Compressor and refrigeration equipment

Abstract

The invention 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 located in the shell, a crankshaft of the pump body assembly is arranged on the upper silencer, the upper bearing, the first air cylinder, the second air cylinder and the lower bearing in a penetrating mode, a stator assembly of the motor is fixedly connected with the inner wall of the shell, and a rotor assembly is connected with the crankshaft. Due to the fact that a lower balance block is too close to an upper silencer or the diameter of the lower balance block is too large, disturbance to a refrigerant discharged by the lower silencer is increased, and the oil spitting rate is increased. The value of L * H / (H * D) is reasonably set to be within the range of 0.17-2.1, disturbance of the lower balance block to a refrigerant can be reduced, backflow of lubricating oil is facilitated, the oil spitting rate is reduced, meanwhile, it can be guaranteed that the overall size of the compressor is not too large, and compact design of the structure of the compressor is facilitated.

Description

Technical Field

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

[0002] The pump assembly of the compressor is provided with multiple cylinders to achieve multi-stage compression. The rotor assembly of the motor is provided with an exhaust flow path, and the stator assembly is provided with a return circuit. The refrigerant mixed with lubricating oil discharged from the pump assembly flows upward through the exhaust flow path, and most of the lubricating oil will be thrown to the inner wall of the shell driven by the rotation of the rotor assembly, and can flow downward along the inner wall of the shell and return to the oil pool from the return circuit. Due to the provision of multiple cylinders, the crankshaft of the pump assembly rotates unsteadily under the drive of the motor, so it is necessary to set a balancing block on the rotor assembly of the motor to improve the stability of the crankshaft operation. However, the displacement of each stage is not equal, and the size of the multi-stage cylinders is different. In order to achieve a better balancing effect, the mass of the balancing block needs to be increased, and the volume is also increased accordingly, so that the balancing block is closer to the exhaust port of the muffler. When the balancing block rotates, the disturbance of the exhaust increases, causing part of the refrigerant that should have gone through the exhaust flow path to flow to the return circuit, hindering the return of the lubricating oil, increasing the oil discharge rate of the compressor, insufficient lubrication of the crankshaft and bearings, increased friction, and reduced life. Summary of the invention

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

[0004] The present invention also provides a refrigeration device having the compressor.

[0005] A compressor according to an embodiment of the first aspect of the present invention comprises: a housing; a pump body assembly, which is arranged in the housing, the pump body assembly comprising 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 at the upper end of 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 is passed through the upper muffler, the upper bearing, the first cylinder, the second cylinder and the lower bearing; a motor is arranged in the housing and located above the upper muffler, The motor comprises a stator assembly and a rotor assembly, wherein the stator assembly is annular and fixedly connected to the inner wall of the housing, the rotor assembly is located in a space formed by the stator assembly and connected to the crankshaft, and the rotor assembly comprises a lower balancing block and a rotor, wherein the lower balancing block is connected to the lower end of the rotor; wherein, the end of the upper muffler facing the rotor assembly is an 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 balancing block is H1, the maximum distance from the rotation center of the lower balancing block to the edge of the lower balancing block along the radial direction of the crankshaft is D, and the following conditions are satisfied: 0.17≤L×H / (H1×D)≤2.1.

[0006] The compressor according to the embodiment of the present invention has at least the following beneficial effects: The pump body assembly is arranged inside the housing, the crankshaft of the pump body assembly is passed through the upper muffler, the upper bearing, the first cylinder, the second cylinder and the 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, the refrigerant in the second cylinder can be compressed, and the compressed refrigerant enters the first cylinder for further compression, and then is discharged to the upper muffler, and then discharged from the pump body assembly; after the refrigerant is discharged from the pump body assembly, it needs to pass through the rotor assembly and flow upward, and finally be 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 to the peripheral wall of the housing. Finally, most of the lubricating oil can flow back to the oil pool at the bottom along the peripheral wall of the housing, and a small amount of lubricating oil follows the refrigerant into the circulation loop. Because the lower balance block is too close to the upper muffler, or the diameter of the lower balance block is too large, the disturbance of the refrigerant discharged from the lower muffler will increase, and the oil discharge rate will increase; and the larger the distance H between the top wall of the inner cavity of the shell and the stator core, the more conducive to the reflux of the lubricating oil, but too large H will cause the height of the shell to increase. 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 can be reduced, which is conducive to the reflux of the lubricating oil, thereby reducing the oil discharge rate, and at the same time, it can ensure that the overall size of the compressor will not be too large, which is conducive to the compact design of the compressor structure.

