Compressor and refrigeration equipment

Abstract

The utility model provides a compressor and refrigeration equipment, and relates to the field of compressors. The rotor assembly comprises a rotor core and a rotating shaft, the rotor core is arranged in the stator assembly, and the rotating shaft penetrates through the rotor core; the pump assembly sleeves the rotating shaft; the bearing comprises a supporting part and a shaft sleeve, the supporting part is arranged on the side, close to the rotor core, of the pump assembly, the side, close to the rotor core, of the supporting part is provided with a first surface, and the shaft sleeve sleeves the rotating shaft and is connected with the supporting part; the silencer is arranged on the side, close to the rotor core, of the supporting part, a first exhaust hole is formed in the silencer, and the shaft sleeve penetrates through the first exhaust hole; the fan cover is arranged on one side of the rotor core close to the bearing; wherein the distance between the side, close to the rotor core, of the silencer and the first surface is a first distance, the distance between the side, close to the bearing, of the fan cover and the first surface is a second distance, and the difference value between the second distance and the first distance is larger than or equal to 1 mm and smaller than or equal to 4 mm.

Description

Technical Field

[0001] This utility model belongs to the field of compressor technology, specifically, it relates to a compressor and a refrigeration device. Background Technology

[0002] Currently, in related technologies, when a compressor operates at low temperatures, the refrigerant and lubricating oil inside the compressor are compressed by the compressor's pump body and move towards the top of the compressor through the through-holes on the rotor core. After separating above the rotor core, the refrigerant and lubricating oil flow back to the oil sump below the compressor via the stator cut edges and pump body cutouts. However, the lubricating oil flowing back through the stator cut edges and pump body cutouts impacts the refrigerant moving towards the top of the compressor, hindering the lubricating oil return flow. This results in the compressor's lubricating oil level falling below the standard, easily causing compressor wear. Utility Model Content

[0003] The present invention aims to solve at least one of the technical problems existing in the prior art or related technologies.

[0004] Therefore, the first aspect of this utility model proposes a compressor.

[0005] The second aspect of this utility model provides a refrigeration device.

[0006] In view of the above, the first aspect of this utility model provides a compressor, including a housing, a stator assembly, a rotor assembly, a pump assembly, a bearing, a silencer, and a fan shroud. The stator assembly is disposed within the housing; the rotor assembly includes a rotor core and a shaft, the rotor core being disposed within the stator assembly, and the shaft passing through the rotor core; the pump assembly is sleeved on the shaft; the bearing includes a support portion and a bushing, the support portion being disposed on the side of the pump assembly near the rotor core, the support portion having a first surface on the side near the rotor core, the bushing being sleeved on the shaft and connected to the support portion; the silencer being disposed on the side of the support portion near the rotor core, the silencer having a first exhaust port, and the bushing passing through the first exhaust port; the fan shroud being disposed on the side of the rotor core near the bearing; wherein, the distance between the side of the silencer near the rotor core and the first surface is a first distance, the distance between the side of the fan shroud near the bearing and the first surface is a second distance, and the difference between the second distance and the first distance is greater than or equal to 1 mm and less than or equal to 4 mm.

[0007] This utility model discloses a compressor comprising a housing, a stator assembly, a rotor assembly, a pump assembly, bearings, a silencer, and a fan shroud. The stator and rotor assemblies are housed within the housing, providing power output for the compressor's operation and enabling the compression and transport of media such as refrigerants, thus completing the compressor's working cycle. The housing encloses the compressor components, making the overall compressor structure more robust and reducing the risk of damage from external forces. The rotor assembly consists of a rotor core and a shaft. The shaft's design, passing through the rotor core, allows the rotor core to drive the shaft to rotate synchronously. Simultaneously, the pump assembly is fitted onto the shaft, allowing the shaft's rotation to drive the pump assembly, thereby compressing media such as refrigerants. The shaft is fixed and limited by a bushing, which is connected and fixed to a support, ensuring stable rotation of the shaft within the bushing. This guarantees the relative positional accuracy of the compressor components, ensuring normal operation and improving the compressor's reliability. The silencer has a first exhaust port, through which a bushing passes, forming a ring structure. Refrigerant can be discharged through this ring structure and then enter the through-holes on the rotor core via the shroud, ensuring that more refrigerant directly enters the through-holes. The surface of the support near the rotor core is designated as the first surface. The distance between the silencer near the rotor core and the first surface is designated as the first distance. The distance between the shroud near the bearing and the first surface is designated as the second distance. With a dimensional fit where the difference between the second and first distances is greater than or equal to 1 mm and less than or equal to 4 mm, combined with the silencer's ring structure, the safe distance and manufacturing tolerances between the silencer and the shroud are ensured. Simultaneously, more refrigerant and lubricating oil enter the upper cavity of the motor through the through-holes on the rotor core. Only a small amount of refrigerant and lubricating oil flows towards the top of the motor through the stator cut edges and pump body cutouts, reducing the resistance to lubricating oil backflow. After the refrigerant and lubricating oil separate above the rotor core, they flow back to the oil sump below the compressor through the stator cut edge and pump body cut. This reduces the resistance to lubricating oil return, improves the compressor's oil return effect, and increases the minimum oil level when the compressor starts at low temperatures. This reduces the risk of compressor wear, improves product reliability, and enhances the user experience.

