Compressor and refrigeration apparatus

Abstract

The application discloses a compressor and refrigeration equipment, and relates to the technical field of compressors. The compressor comprises a shell, a pump body assembly and a motor. The pump body assembly is arranged in the shell, the crankshaft of the pump body assembly is arranged in an upper muffler, an upper bearing, a first cylinder, a second cylinder and a lower bearing, the stator assembly of the motor is fixedly connected with the inner wall of the shell, and the rotor assembly is connected with the crankshaft. Since the lower balance block is too close to the upper muffler or the diameter of the lower balance block is too large, the disturbance to the refrigerant discharged from the lower muffler is increased, and the oil discharge rate is increased. By reasonably setting the value of LxH / (H1x D) in the range of 0.17 to 2.1, the disturbance of the lower balance block to the refrigerant can be reduced, the return of lubricating oil is facilitated, the oil discharge rate is reduced, the overall size of the compressor can be ensured to be not too large, and the compactness design of the compressor structure is facilitated.

Description

Technical Field

[0001] This invention relates to the field of compressor technology, and in particular to a compressor and refrigeration equipment. Background Technology

[0002] The compressor's pump assembly has multiple cylinders for multi-stage compression. The motor's rotor assembly has an exhaust path, and the stator assembly has a return circuit. The pump assembly discharges refrigerant mixed with lubricating oil, which flows upwards through the exhaust path. Most of the lubricating oil, driven by the rotor assembly's rotation, is thrown towards the inner wall of the housing, flowing downwards and returning to the oil sump through the return circuit. Due to the multiple cylinders, the crankshaft of the pump assembly rotates unevenly under the motor's drive. Therefore, a balance block is needed in the motor's rotor assembly to improve crankshaft smoothness. However, the displacement of each stage varies, and the cylinders differ in size. To achieve better balance, the balance block's mass and volume need to be increased, bringing it closer to the muffler's exhaust port. The increased disturbance to the exhaust during balance block rotation causes some refrigerant that should flow through the exhaust path to enter the return circuit, hindering lubricating oil return. This increases the compressor's oil discharge rate, leading to insufficient lubrication of the crankshaft and bearings, increased friction, and reduced lifespan. Summary of the Invention

[0003] The present invention aims to at least solve one of the technical problems existing in the prior art. To this end, the present invention proposes a compressor capable of reducing oil discharge rate.

[0004] The present invention also proposes a refrigeration device having the above-mentioned compressor.

[0005] A compressor according to a first aspect of the present invention includes: a housing; a pump assembly disposed within the housing, the pump assembly including a crankshaft, a first cylinder, a partition assembly, a second cylinder, an upper muffler, an upper bearing, and a lower bearing, the first cylinder and the second cylinder being respectively located between the upper bearing and the lower bearing, the first cylinder being located above the second cylinder and the upper end of the first cylinder being connected to the upper bearing, the partition assembly being connected between the first cylinder and the second cylinder, the upper muffler being connected to the upper end of the upper bearing, the lower bearing being connected to the lower end of the second cylinder, the crankshaft passing through the upper muffler, the upper bearing, the first cylinder, the second cylinder, and the lower bearing; and a motor disposed within the housing and located above the upper muffler. The motor includes a stator assembly and a rotor assembly. The stator assembly is annular and fixedly connected to the inner wall of the housing. The rotor assembly is located within the space formed by the stator assembly and connected to the crankshaft. The rotor assembly includes a lower balance block and a rotor. The lower balance block is connected to the lower end of the rotor. The end of the upper muffler facing the rotor assembly is the upper end face. The shortest distance between the lower end face of the rotor assembly and the upper end face of the upper muffler is L. The maximum distance between the inner top wall of the housing and the upper end face of the stator core of the stator assembly is H. The maximum height of the lower balance block is H1. The maximum distance from the rotation center of the lower balance block to the edge of the lower balance block along the radial direction of the crankshaft is D, satisfying: 0.17≤L×H / (H1×D)≤2.1.

[0006] The compressor according to embodiments of the present invention has at least the following beneficial effects:

[0007] By positioning the pump body assembly within the housing, the crankshaft of the pump body assembly passes through the upper muffler, upper bearing, first cylinder, second cylinder, and lower bearing. The stator assembly of the motor is fixedly connected to the inner wall of the housing, and the rotor assembly is connected to the crankshaft. Therefore, when the crankshaft rotates, it can compress the refrigerant in the second cylinder. The compressed refrigerant then enters the first cylinder for further compression, and then is discharged to the upper muffler, and then discharged from the pump body assembly. After being discharged from the pump body assembly, the refrigerant needs to pass through the rotor assembly and flow upwards, finally exiting the housing. The refrigerant is mixed with lubricating oil. When passing through the rotor assembly, the refrigerant and the mixed lubricating oil will rotate under the drive of the rotor. Since the lubricating oil is heavier than the refrigerant, it will be thrown towards the peripheral wall of the housing. Finally, most of the lubricating oil can flow back along the peripheral wall of the housing to the oil sump at the bottom, and a small portion of the lubricating oil enters the circulation loop with the refrigerant. If the lower balance block is too close to the upper muffler, or if the diameter of the lower balance block is too large, it will increase the disturbance to the refrigerant discharged from the lower muffler, thus increasing the oil discharge rate. While a larger distance H between the top wall of the casing and the stator core is more conducive to lubricating oil return, a large H will increase the height of the casing. Therefore, by reasonably setting the value of L×H / (H1×D) within the range of 0.17 to 2.1, the disturbance of the lower balance block to the refrigerant can be reduced, which is beneficial to lubricating oil return and thus reduces the oil discharge rate. At the same time, it can ensure that the overall size of the compressor is not too large, which is beneficial to the compact design of the compressor structure.