[0007] According to some embodiments of the present invention, the rotor includes a rotor core, which is provided with a plurality of flow holes, which penetrate the rotor core axially, and the plurality of flow holes are arranged at intervals along the circumference of the rotor core; a plurality of guide channels are formed between the stator assembly and the inner wall of the shell, which penetrate the stator assembly axially, and the plurality of guide channels are arranged at intervals along the circumference of the stator assembly.

[0008] According to some embodiments of the present invention, the rotor core is provided with a mounting hole for the crankshaft to pass through, and on an 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 guide channels is S4, satisfying: S1 / S3≥S2 / S4.

[0009] According to some embodiments of the present invention, the shortest distance L between the lower end surface of the rotor assembly and the upper end surface of the upper muffler satisfies: L≥5 mm.

[0010] According to some embodiments of the present invention, the rotor is provided with a plurality of flow holes, and the flow holes penetrate the rotor axially. The rotor assembly also includes a lower wind cover arranged on the lower balance block, and the lower wind cover includes a first base plate and a first surrounding edge, and the first surrounding edge is connected to the edge of the first base plate and is arranged around the lower balance block. The first base plate is provided with a through hole for the crankshaft to pass through, and the side wall of the through hole and the side wall of the crankshaft are spaced apart so that the refrigerant discharged from the upper muffler can pass through the lower wind cover and enter the flow holes.

[0011] According to some embodiments of the present invention, along the axial direction of the crankshaft, the minimum height of the first surrounding edge is H2, and the maximum height of the lower balancing block is H1, satisfying: 0.5×H1≤H2≤H1.

[0012] According to some embodiments of the present invention, the diameter of the maximum inscribed circle of the through hole is D1, and the diameter of the minimum enclosing circle of the rotor assembly is D2, satisfying: 0.4≤D1 / D2≤0.7.

[0013] According to some embodiments of the present invention, the rotor assembly also includes an upper wind shield and an upper balancing block, the upper wind shield includes a second base plate and a second surrounding edge, the second base plate is connected to the upper end of the rotor, the second surrounding edge is connected to the edge of the second base plate and extends in a direction away from the rotor, and the upper balancing block is connected to the second base plate and is located in the space enclosed by the second surrounding edge.

[0014] According to some embodiments of the present invention, along the axial direction of the crankshaft, the minimum height of the second surrounding edge is H3, and the maximum height of the upper balancing block is H4, satisfying: H3≥H4.

[0015] According to some embodiments of the present invention, the rotor assembly further includes a baffle and an upper balancing block, the upper balancing block being connected to the upper end of the rotor, the rotor being provided with a plurality of flow holes, the flow holes penetrating the rotor axially, the baffle being connected to the upper end of the upper balancing block, an air outlet communicating with the flow holes being formed between the baffle and the rotor, the air outlet being extended along the circumferential direction of the rotor assembly.

[0016] According to some embodiments of the present invention, at least a portion of the edge of the baffle is provided with a flange, and the flange is extended in a direction away from the upper balancing weight.

[0017] According to some embodiments of the present invention, along the axial direction of the crankshaft, the height of the flange is H5, which satisfies: 1mm≤H5≤20mm.

[0018] A refrigeration device according to an embodiment of the second aspect of the present invention comprises the compressor described in the above embodiment.

[0019] The refrigeration device according to the embodiment of the present invention has at least the following beneficial effects: By adopting the compressor of the first aspect embodiment, the compressor is located in the shell by setting the pump body assembly, the crankshaft of the pump body assembly is passed through the upper muffler, the upper bearing, the first cylinder, the second cylinder and the lower bearing, the stator assembly of the motor is fixedly connected to the inner wall of the shell, and the rotor assembly is connected to the crankshaft. Therefore, when the crankshaft rotates, the refrigerant in the second cylinder can be compressed, and the compressed refrigerant enters the first cylinder to continue compression, and then is discharged to the upper muffler, and then discharged from the pump body assembly; after the refrigerant is discharged from the pump body assembly, it needs to pass through the rotor assembly and flow upward, and finally discharged from the shell. 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 to the peripheral wall of the shell. Finally, most of the lubricating oil can flow back to the oil pool at the bottom along the peripheral wall of the shell, and a small amount of lubricating oil follows the refrigerant into the circulation loop. Because the lower balance block is too close to the upper muffler, or the diameter of the lower balance block is too large, the disturbance of the refrigerant discharged from the lower muffler will increase, and the oil discharge rate will increase; and the larger the distance H between the top wall of the inner cavity of the shell and the stator core, the more conducive to the reflux of the lubricating oil, but too large H will cause the height of the shell to increase. 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 can be reduced, which is conducive to the reflux of the lubricating oil, thereby reducing the oil discharge rate, and at the same time, it can ensure that the overall size of the compressor will not be too large, which is conducive to the compact design of the compressor structure.