[0008] Taking a compressor with refrigerant deposition as an example, when the compressor is shut down on the low-temperature outdoor side, the refrigerant gradually condenses into a liquid state and accumulates inside the compressor. When the refrigerant and lubricating oil have good compatibility, the lubricating oil and liquid refrigerant mix thoroughly. The lower the ambient temperature and the longer the deposition time, the more refrigerant dissolves in the lubricating oil. When the compressor is started at this time, the refrigerant in the lubricating oil is heated and flashes, carrying a large amount of lubricating oil out of the compressor. When the lubricating oil return is hindered, it can easily lead to a drop in the compressor oil level, increasing the risk of equipment wear, affecting product reliability, user experience, and the company's reputation.

[0009] Meanwhile, this utility model forms a ring structure by inserting a bushing through the first exhaust hole, which allows the refrigerant to be discharged directly through the ring structure and enter the through hole on the rotor core through the fan cover. This ensures that more refrigerant enters the rotor directly, reduces the resistance of the refrigerant to exhaust into the upper cavity of the motor, and improves the working efficiency of the compressor.

[0010] Specifically, the difference between the second distance and the first distance is 1 millimeter.

[0011] The difference between the second distance and the first distance is 4 millimeters.

[0012] The difference between the second distance and the first distance is 2 millimeters.

[0013] The difference between the second distance and the first distance is 2.5 millimeters.

[0014] The difference between the second distance and the first distance is 3 millimeters.

[0015] In addition, the compressor in the above-mentioned technical solution provided by this utility model may also have the following additional technical features:

[0016] In some technical solutions of this utility model, optionally, the outer diameter of the support part is the first diameter; the diameter of the first vent hole is the second diameter; the difference between the second diameter and the first diameter is greater than or equal to 0.3 mm and less than or equal to 0.8 mm.

[0017] In this technical solution, by setting the difference between the second diameter and the first diameter to be greater than or equal to 0.3 mm and less than or equal to 0.8 mm, the refrigerant is better expelled from the muffler and into the rotor.

[0018] Specifically, the smaller the difference between the second diameter and the first diameter, the greater the exhaust resistance. When the difference between the second diameter and the first diameter is 0.3 mm, the amount of refrigerant discharged through the stator slit and pump body slit is reduced, thereby reducing the resistance to lubricating oil return. The larger the difference between the second diameter and the first diameter, the faster the refrigerant can enter the through holes on the rotor core. When the difference between the second diameter and the first diameter is 0.8 mm, it ensures that the refrigerant discharged from the silencer enters the rotor flow at a faster speed, reducing the condensation of gaseous refrigerant in the lower cavity of the motor, reducing the risk of compressor wear, and improving product reliability.

[0019] Meanwhile, by adopting a design structure in which the diameter of the first exhaust hole is greater than or equal to the outer diameter of the support part, which is greater than or equal to 0.3 mm and less than or equal to 0.8 mm, this utility model reduces the probability of gaseous refrigerant condensing in the lower cavity of the motor, thereby reducing the amount of oil carried out of the compressor by the refrigerant, and also reducing the probability of the refrigerant flowing to the stator tangent, improving the oil return effect of the compressor, and increasing the minimum oil level for low-temperature start-up.

[0020] Specifically, the difference between the second diameter and the first diameter is 0.3 mm.

[0021] The difference between the second diameter and the first diameter is 0.8 mm.

[0022] The difference between the second diameter and the first diameter is 0.45 mm.

[0023] The difference between the second diameter and the first diameter is 0.55 mm.

[0024] The difference between the second diameter and the first diameter is 0.65 mm.

[0025] Optionally, in some technical solutions of this utility model, there is a gap between the inner wall of the first exhaust hole and the side wall of the bushing, and the gap is arranged in an annular shape along the circumference of the bushing.

[0026] In this technical solution, a bushing passes through the first exhaust port, and there is a gap between the inner wall of the first exhaust port and the side wall of the bushing. This gap is arranged in a ring shape along the circumference of the bushing, forming a ring structure. The refrigerant can be discharged through the gap of the ring structure and directly enter the through hole on the rotor core through the fan shroud, ensuring that more refrigerant directly enters the rotor, reducing the resistance of the refrigerant exhaust to the upper cavity of the motor, and improving the working efficiency of the compressor.

[0027] Optionally, in some technical solutions of this utility model, the compressor also includes a surrounding plate, which is disposed on the side of the rotor core away from the bearing and arranged in a ring shape along the circumference of the rotor core.

[0028] In this technical solution, the compressor is also equipped with a surrounding plate, which is arranged in a ring around the circumference of the rotor core to effectively separate gas and liquid, thereby improving the separation effect of the gas-liquid mixed refrigerant in the upper cavity of the motor.

[0029] Optionally, in some technical solutions of this utility model, the height of the enclosure plate in the axial direction of the compressor is greater than or equal to 10 mm and less than or equal to 15 mm.

