it can be understood that the rotary compressor also includes a pump assembly 300, which is arranged in the inner cavity 110 of the housing 100 and is located below the motor assembly 200. The pump assembly 300 includes a cylinder, a crankshaft 330, an upper bearing 340, a lower bearing 350, a piston 360 and a muffler 380. The cylinder is fixedly connected to the inner wall of the compressor housing 100. For example, the cylinder is fixed to the inner wall of the housing 100 by welding, so that the cylinder connection is stable and the stability of the cylinder during operation is improved. It is easy to understand that the cylinder is provided with a compression chamber, and the piston 360 performs a cyclic reciprocating motion in the compression chamber.

[0046] Reference Figure 1 and Figure 2 As shown, it can be understood that the lower part of the crankshaft 330 passes through the muffler 380, the upper bearing 340, the cylinder and the lower bearing 350 from top to bottom, and the crankshaft 330 includes an eccentric portion 331, which is located at the lower part of the crankshaft 330, and the eccentric portion 331 is rotatably connected to the piston 360 of the cylinder. During operation, the rotor 220 rotates, and since the rotor 220 is fixedly connected to the crankshaft 330, the rotor 220 further drives the crankshaft 330 to rotate, thereby completing the compression of the refrigerant in the cylinder.

[0047] Reference Figure 1 and Figure 2As shown, it can be understood that the cylinder includes a first cylinder 310 and a second cylinder 320, the first cylinder 310 is located above the second cylinder 320, a partition 370 is provided between the first cylinder 310 and the second cylinder 320, an upper bearing 340 is provided above the first cylinder 310, and a lower bearing 350 is provided below the second cylinder 320, the upper bearing 340 and the lower bearing 350 jointly limit the first cylinder 310 and the second cylinder 320, the piston 360 of the first cylinder 310 is located in the compression chamber of the first cylinder 310; the piston 360 of the second cylinder 320 is located in the compression chamber of the second cylinder 320. The crankshaft 330 is provided with two eccentric parts 331 corresponding to the first cylinder 310 and the second cylinder 320, and the eccentric parts 331 of the two crankshafts 330 are rotatably connected with the piston 360 of the first cylinder 310 and the piston 360 of the second cylinder 320 respectively. Both the upper bearing 340 and the lower bearing 350 are provided with exhaust holes. The exhaust hole of the upper bearing 340 is connected to the compression chamber of the first cylinder 310, and the exhaust hole of the lower bearing 350 is connected to the compression chamber of the second cylinder 320. The muffler 380 is also provided with air holes. The liquid reservoir 600 is connected to the air inlet of the first cylinder 310 and the air inlet of the second cylinder 320 through two intake pipes, so that the liquid reservoir 600 supplies refrigerant to the compressor.

[0048] Reference Figure 1 and Figure 2 As shown, it can be understood that the crankshaft 330 is provided with a central oil hole 332, and the central oil hole 332 penetrates the crankshaft 330 in the up-down direction. The lower end of the central oil hole 332 is connected to the oil pool 120 below the housing 100, and the upper end of the central oil hole 332 is connected to the cavity of the housing 100 located above the motor assembly 200. The inner wall of the lower end of the central oil hole 332 is provided with a spiral oil blade, and the oil blade can rotate with the crankshaft 330. During the operation of the rotary compressor, the rotor 220 and the crankshaft 330 fixedly connected to the rotor 220 rotate through the interaction between the stator 210 and the rotor 220, and the eccentric portion 331 of the crankshaft 330 drives the piston 360 to rotate in the compression chamber of the cylinder, and the refrigerant is compressed into a high temperature and high pressure state, and then the compressed refrigerant is discharged from the exhaust holes of the lower bearing 350 and the upper bearing 340, and finally discharged from the exhaust pipe 130 at the top of the housing 100 to the refrigeration system. During the rotation of the crankshaft 330, the oil blades installed in the center oil hole 332 of the crankshaft 330 rotate together with the crankshaft 330. Under the rotation of the oil blades, the refrigerant oil at the bottom of the shell 100 enters the center oil hole 332 upward and is discharged from the upper end of the crankshaft 330, and then flows downward under the action of gravity. When the refrigerant oil flows back to the oil pool 120, it will pass through the motor assembly 200 and the pump body assembly 300, thereby lubricating the components of the motor assembly 200 and the components of the pump body assembly 300, effectively ensuring the lubrication of the internal parts of the compressor.