[0020] Additional aspects and advantages of the present invention will be given in part in the following description and in part will be obvious from the following description, or will be learned through practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] The present invention will be further described below with reference to the accompanying drawings and embodiments, wherein: Figure 1 is a cross-sectional schematic diagram of a compressor according to an embodiment of the present invention; Figure 2 is a cross-sectional view of a compressor according to an embodiment of the present invention; Figure 3 is a cross-sectional schematic diagram of a rotor assembly according to an embodiment of the present invention; Figure 4 is a cross-sectional schematic diagram of a rotor assembly according to another embodiment of the present invention; Figure 5 It is a relationship curve diagram of the oil discharge rate and the value of the formula L×H / (H1×D) of an embodiment of the present invention.

[0022] Reference numerals: Compressor 1000; Shell 100; exhaust pipe 110; upper shell 120; middle shell 130; lower shell 140; Pump body assembly 200; crankshaft 210; upper muffler 220; upper bearing 230; first cylinder 240; first piston 241; partition assembly 250; second cylinder 260; second piston 261; lower bearing 270; lower muffler 280; refrigerant channel 290; Motor 300; stator assembly 310; stator core 311; sleeve 312; flow guide channel 313; rotor assembly 320; rotor core 321; flow hole 322; mounting hole 323; lower balancing block 330; lower wind shield 340; first bottom plate 341; through hole 3411; first surrounding edge 342; upper balancing block 350; upper wind shield 360; second bottom plate 361; second surrounding edge 362; baffle 370; flange 371; air outlet 373; Liquid storage tank 400; air intake pipe 410. DETAILED DESCRIPTION

[0023] Embodiments of the present invention are described in detail below, examples of which are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention, and cannot be understood as limiting the present invention.

[0024] In the description of the present invention, it is necessary to understand that descriptions involving orientation, such as up, down, front, back, left, right, etc., indicating orientations or positional relationships, are based on the orientations or positional relationships shown in the drawings, and are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present invention.

[0025] In the description of the present invention, "several" means one or more, "more" means more than two, "greater than", "less than", "exceed" etc. are understood as not including the number itself, and "above", "below", "within" etc. are understood as including the number itself. If there is a description of "first" or "second", it is only used for the purpose of distinguishing the technical features, and cannot be understood as indicating or implying the relative importance or implicitly indicating the number of the indicated technical features or implicitly indicating the order of the indicated technical features.

[0026] In the description of the present invention, unless otherwise clearly defined, terms such as setting, installing, connecting, etc. should be understood in a broad sense, and technicians in the relevant technical field can reasonably determine the specific meanings of the above terms in the present invention based on the specific content of the technical solution.

[0027] Reference Figure 1 , Figure 2 and Figure 3As 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 according to the embodiment of the present invention 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 housing portion 120, a middle housing portion 130 and a lower housing portion 140 located at the upper end. The upper housing portion 120 is connected to the upper end of the middle housing portion 130, and the lower housing portion 140 is connected to the lower end of the middle housing portion 130. The inner cavity of the exhaust pipe 110 is connected to the inner cavity of the housing 100. The pump body assembly 200 is arranged inside the housing 100, and 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, and the lower bearing 270 is arranged at intervals 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 first cylinder 240 is connected to the lower end of the upper bearing 230, the second cylinder 260 is connected to the upper end of the lower bearing 270, and 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 .