[0008] According to some embodiments of the present invention, the rotor includes a rotor core, the rotor core having a plurality of flow passages, the flow passages penetrating the rotor core axially, and the plurality of flow passages being arranged at intervals circumferentially along the rotor core; a plurality of flow guiding channels are formed between the stator assembly and the inner wall of the housing, the flow guiding channels penetrating the stator assembly axially, and the plurality of flow guiding channels being arranged at intervals circumferentially along the stator assembly.

[0009] According to some embodiments of the present invention, the rotor core is provided with mounting holes for the crankshaft to pass through. On the axial projection plane perpendicular to the crankshaft, the sum of the flow areas of all the flow holes is S1, the area between the outer contour line of the rotor core and the contour line of the mounting hole is S3, the cross-sectional area of ​​the stator core is S2, and the sum of the flow areas of all the flow channels is S4, satisfying: S1 / S3≥S2 / S4.

[0010] According to some embodiments of the present invention, the shortest distance L between the lower end face of the rotor assembly and the upper end face of the upper muffler satisfies: L≥5mm.

[0011] According to some embodiments of the present invention, the rotor is provided with a plurality of flow holes, the flow holes penetrating the rotor axially, and the rotor assembly further includes a lower shroud covering the lower balance block. The lower shroud includes a first base plate and a first surrounding edge, the first surrounding edge being connected to the edge of the first base plate and surrounding the lower balance block. The first base plate is provided with a through hole for the crankshaft to pass through, and the sidewall of the through hole and the sidewall of the crankshaft are spaced apart so that the refrigerant discharged by the upper muffler can pass through the lower shroud and enter the flow holes.

[0012] According to some embodiments of the present invention, along the axial direction of the crankshaft, the minimum height of the first perimeter is H2, and the maximum height of the lower balance block is H1, satisfying: 0.5×H1≤H2≤H1.

[0013] According to some embodiments of the present invention, the diameter of the largest inscribed circle of the through hole is D1, and the diameter of the smallest enclosing circle of the rotor assembly is D2, satisfying: 0.4≤D1 / D2≤0.7.

[0014] According to some embodiments of the present invention, the rotor assembly further includes an upper shroud and an upper balance block. The upper shroud includes a second base plate and a second surrounding edge. The second base plate is connected to the upper end of the rotor, and the second surrounding edge is connected to the edge of the second base plate and extends in a direction away from the rotor. The upper balance block is connected to the second base plate and is located within the space enclosed by the second surrounding edge.

[0015] According to some embodiments of the present invention, along the axial direction of the crankshaft, the minimum height of the second perimeter is H3, and the maximum height of the upper balance block is H4, satisfying: H3≥H4.

[0016] According to some embodiments of the present invention, the rotor assembly further includes a baffle and an upper balance block, the upper balance block being connected to the upper end of the rotor, the rotor having a plurality of flow passage holes, the flow passage holes penetrating the rotor axially, the baffle being connected to the upper end of the upper balance block, and an air outlet communicating with the flow passage holes being formed between the baffle and the rotor, the air outlet extending circumferentially along the rotor assembly.

[0017] According to some embodiments of the present invention, at least a portion of the edge of the baffle is provided with a flange, the flange extending in a direction away from the upper balance block.

[0018] According to some embodiments of the present invention, the height of the flange along the axial direction of the crankshaft is H5, satisfying: 1mm≤H5≤20mm.

[0019] A refrigeration device according to a second aspect of the present invention includes the compressor described in the above embodiments.