[0049] Reference Figure 1 and Figure 2 As shown, it can be understood that the rotary compressor also includes a support assembly 400, which is installed in the inner cavity 110 of the shell 100 and is located above the motor assembly 200. The support assembly 400 includes a bracket 410 and a motor bearing 420. The bracket 410 is fixed to the inner wall of the shell 100 of the rotary compressor by welding or riveting. The motor bearing 420 is installed on the bracket 410 and is sleeved on the upper end of the crankshaft 330. The motor bearing 420 is rotatably matched with the crankshaft 330. At the same time, the motor bearing 420 can provide support and positioning for the upper end of the crankshaft 330, which is beneficial to improve the coaxiality of the stator 210 and the rotor 220.

[0050] Reference Figure 1 and Figure 4 As shown, it can be understood that the oil-gas separator 500 is fixedly installed on the rotor 220 and is located between the rotor 220 and the bracket 410. The oil-gas separator 500 includes a stirring plate 510. The stirring plate 510 is arranged around the crankshaft 330 as the center, and there is a certain gap between the stirring plate 510 and the crankshaft 330 in the radial direction. The stirring plate 510 is extended toward the bracket 410 along the direction of the central axis of the crankshaft 330, that is, the stirring plate 510 is extended upward. Since the oil-gas separator 500 is fixedly connected to the rotor 220, the stirring plate 510 can rotate synchronously with the rotor 220. During the rotation of the stirring plate 510, the inner wall of the stirring plate 510 can stir the oil-gas mixture of the gaseous refrigerant and the liquid refrigerant oil above the rotor 220, so that the oil-gas mixture will rotate with the stirring plate 510. Under the action of centrifugal force, the refrigerant oil with a density greater than that of the gaseous refrigerant is thrown to the inner wall of the shell 100, and then flows downward along the inner wall of the shell 100 or the gap between the components. During the reflux process, the refrigerant oil flows through the motor assembly 200 and the pump body assembly 300, and finally flows back to the oil pool 120 at the bottom of the shell 100. The gaseous refrigerant with a density smaller than that of the liquid refrigerant oil is discharged upward from the rotary compressor. Therefore, the oil-gas separator 500 can separate the liquid refrigerant oil and the gaseous refrigerant, enhance the oil-gas separation effect, thereby reducing the oil discharge amount, and at the same time make the refrigerant oil reflux to lubricate the components in the shell 100, and finally fall back to the oil pool 120, so that the liquid level of the oil pool 120 remains stable.

[0051] It can be understood that by installing the oil-gas separator 500 on the rotor 220, the stirring plate 510 of the oil-gas separator 500 rotates with the rotor 220. During the rotation of the stirring plate 510, the refrigeration oil and the gaseous refrigerant will rotate along the inner wall of the stirring plate 510. As the stirring plate 510 rotates continuously, the liquid refrigeration oil with a density greater than that of the gaseous refrigerant is subjected to a greater centrifugal force, and the refrigeration oil will be thrown out of the stirring plate 510 and splashed toward the inner circumferential wall of the shell 100, and finally flow along the inner circumferential wall of the shell 100 to the inner cavity 110 of the shell 100. The refrigeration oil circulation is completed in the oil pool 120 at the bottom, and the gaseous refrigerant with a smaller density than the liquid refrigeration oil is subjected to a smaller centrifugal force. Under the action of high temperature and high pressure, the gaseous refrigerant will be discharged upward from the rotary compressor, thereby separating the oil and gas. The refrigerant and refrigeration oil in the cavity between the rotor 220 and the bracket 410 can be separated more fully, thereby enhancing the oil-gas separation effect, reducing the oil discharge amount, and keeping the liquid level of the oil pool 120 stable. The refrigeration oil can also lubricate the internal components of the shell 100 during the reflux process, thereby effectively ensuring the lubrication, sealing and heat dissipation performance of the compressor.