[0030] In this technical solution, the height of the enclosure is set between 10 mm and 15 mm. The motor flow rate is adjusted by regulating the enclosure height. At 10 mm, sufficient airflow to the rotor is ensured, allowing more gaseous refrigerant to enter the upper motor cavity, reducing condensation of gaseous refrigerant in the lower motor cavity, lowering the risk of compressor wear, and improving product reliability and user experience. At 15 mm, excessive airflow prevents refrigerant from entering the upper motor cavity through the tangent or windings, thus preventing refrigerant condensation and improving compressor operational stability.

[0031] Meanwhile, by adopting a design structure in which the height of the enclosure is set between 10 mm and 15 mm, this utility model reduces the probability of gaseous refrigerant condensing in the lower cavity of the motor, thereby reducing the amount of oil carried out of the compressor by the refrigerant, ensuring the oil return effect of the compressor, and increasing the minimum oil level for low-temperature start-up.

[0032] Specifically, the height of the enclosure is 10 millimeters.

[0033] The height of the enclosure is 15 millimeters.

[0034] The height of the enclosure is 11 millimeters.

[0035] The height of the enclosure is 12.5 mm.

[0036] The height of the enclosure is 14 millimeters.

[0037] In some technical solutions of this utility model, optionally, the shroud includes a body and an end plate. The body is connected to the rotor core and is arranged in a ring shape along the circumference of the rotor core; the end plate is connected to the body and is provided with a second exhaust hole, which is arranged opposite to the first exhaust hole.

[0038] In this technical solution, the compressor body is fixedly connected to the rotor core and arranged in a ring around the circumference of the rotor core, so that the compressor body rotates simultaneously with the rotor core when the rotor core rotates. An end plate is connected to the compressor body, and a second exhaust port is provided on the end plate at a position relative to the first exhaust port. This allows the refrigerant, when discharged through the first exhaust port, to directly and more smoothly enter the through-hole on the rotor core through the second exhaust port, improving the refrigerant transfer efficiency and thus enhancing the compressor's performance.

[0039] In some technical solutions of this utility model, optionally, the diameter of the second exhaust hole is larger than the diameter of the first exhaust hole.

[0040] In this technical solution, the diameter of the second exhaust port is larger than that of the first exhaust port, allowing more refrigerant to enter the second exhaust port. This reduces the probability of refrigerant flowing to the stator tangent, improves the oil return effect of the compressor, increases the minimum oil level for low-temperature start-up of the compressor, further reduces the risk of compressor wear, and improves product reliability and user experience.

[0041] Optionally, in some technical solutions of this utility model, the main body is provided with a plurality of oil return holes that penetrate the end plate along the axial direction of the compressor, and the plurality of oil return holes are distributed circumferentially along the second exhaust hole.

[0042] In this technical solution, multiple oil return holes are provided on the end plate, and these multiple oil return holes are distributed circumferentially along the second exhaust hole. This allows the compressor to return oil through multiple oil return holes, reducing the probability of oil returning from the second exhaust hole, further improving the smoothness of refrigerant exhaust, increasing the compressor's working efficiency, and ensuring the reliability of the product.

[0043] Optionally, in some technical solutions of this utility model, the rotor core is provided with multiple through holes that extend along the axial direction. The multiple through holes are distributed circumferentially along the shaft, and the end of the through hole near the bearing is located on the inner side of the body.

[0044] In this technical solution, the rotor core is provided with multiple through holes running along the axial direction, allowing the refrigerant to be transferred to the upper cavity of the motor. Simultaneously, the multiple through holes are distributed circumferentially along the shaft, with the end of the through hole near the bearing located inside the main body. This allows the refrigerant to enter the second exhaust port and then pass through the through holes inside the main body into the upper cavity of the motor, thus facilitating refrigerant transfer and improving the compressor's operating efficiency.

[0045] Optionally, in some technical solutions of this utility model, the side wall surface of the bushing includes a guide surface, the guide surface is arranged obliquely along the axial direction of the compressor, and the guide surface extends from the side near the pump assembly to the side near the rotor core in a direction away from the inner wall of the first exhaust hole.

[0046] In this technical solution, the side wall of the bushing is provided with a guide surface, which can guide the refrigerant to move towards the fan shroud, so that more refrigerant can quickly enter the fan shroud and then enter the upper cavity of the motor through the through hole of the rotor core, thereby improving the working stability and efficiency of the compressor.

[0047] The second aspect of this utility model provides a refrigeration device, including a compressor as described in any of the above-described technical solutions. Therefore, this refrigeration device possesses all the beneficial effects of the compressor described in any of the above-described technical solutions.

[0048] In some technical solutions of this utility model, the compressor may optionally include a liquid receiver, a sealed housing, a piston, a lower bearing, a cylinder, an exhaust port, and a main housing.

[0049] In this technical solution, the compressor also includes a liquid receiver, a sealed housing, a piston, a lower bearing, and a cylinder. The liquid receiver is used for oil separation and to prevent liquid slugging in the compressor. The sealed housing, in conjunction with the casing, ensures an internal seal, preventing refrigerant leakage under high pressure. Simultaneously, the sealed housing and casing also make the overall compressor structure more robust, providing protection. The upper end of the rotating shaft is fixed by a bushing, and the lower end is fixed by a lower bearing. This design prevents the shaft from shifting during high-speed rotation, improving the stability of product operation. This invention uses the rotating shaft to drive the piston in reciprocating motion, compressing the refrigerant within the cylinder. After compression, the refrigerant is discharged through a silencer into the fan shroud, and then enters the upper chamber of the motor through multiple through holes in the rotor core, thus achieving the compressor's operating effect.