[0020] The refrigeration device according to embodiments of the present invention has at least the following beneficial effects:

[0021] The compressor using the first aspect embodiment has a pump body assembly located within the housing. The crankshaft of the pump body assembly passes through an upper muffler, an upper bearing, a first cylinder, a second cylinder, and a lower bearing. The stator assembly of the motor is fixedly connected to the inner wall of the housing, and the rotor assembly is connected to the crankshaft. Therefore, when the crankshaft rotates, it can compress the refrigerant in the second cylinder. The compressed refrigerant then enters the first cylinder for further compression, and is then discharged to the upper muffler and then out of the pump body assembly. After being discharged from the pump body assembly, the refrigerant needs to pass through the rotor assembly and flow upwards before finally being discharged from the housing. The refrigerant is mixed with lubricating oil. When passing through the rotor assembly, the refrigerant and the mixed lubricating oil will rotate under the drive of the rotor. Since the lubricating oil is heavier than the refrigerant, it will be thrown towards the peripheral wall of the housing. Finally, most of the lubricating oil can flow back along the peripheral wall of the housing to the oil sump at the bottom, while a small portion of the lubricating oil enters the circulation loop along with the refrigerant. If the lower balance block is too close to the upper muffler, or if the diameter of the lower balance block is too large, it will increase the disturbance to the refrigerant discharged from the lower muffler, thus increasing the oil discharge rate. While a larger distance H between the top wall of the casing and the stator core is more conducive to lubricating oil return, a large H will increase the height of the casing. Therefore, by reasonably setting the value of L×H / (H1×D) within the range of 0.17 to 2.1, the disturbance of the lower balance block to the refrigerant can be reduced, which is beneficial to lubricating oil return and thus reduces the oil discharge rate. At the same time, it can ensure that the overall size of the compressor is not too large, which is beneficial to the compact design of the compressor structure.

[0022] Additional aspects and advantages of the 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

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

[0024] Figure 1 This is a cross-sectional schematic diagram of a compressor according to an embodiment of the present invention;

[0025] Figure 2 This is a cross-sectional view of a compressor according to an embodiment of the present invention;

[0026] Figure 3 This is a cross-sectional schematic diagram of a rotor assembly according to an embodiment of the present invention;

[0027] Figure 4 This is a cross-sectional schematic diagram of a rotor assembly according to another embodiment of the present invention;

[0028] Figure 5 This is a graph showing the relationship between the oil extraction rate and the value of the formula L×H / (H1×D) according to an embodiment of the present invention.

[0029] Figure label:

[0030] Compressor 1000;

[0031] Shell 100; Exhaust pipe 110; Upper shell 120; Middle shell 130; Lower shell 140;

[0032] Pump body assembly 200; crankshaft 210; upper muffler 220; upper bearing 230; first cylinder 240; first piston 241; baffle assembly 250; second cylinder 260; second piston 261; lower bearing 270; lower muffler 280; refrigerant passage 290;

[0033] Motor 300; Stator assembly 310; Stator core 311; Sleeve 312; Guide channel 313; Rotor assembly 320; Rotor core 321; Flow hole 322; Mounting hole 323; Lower balance block 330; Lower air shroud 340; First base plate 341; Through hole 3411; First surrounding edge 342; Upper balance block 350; Upper air shroud 360; Second base plate 361; Second surrounding edge 362; Baffle 370; Flanged edge 371; Air outlet 373;

[0034] Liquid storage tank 400; air inlet pipe 410. Detailed Implementation

[0035] Embodiments of the present invention are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention, and should not be construed as limiting the present invention.

[0036] In the description of this invention, it should be understood that the orientation descriptions, such as up, down, front, back, left, right, etc., indicating the orientation or positional relationship, are based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this invention and simplifying the description, and are not intended to indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this invention.

[0037] In the description of this invention, "several" means one or more, "more than" means two or more, "greater than," "less than," and "exceeding" are understood to exclude the stated number, while "above," "below," and "within" are understood to include the stated number. The use of "first" and "second" in the description is merely for distinguishing technical features and should not be construed as indicating or implying relative importance, or implicitly indicating the number of indicated technical features, or implicitly indicating the order of the indicated technical features.

[0038] In the description of this invention, unless otherwise explicitly defined, terms such as "set up," "install," and "connect" should be interpreted broadly, and those skilled in the art can reasonably determine the specific meaning of the above terms in this invention in conjunction with the specific content of the technical solution.

[0039] Reference Figure 1 , Figure 2 and Figure 3 As shown, a compressor 1000 according to an embodiment of the present invention can be used in refrigeration equipment such as refrigerators and air conditioners. The compressor 1000 of this embodiment includes a housing 100, a pump assembly 200, a motor 300, and a liquid storage tank 400. An exhaust pipe 110 is provided at the upper end of the housing 100. The housing 100 includes an upper shell portion 120, a middle shell portion 130, and a lower shell portion 140 located at the upper end. The upper shell portion 120 is connected to the upper end of the middle shell portion 130, and the lower shell portion 140 is connected to the lower end of the middle shell portion 130. The inner cavity of the exhaust pipe 110 communicates with the inner cavity of the housing 100. The pump body assembly 200 is disposed inside the housing 100. The pump body assembly 200 includes a crankshaft 210, a first cylinder 240, a second cylinder 260, a partition assembly 250, an upper muffler 220, a lower muffler 280, an upper bearing 230, and a lower bearing 270. The upper bearing 230 is fixedly connected to the inner wall of the housing 100. The lower bearing 270 is spaced below the upper bearing 230. The upper muffler 220 is connected to the upper end of the upper bearing 230. The first cylinder 240 and the second cylinder 260 are located between the upper bearing 230 and the lower bearing 270, and the second cylinder 260 is located at the lower end of the first cylinder 240. The lower end of the first cylinder 240 is connected to the upper bearing 230, and the upper end of the second cylinder 260 is connected to the lower bearing 270. The partition assembly 250 is connected between the first cylinder 240 and the second cylinder 260. The partition assembly 250 includes an upper partition connected to the lower end of the first cylinder 240 and a lower partition connected to the upper end of the second cylinder 260.