[0052] Reference Figure 1 and Figure 4 As shown, it can be understood that the oil-gas separator 500 also includes a fixing plate 520, the stirring plate 510 is connected to the outer peripheral edge of the fixing plate 520, and the stirring plate 510 extends toward the direction of the bracket 410, the fixing plate 520 is a circular plate structure, and an avoidance hole 521 is provided in the middle of the fixing plate 520, and the crankshaft 330 is passed through the avoidance hole 521 of the fixing plate 520, and the fixing plate 520 can be fixed to the upper end surface of the rotor 220 by screw connection or riveting, so that the oil-gas separator 500 is firmly fixed to the upper end surface of the rotor 220, increasing the contact area between the oil-gas separator 500 and the rotor 220, and the oil-gas separator 500 is close to the rotor 220 and installed more firmly, thereby improving the installation stability and enabling the rotary compressor to run smoothly.

[0053] Reference Figure 1 and Figure 4 As shown, it can be understood that the fixing plate 520 is provided with a plurality of fixing holes 522, and the plurality of fixing holes 522 are arranged at intervals in the direction around the central axis. Specifically, six fixing holes 522 are provided, and the six fixing holes 522 are arranged at equal intervals in the circumferential direction with the avoidance hole 521 of the fixing plate 520 as the center, and the upper end surface of the rotor 220 is provided with mounting holes corresponding to the fixing holes 522. A fastener is connected between the fixing plate 520 and the rotor 220, and the fastener is passed through the fixing hole 522. The fastener can be a screw or a rivet, and the screw or the rivet passes through the fixing hole 522 to fix the fixing plate 520 on the rotor 220, so that the fixing plate 520 is firmly fixed to the upper end surface of the rotor 220.

[0054] Reference Figure 1 and Figure 4 As shown, it can be understood that the fixed plate 520 is also provided with a through hole 523, and the rotor 220 is provided with a rotor channel 221. The rotor channel 221 passes through both ends of the rotor 220 along the direction of the central axis. The through hole 523 is connected to the rotor channel 221. The gaseous refrigerant compressed into high temperature and high pressure in the compression chamber of the cylinder will rise along the rotor channel 221 and be discharged to between the fixed plate 520 and the support assembly 400 through the through hole 523. The gaseous refrigerant will form an oil-gas mixture with the liquid refrigerant oil. The stirring plate 510 immediately stirs the oil-gas mixture to separate the refrigerant oil from the oil-gas mixture, thereby realizing oil-gas separation.

[0055] Reference Figure 1 and Figure 4 As shown, it can be understood that the maximum outer diameter of the oil-gas separator 500 is less than or equal to the maximum outer diameter of the rotor 220, that is, the maximum outer diameter of the stirring plate 510 is less than or equal to the maximum outer diameter of the rotor 220. If the maximum outer diameter of the stirring plate 510 is larger than the maximum outer diameter of the rotor 220, but smaller than the inner diameter of the stator 210, the stirring plate 510 may interfere with the stator 210 during rotation, and there is a risk of collision. Therefore, making the maximum outer diameter of the oil-gas separator 500 less than or equal to the maximum outer diameter of the rotor 220 can avoid interference between the oil-gas separator 500 and the stator 210. At the same time, when the maximum outer diameter of the stirring plate 510 is the same as the maximum outer diameter of the rotor 220, the inner wall of the stirring plate 510 can have a larger side area when the extended length of the stirring plate 510 remains unchanged, so that the stirring plate 510 can stir more oil-gas mixture. Because the oil-gas separator 500 is fixedly connected to the rotor 220, the angular velocity of the oil-gas separator 500 is equal to the angular velocity of the rotor 220. When the rotation speed of the rotor 220 is fixed, the larger the outer diameter of the oil-gas separator 500, the greater the linear velocity, the greater the centrifugal force on the oil-gas mixture, and it is easier to separate the liquid refrigerant oil from the oil-gas mixture, thereby enhancing the oil-gas separation effect. The remaining gaseous refrigerant in the oil-gas mixture will continue to be discharged upward from the compressor. Since the liquid refrigerant oil is separated more thoroughly in the oil-gas mixture, the oil discharge amount of the compressor is reduced, and the separated refrigerant oil flows back to the oil pool 120, so that the liquid level of the oil pool 120 remains stable.