[0028] The lower muffler 280 is connected to the lower end of the lower bearing 270, and the crankshaft 210 is provided through the upper muffler 220, the upper bearing 230, the first cylinder 240, the partition assembly 250, the second cylinder 260 and the lower bearing 270. The crankshaft 210 is respectively sleeved with a first piston 241 and a second piston 261, 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 is also provided with a refrigerant channel 290, which is provided through the lower bearing 270, the second cylinder 260 and the partition assembly 250, and the refrigerant channel 290 communicates the inner cavity of the lower muffler 280 and the compression chamber of the first cylinder 240.

[0029] The motor 300 is arranged in the housing 100 and above the pump body assembly 200, and the motor 300 is connected to the crankshaft 210 by driving. 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, and a guide channel 313 is formed between the stator assembly 310 and the inner wall of the housing 100, and the guide channel 313 runs through the two ends of the stator assembly 310 in the axial direction. The rotor assembly 320 is located in the space formed by the stator assembly 310 and is connected to the crankshaft 210 by driving. The rotor assembly 320 includes a rotor and a lower balancing block 330, the rotor is provided with a through hole 322, the through hole 322 runs through the rotor in the axial direction and is configured to allow the refrigerant to flow, and the lower balancing block 330 is connected to the lower end of the rotor.

[0030] 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 shell 100 and the upper end face of the stator core 311 of the stator assembly 310 is H, the maximum height of the lower balancing block 330 is H1, and the maximum distance from the rotation center of the lower balancing block 330 to the edge of the lower balancing block 330 along the radial direction of the crankshaft 210 is D, satisfying: 0.17≤L×H / (H1×D)≤2.1.

[0031] It can be understood that the refrigerant enters the compression chamber of the second cylinder 260 through the intake pipe 410 of the liquid storage tank 400, and 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 through the refrigerant channel 290 for compression. 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. The rotation of the rotor assembly 320 drives the refrigerant and lubricating oil to rotate, so that most of the lubricating oil is thrown to the inner wall of the shell 100, and the lubricating oil can flow downward along the inner wall of the shell 100 and return to the oil pool at the bottom of the shell 100 through the guide channel 313.

[0032] Since the height of the lower balancing block 330 is higher and closer to the upper muffler 220, that is, the shortest distance L between the lower end surface of the rotor assembly 320 and the upper end surface of the upper muffler 220 is too small, or the diameter D of the lower balancing block 330 is too large, it will lead to increased disturbance of the refrigerant discharged from the lower muffler 280, causing part of the refrigerant that should have been discharged from the flow hole 322 of the rotor assembly 320 to flow into the guide channel 313, hindering the reflux of the lubricating oil and increasing the oil discharge rate. The larger the distance H between the top wall of the inner cavity of the shell 100 and the stator core 311, the less the situation where the lubricating oil is directly discharged from the shell 100 without being separated from the refrigerant, which is beneficial to the reflux of the lubricating oil, but if H is too large, it will cause the height of the shell 100 to increase. For example, refer to Figure 5 As shown, Figure 5 The horizontal axis represents the oil discharge rate, and the vertical axis represents the value of L×H / (H1×D). Figure 5 The points in the figure represent the size of the oil discharge rate corresponding to the specific value of L×H / (H1×D), and the dotted line represents the fitting curve for the discrete oil discharge rate, which can reflect the trend of the oil discharge rate changing with the different values ​​of L×H / (H1×D). The value 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 overall oil discharge rate first decreases and then increases. 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 balancing block 330 to the refrigerant can be reduced, which is beneficial to the reflux of the lubricating oil, thereby reducing the oil discharge rate. At the same time, it can ensure that the overall size of the compressor 1000 will not be too large, which is beneficial to the compact design of the compressor 1000 structure.

[0033] Reference Figure 2 As shown, in the embodiment of the present invention, the rotor includes a rotor core 321, the rotor core 321 is provided with a plurality of through holes 322, the through holes 322 penetrate the rotor core 321 in the axial direction and are configured to allow the refrigerant to flow, and the plurality of through 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, and a plurality of guide channels 313 are formed between the sleeve 312 and the inner wall of the housing 100, the guide channels 313 penetrate the stator assembly 310 in the axial direction and are configured to allow the refrigerant to flow, and the plurality of guide channels 313 are arranged at intervals along the circumference of the stator assembly 310. By providing a plurality of through holes 322 and a plurality of guide 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 flow back, thereby improving the refrigerant discharge efficiency and the lubricating oil return efficiency.