[0050] Additional aspects and advantages of this invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

[0051] The above and / or additional aspects and advantages of this utility model will become apparent and readily understood from the description of the embodiments taken in conjunction with the following drawings, in which:

[0052] Figure 1 This is a schematic diagram of the overall structure of a compressor according to an embodiment of the present invention;

[0053] Figure 2 This is one of the schematic diagrams of the compressor part structure according to an embodiment of the present invention;

[0054] Figure 3 This is a second schematic diagram of the compressor section structure according to an embodiment of the present invention;

[0055] Figure 4 This is a schematic diagram of a wind shield according to an embodiment of the present invention;

[0056] Figure 5 This is a schematic diagram showing the relationship between the distance from the muffler to the shroud and the oil level according to an embodiment of the present invention.

[0057] Figure 6 This is a schematic diagram showing the relationship between the difference between the second diameter and the first diameter and the oil level height according to an embodiment of the present invention.

[0058] Figure 7 This is a schematic diagram showing the relationship between the height of the enclosure panel and the oil level according to an embodiment of the present invention.

[0059] in, Figures 1 to 4 The correspondence between the reference numerals and component names in the attached drawings is as follows:

[0060] 100 Compressor, 110 Housing, 120 Stator Assembly, 130 Rotor Assembly, 132 Rotor Core, 134 Shaft, 136 Through Hole, 140 Pump Assembly, 150 Bearing, 152 Support, 154 Bushing, 156 First Surface, 160 Silencer, 162 First Exhaust Hole, 170 Fan Cover, 172 Body, 174 End Plate, 176 Second Exhaust Hole, 178 Oil Return Hole, 180 Inner Wall of First Exhaust Hole, 182 Side Wall of Bushing, 184 Clearance, 186 Guide Surface, 190 Enclosure, 210 Liquid Receiver, 220 Sealed Housing, 230 Piston, 240 Lower Bearing, 250 Cylinder, 260 Exhaust Port. Detailed Implementation

[0061] To better understand the above-mentioned objectives, features, and advantages of this utility model, the present utility model will be further described in detail below with reference to the accompanying drawings and specific embodiments. It should be noted that, unless otherwise specified, the embodiments and features described in these embodiments can be combined with each other.

[0062] Many specific details are set forth in the following description in order to provide a full understanding of the present invention. However, the present invention may also be implemented in other ways different from those described herein. Therefore, the scope of protection of the present invention is not limited to the specific embodiments disclosed below.

[0063] The following reference Figures 1 to 7 This invention describes a compressor 100 and a refrigeration device according to some embodiments of the present invention.

[0064] like Figure 1 , Figure 2 and Figure 3As shown, this utility model provides a compressor 100, including a housing 110, a stator assembly 120, a rotor assembly 130, a pump assembly 140, a bearing 150, a silencer 160, and a fan shroud 170. The stator assembly 120 is disposed within the housing 110; the rotor assembly 130 includes a rotor core 132 and a rotating shaft 134, with the rotor core 132 disposed within the stator assembly 120 and the rotating shaft 134 passing through the rotor core 132; the pump assembly 140 is sleeved on the rotating shaft 134; the bearing 150 includes a support portion 152 and a bushing 154, with the support portion 152 disposed on the side of the pump assembly 140 near the rotor core 132 and having a first surface 156 on the side near the rotor core 132; the bushing 154 is sleeved on the rotating shaft 134 and connected to the support portion 152; the silencer 160... The muffler 160 is located on the side of the support 152 near the rotor core 132. The muffler 160 is provided with a first exhaust port 162, and the bushing 154 passes through the first exhaust port 162. The fan shroud 170 is located on the side of the rotor core 132 near the bearing 150. The distance between the side of the muffler 160 near the rotor core 132 and the first surface 156 is the first distance H1. The distance between the side of the fan shroud 170 near the bearing 150 and the first surface 156 is the second distance H2. The difference between the second distance H2 and the first distance H1 is greater than or equal to 1 mm and less than or equal to 4 mm.