[0056] In addition, the maximum outer diameter of the oil-gas separator 500 is made larger than twice the maximum distance between the inner wall of the rotor channel 221 and the central axis of the crankshaft 330 along the radial direction of the crankshaft 330, so that the mixture of refrigerant and refrigeration oil discharged from the upper end opening of the rotor channel 221 is located in the space surrounded by the stirring plate 510 to perform oil-gas separation.

[0057] Reference Figure 1 and Figure 4As shown, it can be understood that the stator 210 includes a first core 211 and a coil 212, the coil 212 is wound around the first core 211 and protrudes from the upper end of the first core 211, and the coil 212 is a winding installed on the stator 210, that is, a copper wire wound on the stator 210. The upper end surface of the first core 211 is a first wall 2111, the upper end surface of the coil 212 is a second wall 2121, and the upper end surface of the stirring plate 510 close to the bracket 410 is a fourth wall 511. Along the central axis direction of the crankshaft 330, the second wall 2121 is higher than the first wall 2111, and the fourth wall 511 is lower than the second wall 2121, that is, the upper end of the coil 212 is higher than the upper end of the first core 211 and the upper end of the stirring plate 510, and the upper end surface of the stirring plate 510 is higher than the upper end surface of the first core 211. A gap is left between the bracket 410 and the coil 212. The stirring plate 510 that rotates with the rotor 220 separates the oil-gas mixture, and the separated refrigerant oil will be thrown toward the inner wall of the shell 100 along the gap between the bracket 410 and the coil 212 in a direction away from the crankshaft 330, thereby realizing oil-gas separation.

[0058] Reference Figures 1 to 3 As shown, it can be understood that the lower end surface of the bracket 410 close to the stator 210 is the third wall 411, and the minimum distance between the third wall 411 and the first wall 2111 is defined as H. 1 , it can also be understood that along the central axis direction of the crankshaft 330, the minimum distance from the lower end surface of the bracket 410 to the upper end surface of the first core 211 is H 1 Define the minimum distance between the third wall 411 and the fourth wall 511 as H 2 , that is, H 2 The minimum distance from the upper end surface of the stirring plate 510 to the lower end surface of the bracket 410 is H. It is easy to understand that the lower end surface of the bracket 410 is parallel to the upper end surface of the first core 211, and the lower end surface of the bracket 410 is also parallel to the upper end surface of the stirring plate 510. That is, the distance from the lower end surface of the bracket 410 to the upper end surface of the stirring plate 510 is equal everywhere, and the distance is H. 2 , H 1 and H 2 Satisfy between: 0.51≤H 2 / H 1 ≤0.72.

[0059] It should be noted that, assuming H 1 unchanged, so that H 2 H 2 / H 1is less than 0.51, that is, the minimum distance between the lower end surface of the bracket 410 and the upper end surface of the first core 211 remains unchanged, and the upper end surface of the stirring plate 510 becomes higher, so that the minimum distance from the upper end surface of the stirring plate 510 to the lower end surface of the bracket 410 becomes smaller, and the height of the stirring plate 510 becomes higher, so that the axial stirring range of the oil-gas mixture by the stirring plate 510 becomes larger, resulting in an excessively fast stirring speed of the refrigerant. The high-speed refrigerant carries the refrigeration oil into the refrigeration system through the exhaust pipe 130, resulting in an increase in the amount of oil discharged. Assuming H 1 unchanged, so that H 2 Increases so that H 2 / H 1 Greater than 0.72, that is, the minimum distance between the lower end face of the bracket 410 and the upper end face of the first iron core 211 remains unchanged, the upper end face of the stirring plate 510 becomes lower, so that the minimum distance between the upper end face of the stirring plate 510 and the lower end face of the bracket 410 becomes larger, the axial stirring range of the stirring plate 510 during rotation is small, the stirring speed of the oil-gas mixture rotating with the stirring plate 510 is small, the centrifugal force is insufficient, the liquid refrigerant oil is difficult to separate from the oil-gas mixture, and the oil-gas separation effect is poor.