[0034] Reference Figure 2As shown, in the embodiment of the present invention, the rotor core 321 is provided with a mounting hole 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 guide 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 can be understood that S1 / S3 reflects the area occupied by all the through-holes 322 on the rotor core 321, and S2 / S4 reflects the area occupied by the guide channel 313 on the stator core 311. When S1 / S3<S2 / S4, that is, the flow area of ​​the through-holes 322 is small, and the flow area of ​​the guide channel 313 is large, it is not conducive to the refrigerant passing through the rotor assembly 320. Therefore, by setting S1 / S3≥S2 / S4, it is beneficial for the refrigerant to pass through the through-holes 322 of the rotor assembly 320, thereby improving the discharge efficiency of the refrigerant. It should be noted that when measuring the size of S1, S3, S2 and S4, the structures such as the stator core 311, the sleeve 312, and the rotor core 321 can be arranged in the up and down direction, and the top contours of the structures such as the stator core 311, the sleeve 312, and the rotor core 321 can be obtained by using a two-dimensional scanner, and then the area can be calculated by related software.

[0035] Reference Figure 1 As shown, in the embodiment of the present invention, the shortest distance L between the lower end surface of the rotor assembly 320 and the upper end surface 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 balancing block 330, due to the irregular structure of the lower balancing block 330, the disturbance effect on the refrigerant after rotation is relatively large. When L is less than 5mm, the shortest distance L between the lower balancing block 330 and the upper end surface of the upper muffler 220 is too small, which will increase the disturbance of the refrigerant discharged from the lower muffler 280, causing part 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 reflux of the 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 refrigerant by the lower balancing block 330, thereby reducing the oil discharge rate.

[0036] In order to further reduce the disturbance of the lower balancing block 330 to the refrigerant, refer to Figure 1 and Figure 3As shown, in the embodiment of the present invention, the rotor assembly 320 further includes a lower air cover 340 which is covered on the lower balance block 330, and the lower air cover 340 is cylindrical. The lower air cover 340 includes a first bottom plate 341 and a first surrounding edge 342, the first surrounding edge 342 is connected to the edge of the first bottom plate 341 and is arranged around the lower balance block 330, the first bottom plate 341 is provided with a through hole 3411 for the crankshaft 210 to pass through, and the side wall of the through hole 3411 and the side wall of the crankshaft 210 are arranged at intervals, so that the refrigerant discharged from the upper muffler 220 can pass through the lower air cover 340 and enter the flow hole 322. Since the lower air cover 340 is cylindrical and covered on the lower balance block 330, when the lower air cover 340 rotates driven by the rotor assembly 320, the disturbance effect on the refrigerant is smaller than the disturbance effect of the lower balance block 330, which is conducive to the refrigerant entering the flow hole 322, thereby reducing the oil discharge rate. Therefore, after the lower wind shield 340 is provided, the lower balancing block 330 can be closer to the upper muffler 220 , which is beneficial to the compact design of the compressor 1000 .

[0037] 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 surrounding edge 342 is H2, and the maximum height of the lower balancing block 330 is H1, which satisfies: 0.5×H1≤H2≤H1, and the formula 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 surrounding edge 342 is relatively short and can only cover a small part of the lower balancing block 330. When the lower balancing block 330 rotates, the disturbance to the refrigerant is still relatively large, so it is difficult for the lower wind cover 340 to reduce the disturbance. When the ratio of H2 / H1 is greater than 1, that is, the height of the first surrounding edge 342 is greater than the height of the lower balancing block 330, the lower wind shield 340 cannot be installed due to assembly problems. Even if it can be installed, the first surrounding edge 342 needs to wrap the rotor core 321, which will increase the outer diameter of the rotor assembly 320 and affect the performance of the motor 300. Therefore, a reasonable design of the ratio of H2 / H1 within the range of 0.5 to 1 can enable the lower wind shield 340 to effectively reduce disturbances while facilitating assembly and improving the reliability of the motor 300.