[0040] The lower muffler 280 is connected to the lower end of the lower bearing 270. The crankshaft 210 passes through the upper muffler 220, the upper bearing 230, the first cylinder 240, the baffle assembly 250, the second cylinder 260, and the lower bearing 270. A first piston 241 and a second piston 261 are respectively mounted on the crankshaft 210. The first piston 241 is located in the compression chamber of the first cylinder 240, and the second piston 261 is located in the compression chamber of the second cylinder 260. The liquid storage tank 400 is located outside the housing 100 and is connected to the second cylinder 260 through the intake pipe 410. The pump body assembly 200 also has a refrigerant passage 290, which passes through the lower bearing 270, the second cylinder 260, and the baffle assembly 250. The refrigerant passage 290 connects the inner cavity of the lower muffler 280 and the compression chamber of the first cylinder 240.

[0041] The motor 300 is located inside the housing 100 and above the pump body assembly 200, and is drivenly connected to the crankshaft 210. The motor 300 includes a stator assembly 310 and a rotor assembly 320. The stator assembly 310 is annular and fixedly connected to the inner wall of the housing 100. A flow guide channel 313 is formed between the stator assembly 310 and the inner wall of the housing 100, and the flow guide channel 313 passes through both ends of the stator assembly 310 along the axial direction. The rotor assembly 320 is located within the space formed by the stator assembly 310 and is drivenly connected to the crankshaft 210. The rotor assembly 320 includes a rotor and a lower balance block 330. The rotor has a flow passage 322 that passes through the rotor axially and is configured to supply refrigerant flow. The lower balance block 330 is connected to the lower end of the rotor.

[0042] Among them, the end of the upper muffler 220 facing the rotor assembly 320 is the upper end face, the shortest distance between the lower end face of the rotor assembly 320 and the upper end face of the upper muffler 220 is L, the maximum distance between the inner top wall of the housing 100 and the upper end face of the stator core 311 of the stator assembly 310 is H, the maximum height of the lower balance block 330 is H1, and the maximum distance from the rotation center of the lower balance block 330 to the edge of the lower balance block 330 along the radial direction of the crankshaft 210 is D, satisfying: 0.17≤L×H / (H1×D)≤2.1.

[0043] Understandably, the refrigerant enters the compression chamber of the second cylinder 260 through the intake pipe 410 of the liquid storage tank 400. The rotor assembly 320 of the motor 300 drives the crankshaft 210 to rotate. When the crankshaft 210 rotates, it drives the second piston 261 to rotate in the second cylinder 260, thereby compressing the refrigerant in the second cylinder 260. The refrigerant discharged from the second cylinder 260 enters the lower muffler 280, and then enters the first cylinder 240 for compression through the refrigerant passage 290. The refrigerant after secondary compression is discharged to the upper muffler 220 and then discharged from the upper muffler 220. The refrigerant mixed with lubricating oil is discharged from the pump body assembly 200 and passes through the flow hole 322 of the rotor assembly 320. Under the rotation of the rotor assembly 320, the refrigerant and lubricating oil are driven to rotate, so that most of the lubricating oil is thrown towards the inner wall of the housing 100. The lubricating oil can flow downward along the inner wall of the housing 100 and return to the oil sump at the bottom of the housing 100 through the guide channel 313.

[0044] Because the higher the height of the lower balance block 330, the closer it is to the upper muffler 220. This means that if the shortest distance L between the lower end face of the rotor assembly 320 and the upper end face of the upper muffler 220 is too small, or if the diameter D of the lower balance block 330 is too large, it will increase the disturbance to the refrigerant discharged from the lower muffler 280. This will cause some of the refrigerant that should have been discharged from the flow holes 322 of the rotor assembly 320 to flow into the guide channel 313, hindering the return flow of lubricating oil and increasing the oil discharge rate. A larger distance H between the top wall of the inner cavity of the housing 100 and the stator core 311 reduces the likelihood of lubricating oil being discharged directly from the housing 100 without separating from the refrigerant, thus facilitating the return flow of lubricating oil. However, a larger H will increase the height of the housing 100. For example, refer to... Figure 5 As shown, Figure 5 The horizontal axis represents the oil extraction rate, and the vertical axis represents the value of L×H / (H1×D). Figure 5 The dots in the graph represent the oil discharge rate corresponding to specific values ​​of L×H / (H1×D), and the dashed line represents the fitting curve for the discrete oil discharge rate, reflecting the trend of oil discharge rate variation with different values ​​of L×H / (H1×D). The values ​​of L×H / (H1×D) can be 0.17, 0.2, 0.3, 0.4, 0.8, 1.2, 1.6, 2.1, 2.4, 3, 3.6, etc. As the value of L×H / (H1×D) increases from 0 to 4, it can be seen that the oil discharge rate first decreases and then increases overall. Therefore, by reasonably setting the value of L×H / (H1×D) within the range of 0.17 to 2.1, the disturbance of the refrigerant by the lower balance block 330 can be reduced, which is beneficial to the return of lubricating oil, thereby reducing the oil discharge rate. At the same time, it can also ensure that the overall size of the compressor 1000 is not too large, which is beneficial to the compact design of the compressor 1000 structure.