[0060] Reference Figure 3 and 5 As shown, the minimum distance between the upper end surface of the first core 211 and the lower end surface of the bracket 410 (ie, H 1 ), the minimum distance between the lower end surface of the bracket 410 and the upper end surface of the stirring plate 510 (i.e., H 2 ) satisfies 0.51≤H 2 / H 1 ≤0.72, which enables the compressor to reduce the amount of oil discharged while also achieving better oil-gas separation effect, refer to Figure 5 , when H 2 / H 1 =0.51, the relative height of the oil level is about 0.72 (the relative height of the oil level is the ratio of the actual liquid level to the theoretical maximum liquid level). 2 / H 1 =0.6 The relative height of the oil level is 0.8. When H 2 / H 1 =0.72 The relative height of the oil level is about 0.73, Figure 5 As can be seen in 1 and H 2 When the ratio is in the range of 0.51 to 0.72, the oil-gas separation effect of the oil-gas mixture is good, the separation effect can be enhanced, more refrigerant oil flows back to the oil pool 120, the oil discharge amount is reduced, the liquid level of the oil pool 120 remains stable, and the relative height of the oil level will be maintained in the range of 0.72 to 0.8.

[0061] Reference Figures 1 to 3As shown, it can be understood that the upper end surface of the coil 212 is higher than the upper end surface of the first core 211. Along the central axis direction of the crankshaft 330, the maximum distance between the upper end surface of the coil 212 and the upper end surface of the first core 211 is defined as H. 3 , that is, the maximum distance from the second wall 2121 to the first wall 2111 is H 3 , H 3 and H 1 Satisfy 0.8≤H 3 / H 1 ≤0.95.

[0062] It should be noted that, assuming H 1 unchanged, so that H 3 Increases so that H 3 / H 1 is greater than 0.95, that is, the minimum distance from the lower end surface of the bracket 410 to the first core 211 remains unchanged, and the height of the upper end surface of the coil 212 becomes higher, which will reduce the gap between the upper end surface of the coil 212 and the lower end surface of the bracket 410. When the refrigerant oil passes through the narrow gap, the regional velocity will be too large, and the oil droplets will directly impact the wall surface of the shell 100 and become broken refrigerant oil beads, resulting in the refrigerant oil not directly hanging on the wall surface of the shell 100. The refrigerant carries the refrigerant oil beads into the refrigeration system from the exhaust pipe 130, increasing the oil discharge amount. Assuming H 3 unchanged, so that H 1 Increases so that H 3 / H 1 Less than 0.8, that is, the minimum distance from the upper end surface of the coil 212 to the upper end surface of the first core 211 remains unchanged, and the lower end surface of the bracket 410 becomes higher. The higher lower end surface of the bracket 410 means that the overall height of the bracket 410 becomes higher, and the bracket 410 will occupy more upper space of the shell 100, affecting the separation effect of the upper cavity, resulting in insufficient oil-gas separation, causing more refrigerant oil to enter the refrigeration system from the exhaust pipe 130, increasing the oil discharge volume, and reducing the refrigerant oil level in the compressor oil pool 120.

[0063] Reference Figure 3 and Figure 6 As shown, the minimum distance between the upper end surface of the first core 211 and the lower end surface of the bracket 410 (ie, H 1 ), and the maximum distance between the upper end surface of the coil 212 and the upper end surface of the first core 211 (i.e., H 3 ) satisfies 0.8≤H 3 / H 1 ≤0.95, which enables the compressor to reduce the amount of oil discharged while also achieving better oil-gas separation effect, refer to Figure 6 , when H 3 / H 1 =0.8 The relative height of the oil level is 0.7. When H 3 / H1 =0.9 The relative height of the oil level is 0.8. When H 3 / H 1 =0.95 The relative height of the oil level is 0.7, Figure 6 As can be seen in 3 and H 1 When the ratio is in the range of 0.8 to 0.95, the oil-gas separation effect of the oil-gas mixture is good, the oil-gas separation effect is enhanced, more refrigerant oil flows back to the oil pool 120, the oil discharge amount is reduced, the liquid level of the oil pool 120 remains stable, and the relative height of the oil level will be maintained in the range of 0.7 to 0.9.