[0065] This utility model discloses a compressor 100, which includes a housing 110, a stator assembly 120, a rotor assembly 130, a pump assembly 140, a bearing 150, a silencer 160, and a fan shroud 170. The stator assembly 120 and rotor assembly 130 are housed within the housing 110, providing power output for the operation of the compressor 100 and enabling the compression and transport of media such as refrigerant, thus completing the compressor 100's working cycle. The housing 110 encloses the compressor 100 components, making the overall structure of the compressor 100 more robust and reducing the risk of damage from external forces. The rotor assembly 130 consists of a rotor core 132 and a rotating shaft 134. The design of the rotating shaft 134 penetrating the rotor core allows the rotor core to drive the rotating shaft 134 to rotate synchronously. Simultaneously, the pump assembly 140 is fitted onto the rotating shaft 134, so that the rotation of the rotating shaft 134 drives the pump assembly 140 to work, thereby achieving the function of compressing media such as refrigerant. The rotating shaft 134 is limited and fixed by the bushing 154, which is connected and fixed to the support part 152. This allows the rotating shaft 134 to rotate stably within the bushing 154, ensuring the relative positional accuracy of the components of the compressor 100, ensuring the normal operation of the compressor 100, and improving the reliability of the compressor 100. The silencer 160 is provided with a first exhaust port 162, and the bushing 154 passes through the first exhaust port 162, thus forming a ring structure. The refrigerant can be discharged through the ring structure of the silencer 160 and then enter the through hole 136 on the rotor core 132 through the fan shroud 170, ensuring that more refrigerant directly enters the rotor. The surface of the support 152 near the rotor core 132 is designated as the first surface 156. The distance between the side of the muffler 160 near the rotor core 132 and the first surface 156 is designated as the first distance H1. The distance between the side of the shroud 170 near the bearing 150 and the first surface 156 is designated as the second distance H2. With the difference between the second distance H2 and the first distance H1 being greater than or equal to 1 mm and less than or equal to 4 mm, combined with the ring structure of the muffler 160, the safe distance and manufacturing tolerance between the muffler 160 and the shroud 170 are ensured. At the same time, more refrigerant and lubricating oil are allowed to enter the upper cavity of the motor through the through hole 136 on the rotor core 132. Only a small amount of refrigerant and lubricating oil flows to the top of the motor through the stator cut edge and the pump body cut, reducing the resistance to lubricating oil backflow. After the refrigerant and lubricating oil separate above the rotor core 132, they flow back to the oil sump below the compressor through the stator cut edge and pump body cut. This reduces the resistance to lubricating oil return, improves the oil return effect of the compressor 100, and increases the minimum oil level of the compressor 100 during low-temperature start-up, thereby reducing the wear risk of the compressor 100 and improving the reliability of the product and the user experience.

[0066] Taking the refrigerant deposition-driven compressor 100 as an example, when compressor 100 is shut down on the low-temperature outdoor side, the refrigerant gradually condenses into a liquid state and accumulates inside compressor 100. When the refrigerant and lubricating oil have good compatibility, the lubricating oil and liquid refrigerant mix thoroughly. The lower the ambient temperature and the longer the deposition time, the more refrigerant dissolves in the lubricating oil. When compressor 100 is started at this time, the refrigerant in the lubricating oil is heated and flashes, carrying a large amount of lubricating oil out of compressor 100. When the lubricating oil return is hindered, it can easily cause the oil level in compressor 100 to drop, increasing the risk of equipment wear, affecting product reliability, user experience, and the company's reputation.

[0067] Meanwhile, the present invention forms a ring structure by passing the bushing 154 through the first exhaust hole 162, so that the refrigerant can be discharged from the ring structure and directly enter the through hole 136 on the rotor core 132 through the fan cover 170. This ensures that more refrigerant enters the rotor directly, reduces the resistance of the refrigerant to exhaust to the upper cavity of the motor, and improves the working efficiency of the compressor 100.

[0068] Specifically, such as Figure 5 As shown, the difference between the second distance H2 and the first distance H1 is greater than or equal to 1 mm and less than or equal to 4 mm, indicating that the oil level is relatively high.

[0069] Specifically, the difference between the second distance H2 and the first distance H1 is 1 mm.

[0070] The difference between the second distance H2 and the first distance H1 is 4 millimeters.

[0071] The difference between the second distance H2 and the first distance H1 is 2 millimeters.

[0072] The difference between the second distance H2 and the first distance H1 is 2.5 mm.

[0073] The difference between the second distance H2 and the first distance H1 is 3 millimeters.

[0074] Specifically, the axial direction in this application is Figure 1 The direction indicated by arrow A. The circumferential direction in this application is... Figure 4 The direction indicated by the middle arrow C.

[0075] This embodiment provides a compressor 100, which, in addition to the technical features of the above embodiments, further includes the following technical features.

[0076] like Figure 1 , Figure 2 , Figure 3 and Figure 6As shown, the outer diameter of the support portion 152 is the first diameter D1; the diameter of the first vent hole 162 is the second diameter D2; the difference between the second diameter D2 and the first diameter D1 is greater than or equal to 0.3 mm and less than or equal to 0.8 mm.

[0077] In this embodiment, by setting the difference between the second diameter D2 and the first diameter D1 to be greater than or equal to 0.3 mm and less than or equal to 0.8 mm, the refrigerant is better expelled from the muffler 160 into the rotor.

[0078] Specifically, the smaller the difference between the second diameter D2 and the first diameter D1, the greater the exhaust resistance. When the difference between the second diameter D2 and the first diameter D1 is equal to 0.3 mm, the amount of refrigerant discharged through the stator slit and pump body slit is reduced, thereby reducing the resistance to lubricating oil return. The larger the difference between the second diameter D2 and the first diameter D1, the faster the refrigerant can enter the through hole 136 of the rotor core 132. When the difference between the second diameter D2 and the first diameter D1 is 0.8 mm, it ensures that the refrigerant discharged from the silencer 160 enters the rotor flow more quickly, reducing the condensation of gaseous refrigerant in the lower cavity of the motor, reducing the wear risk of the compressor, and improving the reliability of the product.