[0045] Reference Figure 2 As shown, in an embodiment of the present invention, the rotor includes a rotor core 321. The rotor core 321 is provided with a plurality of flow holes 322. The flow holes 322 penetrate the rotor core 321 axially and are configured to allow refrigerant flow. The plurality of flow holes 322 are arranged at intervals along the circumference of the rotor core 321. The stator assembly 310 includes a stator core 311 and a sleeve 312. The stator core 311 is connected to the inner side of the sleeve 312. The sleeve 312 is fixedly connected to the housing 100. A plurality of flow channels 313 are formed between the inner wall of the sleeve 312 and the housing 100. The flow channels 313 penetrate the stator assembly 310 axially and are configured to allow refrigerant flow. The plurality of flow channels 313 are arranged at intervals along the circumference of the stator assembly 310. By providing a plurality of flow holes 322 and a plurality of flow channels 313, it is beneficial for the refrigerant to be discharged through the rotor core 321, and it is also beneficial for the lubricating oil to return, thereby improving the discharge efficiency of the refrigerant and the return efficiency of the lubricating oil.

[0046] Reference Figure 2As shown, in an embodiment of the present invention, the rotor core 321 is provided with mounting holes 323 for the crankshaft 210 to pass through. On the axial projection plane perpendicular to the crankshaft 210, the sum of the flow areas of all the flow holes 322 is S1, the area between the outer contour line of the rotor core 321 and the contour line of the mounting hole 323 is S3, the cross-sectional area of ​​the stator core 311 is S2, and the sum of the flow areas of all the flow channels 313 is S4, satisfying: S1 / S3≥S2 / S4, for example, S1 / S3=S2 / S4, S1 / S3=1.2×S2 / S4, S1 / S3=1.5×S2 / S4, S1 / S3=2×S2 / S4, S1 / S3=2.5×S2 / S4. It is understandable that S1 / S3 reflects the proportion of the total area of ​​all flow holes 322 on the rotor core 321, while S2 / S4 reflects the proportion of the area of ​​the flow guide channel 313 on the stator core 311. When S1 / S3 < S2 / S4, that is, the flow area of ​​the flow holes 322 is small, while the flow area of ​​the flow guide channel 313 is large, which is not conducive to the refrigerant passing through the rotor assembly 320. Therefore, setting S1 / S3 ≥ S2 / S4 is beneficial for the refrigerant to pass through the flow holes 322 of the rotor assembly 320, thereby improving the refrigerant discharge efficiency. It should be noted that when measuring the values ​​of S1, S3, S2, and S4, the stator core 311, sleeve 312, rotor core 321, and other structures can be arranged vertically. The top contours of the stator core 311, sleeve 312, rotor core 321, and other structures can be obtained using a 2D scanner, and then the area can be calculated using relevant software.

[0047] Reference Figure 1 As shown, in the embodiment of the present invention, the shortest distance L between the lower end face of the rotor assembly 320 and the upper end face of the upper muffler 220 satisfies: L ≥ 5mm, for example, the value of L can be 5mm, 6mm, 7mm, 8mm, 10mm, etc. Since the lower end of the rotor assembly 320 is usually the lower balance block 330, and due to the irregular structure of the lower balance block 330, it has a significant impact on the disturbance of the refrigerant after rotation. When L is less than 5mm, the shortest distance L between the lower balance block 330 and the upper end face of the upper muffler 220 is too small, which will lead to increased disturbance to the refrigerant discharged from the lower muffler 280. This will cause some of the refrigerant that should be discharged from the flow hole 322 of the rotor assembly 320 to flow into the guide channel 313, hindering the return of lubricating oil and increasing the oil discharge rate. Therefore, designing L to be greater than or equal to 5mm can reduce the disturbance of the lower balance block 330 to the refrigerant, thereby reducing the oil discharge rate.