[0064] Reference Figures 1 to 3 As shown, it can be understood that the minimum distance H between the lower end surface of the bracket 410 and the upper end surface of the first core 211 is 1 The maximum distance H between the upper end surface of the coil 212 and the upper end surface of the first core 211 3 Satisfaction: H 1 -H 3 ≥2mm, that is, the distance from the third wall 411 to the second wall 2121 is greater than or equal to 2mm, and the gap between the upper end surface of the coil 212 and the lower end surface of the bracket 410 is further limited. Because the coil has a certain voltage when the compressor is running, the gap between the upper end surface of the coil 212 and the lower end surface of the bracket 410 is greater than 2mm, which can prevent electric shock between the coil 212 and the bracket 410, thereby allowing the compressor to operate normally.

[0065] The refrigeration device of the second embodiment of the utility model comprises the rotary compressor of the first embodiment of the utility model.

[0066] Since the refrigeration equipment adopts all the technical solutions of the rotary compressor of the above embodiment, it has at least all the beneficial effects brought by the technical solutions of the above embodiment.

[0067] The embodiments of the present invention are described in detail above in conjunction with the accompanying drawings, but the present invention is not limited to the above embodiments, and various changes can be made within the knowledge scope of ordinary technicians in the relevant technical field without departing from the purpose of the present invention.

Claims

1. A rotary compressor, characterized in that: include: a housing having an inner cavity; A motor assembly is disposed in the inner cavity, the motor assembly comprises a stator and a rotor, the stator is connected to the housing and is disposed around the outer circumference of the rotor; A crankshaft, fixedly connected to the rotor and protruding upward from the rotor; A support assembly is installed in the inner cavity and located above the motor assembly, the support assembly includes a bracket and a motor bearing, the bracket is fixedly connected to the inner wall of the shell, and the motor bearing is installed on the bracket and sleeved on the upper end of the crankshaft; The oil-gas separator is fixedly mounted on the rotor and located between the rotor and the bracket. The oil-gas separator includes a stirring plate, which is arranged around the outer circumference of the crankshaft and extends toward the bracket.

2. The rotary compressor according to claim 1, characterized in that: The oil-gas separation component also includes a fixed plate, the stirring plate is connected to the outer periphery of the fixed plate, the fixed plate is provided with an avoidance hole, the fixed plate is fixedly connected to the upper end of the rotor, and the crankshaft is passed through the avoidance hole.

3. The rotary compressor according to claim 2, characterized in that: The fixing plate is provided with a plurality of fixing holes, and the plurality of fixing holes are arranged at intervals along a direction surrounding the central axis of the crankshaft. A fastener is connected between the fixing plate and the rotor, and the fastener is passed through the fixing holes.

4. The rotary compressor according to claim 2, characterized in that: The fixing plate is further provided with a through hole, and the rotor is provided with a rotor channel. The rotor channel penetrates through both ends of the rotor along the direction of the central axis of the crankshaft, and the through hole is communicated with the rotor channel.

5. The rotary compressor according to claim 4, characterized in that: The maximum outer diameter of the oil-gas separation element is greater than twice the maximum distance between the inner wall of the rotor channel and the central axis of the crankshaft, and is less than or equal to the maximum outer diameter of the rotor.

6. The rotary compressor according to claim 1, characterized in that: The stator includes a first core and a coil, the coil is wound around the first core and protrudes from the upper end of the first core, and along the direction of the central axis of the crankshaft, the upper end of the coil is higher than the upper end of the stirring plate.

7. The rotary compressor according to claim 6, characterized in that: Along the direction of the central axis of the crankshaft, the minimum distance between the bracket and the first iron core is H1, and the minimum distance between the bracket and the stirring plate is H2, satisfying: 0.51≤H2 / H1≤0.

72.

8. The rotary compressor according to claim 6, characterized in that: Along the direction of the central axis of the crankshaft, the minimum distance between the bracket and the first iron core is H1, and the maximum distance between the upper end of the coil and the first iron core is H3, satisfying: 0.8≤H3 / H1≤0.

95.

9. The rotary compressor according to claim 8, characterized in that: A minimum distance H1 between the bracket and the first core and a maximum distance H3 between the upper end of the coil and the first core satisfy: H1-H3≥2mm.

10. Refrigeration equipment, characterized in that Comprising a rotary compressor as claimed in any one of claims 1 to 9.

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