[0079] Meanwhile, by adopting a design structure in which the diameter of the first exhaust hole 162 is greater than or equal to the outer diameter of the support part 152, which is greater than or equal to 0.3 mm and less than or equal to 0.8 mm, this utility model reduces the probability of gaseous refrigerant condensing in the lower cavity of the motor, thereby reducing the amount of oil carried out of the compressor 100 by the refrigerant, and also reducing the probability of the refrigerant flowing to the stator tangent, thus improving the oil return effect of the compressor 100 and increasing the minimum oil level for low-temperature start-up.

[0080] Specifically, such as Figure 6 As shown, the difference between the second diameter D2 and the first diameter D1 is greater than or equal to 0.3 mm and less than or equal to 0.8 mm, indicating a relatively high oil level.

[0081] Specifically, the difference between the second diameter D2 and the first diameter D1 is 0.3 mm.

[0082] The difference between the second diameter D2 and the first diameter D1 is 0.8 mm.

[0083] The difference between the second diameter D2 and the first diameter D1 is 0.45 mm.

[0084] The difference between the second diameter D2 and the first diameter D1 is 0.55 mm.

[0085] The difference between the second diameter D2 and the first diameter D1 is 0.65 mm.

[0086] This embodiment provides a compressor 100, which, in addition to the technical features of the above embodiments, further includes the following technical features.

[0087] like Figure 1 , Figure 2 and Figure 3 As shown, there is a gap 184 between the inner wall 180 of the first exhaust hole 162 and the side wall 182 of the bushing 154, and the gap 184 is arranged in a ring shape along the circumference of the bushing 154.

[0088] In this embodiment, the bushing 154 passes through the first exhaust port 162. A gap 184 exists between the inner wall 180 of the first exhaust port 162 and the side wall 182 of the bushing 154. This gap 184 is arranged in a ring shape along the circumference of the bushing 154, forming a ring structure. The refrigerant can be discharged through the gap 184 of the ring structure and directly enter the through-hole 136 on the rotor core 132 through the fan shroud 170, ensuring that more refrigerant directly enters the rotor, reducing the resistance to refrigerant exhaust to the upper cavity of the motor, and improving the working efficiency of the compressor 100.

[0089] This embodiment provides a compressor 100, which, in addition to the technical features of the above embodiments, further includes the following technical features.

[0090] like Figure 1 , Figure 2 and Figure 3 As shown, the compressor 100 also includes a surrounding plate 190, which is disposed on the side of the rotor core 132 away from the bearing 150 and is arranged in a ring along the circumference of the rotor core 132.

[0091] In this embodiment, the compressor 100 is also provided with a surrounding plate 190, which is arranged in a ring around the circumference of the rotor core 132 to effectively separate gas and liquid, thereby improving the separation effect of the gas-liquid mixed refrigerant in the upper cavity of the motor.

[0092] This embodiment provides a compressor 100, which, in addition to the technical features of the above embodiments, further includes the following technical features.

[0093] like Figure 1 , Figure 2 , Figure 3 and Figure 7 As shown, in the axial direction of the compressor 100, the height H3 of the enclosure 190 is greater than or equal to 10 mm and less than or equal to 15 mm.

[0094] In this embodiment, the height H3 of the enclosure 190 is set between 10 mm and 15 mm. The motor flow rate is adjusted by controlling the height of the enclosure 190. When the height is 10 mm, sufficient airflow to the rotor is ensured, allowing more gaseous refrigerant to enter the upper motor cavity, reducing condensation of the gaseous refrigerant in the lower motor cavity, lowering the risk of compressor wear, and improving product reliability and user experience. When the height is 15 mm, excessive airflow is prevented from causing refrigerant condensation after entering the upper motor cavity from the cut edge or windings, thus improving the operational stability of the compressor 100.

[0095] Meanwhile, by adopting a design structure in which the height H3 of the enclosure 190 is set between 10 mm and 15 mm, this utility model reduces the probability of gaseous refrigerant condensing in the lower cavity of the motor, thereby reducing the amount of oil carried out of the compressor 100 by the refrigerant, ensuring the oil return effect of the compressor 100, and increasing the minimum oil level for low-temperature start-up.

[0096] Specifically, such as Figure 7 As shown, the height H3 of the enclosure 190 is greater than or equal to 10 mm and less than or equal to 15 mm, and the oil level is relatively high.

[0097] Specifically, the height H3 of the enclosure is 10 millimeters.

[0098] The height H3 of the enclosure is 15 mm.

[0099] The height H3 of the enclosure is 11 mm.

[0100] The height H3 of the enclosure is 12.5 mm.

[0101] The height H3 of the enclosure is 14 mm.

[0102] This embodiment provides a compressor 100, which, in addition to the technical features of the above embodiments, further includes the following technical features.