[0048] To further reduce the disturbance of the refrigerant by the lower balance block 330, refer to Figure 1 and Figure 3As shown in the embodiment of the present invention, the rotor assembly 320 further includes a lower shroud 340 covering the lower balance block 330, and the lower shroud 340 is cylindrical. The lower shroud 340 includes a first base plate 341 and a first surrounding edge 342. The first surrounding edge 342 is connected to the edge of the first base plate 341 and surrounds the lower balance block 330. The first base plate 341 has a through hole 3411 for the crankshaft 210 to pass through. The side wall of the through hole 3411 and the side wall of the crankshaft 210 are spaced apart so that the refrigerant discharged from the upper muffler 220 can pass through the lower shroud 340 and enter the flow hole 322. Since the lower shroud 340 is cylindrical and covers the lower balance block 330, when the lower shroud 340 rotates under the drive of the rotor assembly 320, the disturbance effect on the refrigerant is smaller than the disturbance effect on the lower balance block 330, which is conducive to the refrigerant entering the flow hole 322, thereby reducing the oil discharge rate. Therefore, by setting the lower hood 340, the lower balance block 330 can be closer to the upper silencer 220, which is beneficial to the compact design of the compressor 1000.

[0049] Reference Figure 2 As shown in the embodiment of the present invention, along the axial direction of the crankshaft 210, the minimum height of the first circumference 342 is H2, and the maximum height of the lower balance block 330 is H1, satisfying: 0.5×H1≤H2≤H1, which is equivalent to 0.5≤H2 / H1≤1. For example, the value of H2 / H1 is 0.5, 0.6, 0.7, 0.8, 0.9, 1, etc. It can be understood that when H2 / H1 is less than 0.5, the height of the first circumference 342 is relatively low, and it can only cover a small part of the lower balance block 330. When the lower balance block 330 rotates, the disturbance to the refrigerant is still relatively large, so the lower hood 340 is difficult to reduce the disturbance. When the H2 / H1 ratio is greater than 1, meaning the height of the first surrounding edge 342 is greater than the height of the lower balance block 330, the lower fan cover 340 cannot be installed due to assembly issues. Even if it could be installed, the first surrounding edge 342 would need to enclose the rotor core 321, leading to an increase in the outer diameter of the rotor assembly 320 and affecting the performance of the motor 300. Therefore, by rationally designing the H2 / H1 ratio to be within the range of 0.5 to 1, the lower fan cover 340 can effectively reduce disturbances while also facilitating assembly and improving the reliability of the motor 300.

[0050] Continue to refer to Figure 2As shown, in the embodiment of the present invention, the diameter of the largest inscribed circle of the through hole 3411 is D1. For example, when the through hole 3411 is a circular hole, the diameter of the largest inscribed circle of the through hole 3411 is the hole diameter of the through hole 3411. The diameter of the smallest enclosing circle of the rotor assembly 320 is D2, satisfying: 0.4≤D1 / D2≤0.7. For example, the value of D1 / D2 can be 0.4, 0.5, 0.7, 0.7, etc. When D1 / D2 is less than 0.4, the flow area of ​​the through hole 3411 is small, and the resistance of the refrigerant entering the flow hole 322 through the through hole 3411 is large, which is not conducive to the conduction of the refrigerant. When D1 / D2 is greater than 0.7, the hole diameter of the through hole 3411 is too large, and the lower shroud 340 is difficult to cover most of the structure of the lower balance block 330. The disturbance of the refrigerant by the lower balance block 330 increases, and the oil discharge rate increases. Therefore, by reasonably designing the ratio of D1 / D2 to be within the range of 0.4 to 0.7, the refrigerant intake resistance can be reduced, while the lower shroud 340 can be effectively wrapped to reduce the disturbance of the refrigerant by the lower balance block 330.

[0051] Reference Figure 3 As shown, in an embodiment of the present invention, the rotor assembly 320 further includes a baffle 370 and an upper balancing block 350, the upper balancing block 350 being connected to the upper end of the rotor. The baffle 370 is connected to the upper end of the upper balancing block 350, and an outlet 373 is formed between the baffle 370 and the rotor, communicating with the flow passage 322. The outlet 373 extends circumferentially along the rotor assembly 320. Therefore, the refrigerant discharged from the vent will flow radially towards the rotor assembly 320 under the guidance of the baffle 370. The lighter refrigerant can flow upwards, and finally be discharged from the housing 100 through the exhaust pipe 110. The lubricating oil mixed in the refrigerant is thrown onto the inner wall of the housing 100, thereby returning to the oil sump and reducing the oil discharge rate of the compressor 1000.

[0052] Continue to refer to Figure 3 As shown in the embodiment of the present invention, at least a portion of the edge of the baffle 370 is provided with a flange 371, which extends in a direction away from the upper balance block 350. For example, the flange 371 is provided only at the location of the upper balance block 350 on the baffle 370, thereby facilitating the positioning of the upper balance block 350. Alternatively, the flange 371 can also be constructed as a complete ring, with the appropriate solution selected according to the actual situation. By providing the flange 371, the baffle 370 can rotate under the drive of the rotor assembly 320, and therefore the flange 371 will also rotate, thereby further driving the nearby refrigerant to rotate, increasing the rotational speed of the refrigerant, which is beneficial for throwing the lubricating oil towards the side wall of the housing 100, improving the separation efficiency with the refrigerant, and thus reducing the oil discharge rate.