[0038] Continue to refer to Figure 2As shown, in the embodiment of the present invention, the diameter of the maximum inscribed circle of the through hole 3411 is D1. For example, when the through hole 3411 is a circular hole, the diameter of the maximum inscribed circle of the through hole 3411 is the aperture of the through hole 3411. The diameter of the minimum enclosing circle of the rotor assembly 320 is D2, which satisfies: 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 aperture of the through hole 3411 is too large, and the lower wind cover 340 is difficult to wrap most of the structure of the lower balance block 330, and the disturbance of the lower balance block 330 to the refrigerant increases, and the oil discharge rate increases. Therefore, a reasonable design of the ratio of D1 / D2 within the range of 0.4 to 0.7 can reduce the refrigerant intake resistance while effectively wrapping the lower wind hood 340 and reducing the disturbance of the lower balance block 330 to the refrigerant.

[0039] Reference Figure 3 As shown, in the embodiment of the present invention, the rotor assembly 320 further includes a baffle 370 and an upper balancing block 350, and the upper balancing block 350 is 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 air outlet 373 communicating with the flow hole 322 is formed between the baffle 370 and the rotor, and the air outlet 373 is arranged to extend along the circumference of the rotor assembly 320. Therefore, the refrigerant discharged from the vent will flow radially toward the rotor assembly 320 under the guidance of the baffle 370, and the refrigerant can flow upward if it is lighter, and finally be discharged from the shell 100 through the exhaust pipe 110. The lubricating oil mixed in the refrigerant is thrown to the inner wall of the shell 100, thereby returning to the oil pool, which can reduce the oil discharge rate of the compressor 1000.

[0040] Continue to refer to Figure 3 As shown, in the embodiment of the present invention, at least part of the edge of the baffle 370 is provided with a flange 371, and the flange 371 is extended in a direction away from the upper balancing block 350. For example, the baffle 370 is provided with a flange 371 only at the position where the upper balancing block 350 is located, so as to facilitate the positioning of the upper balancing block 350. Or the flange 371 can also be constructed as a complete ring, and a suitable solution is selected according to the actual situation. By providing the flange 371, the baffle 370 can rotate under the drive of the rotor assembly 320, so the flange 371 will also rotate to further drive the nearby refrigerant to rotate, increase the rotation speed of the refrigerant, and help to throw the lubricating oil to the side wall of the shell 100, improve the separation efficiency from the refrigerant, and thus reduce the oil discharge rate.

[0041] Continue to refer to Figure 3As shown, in an embodiment of the present invention, along the axial direction of the crankshaft 210, the height of the flange 371 is H5, which satisfies: 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 to play a role in driving the refrigerant to rotate. When H5 is greater than 20mm, the height of the flange 371 is too high, which can easily cause the rotor assembly 320 to run unsteadily and hinder the flow of the refrigerant. Therefore, a reasonable design of 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 the refrigerant and the lubricating oil and reduces the oil discharge rate.

[0042] Reference Figure 4 As shown, in another embodiment of the present invention, the rotor assembly 320 further includes an upper wind shield 360 and an upper balancing block 350, the upper wind shield 360 includes a second bottom plate 361 and a second surrounding edge 362, the second bottom plate 361 is connected to the upper end of the rotor, the second surrounding edge 362 surrounds and is connected to the edge of the second bottom plate 361, and is extended in a direction away from the rotor, and the upper balancing block 350 is connected to the second bottom plate 361 and is located in a space enclosed by the second surrounding edge 362. It can be understood that the upper wind shield 360 can rotate under the drive of the rotor assembly 320, so when the second surrounding edge 362 rotates, it will drive the nearby refrigerant to rotate, increase the rotation speed of the refrigerant, and help to throw the lubricating oil to the side wall of the shell 100, improve the separation efficiency from the refrigerant, and thus reduce the oil discharge rate.

[0043] 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 surrounding edge 362 is H3, and the maximum height of the upper balancing block 350 is H4, satisfying: H3 ≥ H4. It can be understood that when H4 is less than H3, the height of the second surrounding edge 362 is relatively short, and it is difficult to drive the refrigerant to rotate. For this reason, by designing H3 to be greater than or equal to H4, it is convenient for the second surrounding edge 362 to continue to drive the refrigerant to rotate, which is conducive to throwing the lubricating oil to the side wall of the shell 100, improving the separation efficiency from the refrigerant, and thus reducing the oil discharge rate.