[0103] like Figure 1 , Figure 2 and Figure 3 As shown, the shroud 170 includes a body 172 and an end plate 174. The body 172 is connected to the rotor core 132 and is arranged in a ring along the circumference of the rotor core 132; the end plate 174 is connected to the body 172 and is provided with a second exhaust hole 176, which is opposite to the first exhaust hole 162.

[0104] In this embodiment, the body 172 is fixedly connected to the rotor core 132 and arranged in a ring around the circumference of the rotor core 132, so that the body 172 rotates simultaneously with the rotor when the rotor core rotates. An end plate 174 is connected to the body 172, and a second exhaust port 176 is provided on the end plate 174 at a position relative to the first exhaust port 162. This allows the refrigerant to pass through the first exhaust port 162 and then directly enter the through hole 136 on the rotor core 132 more smoothly through the second exhaust port 176, improving the refrigerant transfer effect and thus enhancing the working efficiency of the compressor 100.

[0105] This embodiment provides a compressor 100, which, in addition to the technical features of the above embodiments, further includes the following technical features.

[0106] like Figure 1 , Figure 2 , Figure 3 and Figure 4 As shown, the diameter D3 of the second vent 176 is greater than the diameter D1 of the first vent 162.

[0107] In this embodiment, since the diameter D3 of the second exhaust port 176 is larger than the diameter D1 of the first exhaust port 162, more refrigerant enters the second exhaust port 176, reducing the probability of refrigerant flowing to the stator tangent, improving the oil return effect of the compressor 100, increasing the minimum oil level for low-temperature start-up of the compressor 100, further reducing the wear risk of the compressor, and improving the reliability of the product and the user experience.

[0108] This embodiment provides a compressor 100, which, in addition to the technical features of the above embodiments, further includes the following technical features.

[0109] like Figure 1 , Figure 2 and Figure 3 As shown, the main body 172 is provided with a plurality of oil return holes 178 that pass through the end plate 174 along the axial direction of the compressor 100, and the plurality of oil return holes 178 are distributed circumferentially along the second exhaust hole 176.

[0110] In this embodiment, a plurality of oil return holes 178 are provided on the end plate 174, and the plurality of oil return holes 178 are distributed circumferentially along the second exhaust hole 176, so that when the compressor 100 returns oil, it returns oil through the plurality of oil return holes 178, reducing the probability of oil returning through the second exhaust hole 176, further improving the smoothness of refrigerant exhaust, improving the working efficiency of the compressor 100, and ensuring the reliability of the product.

[0111] This embodiment provides a compressor 100, which, in addition to the technical features of the above embodiments, further includes the following technical features.

[0112] like Figure 1 , Figure 2 and Figure 3 As shown, the rotor core 132 is provided with a plurality of through holes 136 extending along the axial direction. The plurality of through holes 136 are distributed circumferentially along the shaft 134, and the end of the through hole 136 near the bearing 150 is located on the inner side of the body 172.

[0113] In this embodiment, the rotor core 132 is provided with a plurality of through holes 136 extending axially, allowing the refrigerant to be transferred to the upper cavity of the motor. Simultaneously, the plurality of through holes 136 are distributed circumferentially along the shaft 134, and the end of the through hole 136 near the bearing 150 is located inside the body 172. This allows the refrigerant to enter the second exhaust port 176 and then pass through the through holes 136 inside the body 172 into the upper cavity of the motor, thus facilitating refrigerant transfer and improving the operating efficiency of the compressor 100.

[0114] This embodiment provides a compressor 100, which, in addition to the technical features of the above embodiments, further includes the following technical features.

[0115] like Figure 1 , Figure 2 and Figure 3 As shown, the side wall surface 182 of the bushing 154 includes a guide surface 186, which is arranged obliquely along the axial direction of the compressor 100, and the guide surface 186 extends from the side near the pump assembly 140 to the side near the rotor core 132 toward the inner wall 180 away from the first exhaust port 162.

[0116] In this technical solution, the side wall 182 of the bushing 154 is provided with a guide surface 186, which can guide the refrigerant to move towards the fan shroud 170, so that more refrigerant can quickly enter the fan shroud 170 and then enter the upper cavity of the motor through multiple through holes 136 of the rotor core 132, thereby improving the working stability and efficiency of the compressor 100.

[0117] This utility model provides a refrigeration device, including a compressor 100 as described in any of the above embodiments. Therefore, this refrigeration device possesses all the beneficial effects of the compressor 100 as described in any of the above embodiments.

[0118] Specifically, refrigeration equipment includes refrigerators, air conditioners, freezers, wine cabinets, or display cases.

[0119] This embodiment provides a compressor 100, which, in addition to the technical features of the above embodiments, further includes the following technical features.

[0120] like Figure 1 , Figure 2 and Figure 3As shown, the compressor 100 also includes a liquid receiver 210, a sealing housing 220, a piston 230, a lower bearing 240, a cylinder 250, an exhaust port 260, and a main housing 110.