[0053] Continue to refer to Figure 3As shown in the embodiment of the present invention, the height of the flange 371 along the axial direction of the crankshaft 210 is H5, satisfying: 1mm ≤ H5 ≤ 20mm. For example, the value of H5 can be 1mm, 5mm, 8mm, 15mm, 20mm, etc. When H5 is less than 1mm, the height of the flange 371 is too short, making it difficult to drive the refrigerant to rotate. When H5 is greater than 20mm, the height of the flange 371 is too high, which can easily lead to unstable operation of the rotor assembly 320 and hinder the flow of refrigerant. Therefore, reasonably designing the height H5 of the flange 371 within the range of 1mm to 20mm can effectively drive the refrigerant to rotate, which is beneficial to the separation of refrigerant and lubricating oil and reduces the oil discharge rate.

[0054] Reference Figure 4 As shown, in another embodiment of the present invention, the rotor assembly 320 further includes an upper shroud 360 and an upper balance block 350. The upper shroud 360 includes a second base plate 361 and a second perimeter 362. The second base plate 361 is connected to the upper end of the rotor, and the second perimeter 362 surrounds the edge of the second base plate 361 and extends in a direction away from the rotor. The upper balance block 350 is connected to the second base plate 361 and is located within the space enclosed by the second perimeter 362. It is understood that the upper shroud 360 can rotate under the drive of the rotor assembly 320. Therefore, when the second perimeter 362 rotates, it will drive the nearby refrigerant to rotate, increasing the rotational speed of the refrigerant. This is beneficial for throwing the lubricating oil towards the side wall of the housing 100, improving the separation efficiency with the refrigerant, and thus reducing the oil discharge rate.

[0055] Continue to refer to Figure 4 As shown in the embodiment of the present invention, along the axial direction of the crankshaft 210, the minimum height of the second perimeter 362 is H3, and the maximum height of the upper balance block 350 is H4, satisfying: H3 ≥ H4. It can be understood that when H4 is less than H3, the height of the second perimeter 362 is relatively short, making it difficult to drive the refrigerant to rotate. Therefore, by designing H3 to be greater than or equal to H4, it is easier for the second perimeter 362 to continue driving the refrigerant to rotate, which is beneficial for throwing the lubricating oil towards the side wall of the housing 100, improving the separation efficiency with the refrigerant, and thus reducing the oil discharge rate.

[0056] A refrigeration device according to one embodiment of the present invention includes the compressor 1000 of the above embodiments. The refrigeration device can be an air conditioner, refrigerator, etc. The refrigeration device of this embodiment uses the compressor 1000 of the above embodiments. A pump assembly 200 is located inside a housing 100. The crankshaft 210 of the pump assembly 200 passes through an upper muffler 220, an upper bearing 230, a first cylinder 240, a second cylinder 260, and a lower bearing 270. The stator assembly 310 of the motor 300 is fixedly connected to the inner wall of the housing 100, and the rotor assembly 320 is connected to the crankshaft 210. Therefore, when the crankshaft 210 rotates, it can compress the refrigerant in the second cylinder 260. The compressed refrigerant then enters the first cylinder 240 for further compression, then is discharged to the upper muffler 220, and then discharged from the pump assembly 200. After being discharged from the pump assembly 200, the refrigerant needs to pass through the rotor assembly 320 and flow upwards before finally being discharged from the housing 100. The refrigerant is mixed with lubricating oil. When passing through the rotor assembly 320, the refrigerant and the mixed lubricating oil rotate under the drive of the rotor. Since the lubricating oil is heavier than the refrigerant, it is thrown towards the peripheral wall of the housing 100. Finally, most of the lubricating oil can flow back to the oil sump at the bottom along the peripheral wall of the housing 100, and a small part of the lubricating oil enters the circulation loop with the refrigerant. If the lower balance block 330 is too close to the upper muffler 220, or if the diameter of the lower balance block 330 is too large, it will increase the disturbance to the refrigerant discharged from the lower muffler 280 and increase the oil discharge rate. The larger the distance H between the top wall of the inner cavity of the housing 100 and the stator core 311, the more conducive it is to the return flow of lubricating oil. However, if H is too large, it will increase the height of the housing 100. Therefore, by reasonably setting the value of L×H / (H1×D) within the range of 0.17 to 2.1, the disturbance of the refrigerant by the lower balance block 330 can be reduced, which is conducive to the return of lubricating oil and thus reduces the oil discharge rate. At the same time, it can also ensure that the overall size of the compressor 1000 is not too large, which is conducive to the compact design of the compressor 1000 structure.

[0057] Since the refrigeration equipment adopts all the technical solutions of the compressor 1000 in the above embodiments, it has at least all the beneficial effects brought about by the technical solutions in the above embodiments, which will not be repeated here.

[0058] The embodiments of the present invention have been described in detail above with reference to the accompanying drawings. However, the present invention is not limited to the above embodiments. Within the scope of knowledge possessed by those skilled in the art, various changes can be made without departing from the spirit of the present invention.