[0121] In this embodiment, the compressor 100 also includes a liquid receiver 210, a sealing housing 220, a piston 230, a lower bearing 240, an exhaust port 260, and a cylinder 250. The liquid receiver 210 is used for oil separation and to prevent liquid slugging in the compressor 100. The sealing housing 220, in conjunction with the housing 110, seals the interior of the compressor 100, preventing refrigerant leakage under high pressure. Simultaneously, the sealing housing 220 and housing 110 also make the overall structure of the compressor 100 more robust, providing protection for the compressor 100. The upper end of the rotating shaft 134 is fixed by a bushing 154, and the lower end is fixed by a lower bearing 240. This design prevents the rotating shaft 134 from shifting during high-speed rotation, improving the stability of product operation. This utility model uses a rotating shaft 134 to drive a piston 230 to reciprocate, compressing the refrigerant in a cylinder 250. After compression, the refrigerant is discharged through a muffler 160 and enters a fan shroud 170, then enters the upper cavity of the motor through multiple through holes 136 in the rotor core, thus achieving the working effect of the compressor 100.

[0122] This embodiment provides a compressor 100, which, in addition to the technical features of the above embodiments, further includes the following technical features.

[0123] Compressor 100 can be used in jet enthalpy-increasing compressors.

[0124] In the claims, description, and accompanying drawings of this utility model, the term "plural" refers to two or more objects. Unless otherwise explicitly defined, the terms "upper," "lower," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of describing this utility model and simplifying the description process, and are not intended to indicate or imply that the device or element referred to must have the described specific orientation, or be constructed and operated in a specific orientation. Therefore, these descriptions should not be construed as limitations on this utility model. The terms "connect," "install," "fix," etc., should be interpreted broadly. For example, "connect" can be a fixed connection between multiple objects, a detachable connection between multiple objects, or an integral connection; it can be a direct connection between multiple objects or an indirect connection between multiple objects through an intermediate medium. For those skilled in the art, the specific meaning of the above terms in this utility model can be understood based on the specific circumstances described above.

[0125] In the claims, description, and drawings of this utility model, the terms "one embodiment," "some embodiments," "specific embodiment," etc., refer to a specific feature, structure, material, or characteristic described in connection with that embodiment or example, which is included in at least one embodiment or example of this utility model. In the claims, description, and drawings of this utility model, the illustrative expressions of the above terms do 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 one or more embodiments or examples.

[0126] The above description is merely a preferred embodiment of this utility model and is not intended to limit the utility model. Various modifications and variations can be made to this utility model by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this utility model should be included within the protection scope of this utility model.

Claims

1. A compressor, characterized in that, include: case; A stator assembly disposed within the housing; A rotor assembly, comprising a rotor core and a shaft, wherein the rotor core is disposed within the stator assembly and the shaft passes through the rotor core; A pump assembly, wherein the pump assembly is sleeved on the rotating shaft; The bearing includes a support portion and a bushing. The support portion is disposed on the side of the pump assembly near the rotor core and has a first surface on the side near the rotor core. The bushing is sleeved on the rotating shaft and connected to the support portion. A muffler is provided on the side of the support near the rotor core, and the muffler is provided with a first exhaust hole, through which the bushing passes; A fan shroud is disposed on the side of the rotor core near the bearing; The distance between the side of the muffler closest to the rotor core and the first surface is the first distance, and the distance between the side of the shroud closest to the bearing and the first surface is the second distance. The difference between the second distance and the first distance is greater than or equal to 1 mm and less than or equal to 4 mm.

2. The compressor according to claim 1, characterized in that, The outer diameter of the support portion is the first diameter; The diameter of the first vent hole is the same as the second diameter; The difference between the second diameter and the first diameter is greater than or equal to 0.3 mm and less than or equal to 0.8 mm.

3. The compressor according to claim 1, characterized in that, There is a gap between the inner wall of the first vent hole and the side wall of the bushing, and the gap is arranged in a ring shape along the circumference of the bushing.

4. The compressor according to claim 1, characterized in that, Also includes: A surrounding plate is disposed on the side of the rotor core away from the bearing and is arranged in a ring shape along the circumference of the rotor core.

5. The compressor according to claim 4, characterized in that, Along the axial direction of the compressor, the height of the enclosure is greater than or equal to 10 mm and less than or equal to 15 mm.

6. The compressor according to claim 1, characterized in that, The wind shield includes: The body is connected to the rotor core and is arranged in a ring shape along the circumference of the rotor core; An end plate is connected to the body, and the end plate is provided with a second vent hole, which is disposed opposite to the first vent hole.

7. The compressor according to claim 6, characterized in that, The diameter of the second vent is larger than the diameter of the first vent.

8. The compressor according to claim 7, characterized in that, The main body is provided with a plurality of oil return holes that penetrate the end plate along the axial direction of the compressor, and the plurality of oil return holes are distributed circumferentially along the second exhaust hole.

9. The compressor according to claim 6, characterized in that, The rotor core is provided with a plurality of through holes that extend along the axial direction. The plurality of through holes are distributed circumferentially along the shaft. The end of the through hole near the bearing is located on the inner side of the body.

10. The compressor according to any one of claims 1 to 9, characterized in that, The sidewall of the bushing includes a guide surface that is inclined along the axial direction of the compressor and extends from the side near the pump assembly to the side near the rotor core toward the inner wall away from the first exhaust port.

11. A refrigeration device, characterized in that, Includes the compressor as described in any one of claims 1 to 10.

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