Claims

1. A compressor, characterized in that, include: case; A pump body assembly is disposed within the housing. The pump body assembly includes a crankshaft, a first cylinder, a partition assembly, a second cylinder, an upper muffler, an upper bearing, and a lower bearing. The first cylinder and the second cylinder are respectively located between the upper bearing and the lower bearing. The first cylinder is located above the second cylinder, and the upper end of the first cylinder is connected to the upper bearing. The partition assembly is connected between the first cylinder and the second cylinder. The upper muffler is connected to the upper end of the upper bearing, and the lower bearing is connected to the lower end of the second cylinder. The crankshaft passes through the upper muffler, the upper bearing, the first cylinder, the second cylinder, and the lower bearing. An electric motor is disposed within the housing and located above the upper muffler. The electric motor includes a stator assembly and a rotor assembly. The stator assembly is annular and fixedly connected to the inner wall of the housing. The rotor assembly is located within the space formed by the stator assembly and connected to the crankshaft. The rotor assembly includes a lower balance block and a rotor. The lower balance block is connected to the lower end of the rotor. Wherein, the end of the upper muffler facing the rotor assembly is the upper end face, the shortest distance between the lower end face of the rotor assembly and the upper end face of the upper muffler is L, the maximum distance between the inner top wall of the housing and the upper end face of the stator core of the stator assembly is H, the maximum height of the lower balance block is H1, and the maximum distance from the rotation center of the lower balance block along the radial direction of the crankshaft to the edge of the lower balance block is D, satisfying: 0.17≤L×H / (H1×D)≤2.

1.

2. The compressor according to claim 1, characterized in that: The rotor includes a rotor core, which has multiple flow passages that penetrate the rotor core axially and are arranged at intervals along the circumference of the rotor core. A plurality of flow channels are formed between the stator assembly and the inner wall of the housing, which penetrate the stator assembly axially and are arranged at intervals along the circumference of the stator assembly.

3. The compressor according to claim 2, characterized in that: The rotor core is provided with mounting holes for the crankshaft to pass through. On the axial projection plane perpendicular to the crankshaft, the sum of the flow areas of all the flow holes is S1, the area between the outer contour line of the rotor core and the contour line of the mounting hole is S3, the cross-sectional area of ​​the stator core is S2, and the sum of the flow areas of all the flow channels is S4, satisfying: S1 / S3≥S2 / S4.

4. The compressor according to claim 1, characterized in that: The shortest distance L between the lower end face of the rotor assembly and the upper end face of the upper muffler satisfies: L≥5mm.

5. The compressor according to claim 1, characterized in that: The rotor is provided with multiple flow holes, which penetrate the rotor axially. The rotor assembly also includes a lower air shroud covering the lower balance block. The lower air shroud includes a first base plate and a first surrounding edge. The first surrounding edge is connected to the edge of the first base plate and surrounds the lower balance block. The first base plate is provided with a through hole for the crankshaft to pass through. The sidewall of the through hole and the sidewall of the crankshaft are spaced apart so that the refrigerant discharged from the upper muffler can pass through the lower air shroud and enter the flow holes.

6. The compressor according to claim 5, characterized in that: Along the axial direction of the crankshaft, the minimum height of the first circumference is H2, and the maximum height of the lower balance block is H1, satisfying: 0.5×H1≤H2≤H1.

7. The compressor according to claim 5, characterized in that: The diameter of the largest inscribed circle of the through hole is D1, and the diameter of the smallest enclosing circle of the rotor assembly is D2, satisfying: 0.4≤D1 / D2≤0.

7.

8. The compressor according to claim 1, characterized in that: The rotor assembly also includes an upper shroud and an upper balance block. The upper shroud includes a second base plate and a second surrounding edge. The second base plate is connected to the upper end of the rotor, and the second surrounding edge is connected to the edge of the second base plate and extends in a direction away from the rotor. The upper balance block is connected to the second base plate and is located within the space enclosed by the second surrounding edge.

9. The compressor according to claim 8, characterized in that: Along the axial direction of the crankshaft, the minimum height of the second perimeter is H3, and the maximum height of the upper balance block is H4, satisfying: H3≥H4.

10. The compressor according to claim 1, characterized in that: The rotor assembly further includes a baffle and an upper balance block. The upper balance block is connected to the upper end of the rotor. The rotor is provided with a plurality of flow holes. The flow holes penetrate the rotor axially. The baffle is connected to the upper end of the upper balance block. An air outlet is formed between the baffle and the rotor, communicating with the flow holes. The air outlet extends circumferentially along the rotor assembly.

11. The compressor according to claim 10, characterized in that: At least a portion of the edge of the baffle is provided with a flange, which extends in a direction away from the upper balance block.

12. The compressor according to claim 11, characterized in that: Along the axial direction of the crankshaft, the height of the flange is H5, which satisfies: 1mm≤H5≤20mm.

13. A refrigeration device, characterized in that: Includes the compressor as described in any one of claims 1 to 12.

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