[0044] A refrigeration device according to an embodiment of the present invention comprises the compressor 1000 according to the above embodiment, and the refrigeration device may be an air conditioner, a refrigerator, etc. The refrigeration device according to the embodiment of the present invention adopts the compressor 1000 according to the above embodiment, and the pump body assembly 200 is arranged in the housing 100, the crankshaft 210 of the pump body assembly 200 is passed through the upper muffler 220, the upper bearing 230, the first cylinder 240, the second cylinder 260 and the 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, the refrigerant in the second cylinder 260 can be compressed, and the compressed refrigerant enters the first cylinder 240 for further compression, and then is discharged to the upper muffler 220, and then discharged from the pump body assembly 200; after the refrigerant is discharged from the pump body assembly 200, it needs to pass through the rotor assembly 320 and flow upward, and finally 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 will rotate under the drive of the rotor. Since the lubricating oil is heavier than the refrigerant, it will be thrown to the peripheral wall of the shell 100. Finally, most of the lubricating oil can flow back to the oil pool at the bottom along the peripheral wall of the shell 100, and a small amount of lubricating oil will enter the circulation loop with the refrigerant. Since the lower balance block 330 is too close to the upper muffler 220, or the diameter of the lower balance block 330 is too large, the disturbance of the refrigerant discharged from the lower muffler 280 will increase, and the oil discharge rate will increase; and the larger the distance H between the top wall of the inner cavity of the shell 100 and the stator core 311, the more conducive it is to the reflux of the lubricating oil, but if H is too large, the height of the shell 100 will increase. 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 balancing block 330 to the refrigerant can be reduced, which is beneficial to the reflux of the lubricating oil, thereby reducing the oil discharge rate. At the same time, it can 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] Since the refrigeration device adopts all the technical solutions of the compressor 1000 of the above embodiment, it has at least all the beneficial effects brought by the technical solutions of the above embodiment, which will not be repeated here.

[0046] The embodiments of the present invention are described in detail above with reference to the accompanying drawings, but the present invention is not limited to the above embodiments, and various changes can be made within the knowledge scope of ordinary technicians in the relevant technical field without departing from the purpose of the present invention.

Claims

1. A compressor, characterized in that include: case; A pump body assembly is arranged in the housing, the pump body assembly comprises 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 at the upper end of 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, the lower bearing is connected to the lower end of the second cylinder, and the crankshaft is passed through the upper muffler, the upper bearing, the first cylinder, the second cylinder and the lower bearing; a motor, arranged in the housing and located above the upper muffler, the motor comprising a stator assembly and a rotor assembly, the stator assembly being annular and fixedly connected to the inner wall of the housing, the rotor assembly being located in a space formed by the stator assembly and connected to the crankshaft, the rotor assembly comprising a lower balancing block and a rotor, the lower balancing block being connected to the lower end of the rotor; Among them, 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 shell and the upper end face of the stator core of the stator assembly is H, the maximum height of the lower balancing block is H1, and the maximum distance from the rotation center of the lower balancing block to the edge of the lower balancing block along the radial direction of the crankshaft 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 is provided with a plurality of flow holes, which penetrate the rotor core in the axial direction, and are arranged at intervals along the circumference of the rotor core; a plurality of guide channels are formed between the stator assembly and the inner wall of the shell, which penetrate the stator assembly in the axial direction, 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 a mounting hole for the crankshaft to pass through. On an 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 guide 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 surface of the rotor assembly and the upper end surface of the upper muffler satisfies: L≥5mm.

5. The compressor according to claim 1, characterized in that: The rotor is provided with a plurality of flow holes, and the flow holes penetrate the rotor axially. The rotor assembly also includes a lower wind cover covered on the lower balance block, and the lower wind cover includes a first base plate and a first surrounding edge, and the first surrounding edge is connected to the edge of the first base plate and is arranged around the lower balance block. The first base plate is provided with a through hole for the crankshaft to pass through, and the side wall of the through hole and the side wall of the crankshaft are spaced apart so that the refrigerant discharged from the upper muffler can pass through the lower wind cover 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 surrounding edge is H2, and the maximum height of the lower balancing block is H1, satisfying: 0.5×H1≤H2≤H1.

7. The compressor according to claim 5, characterized in that: The diameter of the maximum inscribed circle of the through hole is D1, and the diameter of the minimum surrounding 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 wind shield and an upper balancing block. The upper wind shield includes a second base plate and a second surrounding edge. The second base plate is connected to the upper end of the rotor. 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 balancing block is connected to the second base plate and is located in a 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 surrounding edge is H3, and the maximum height of the upper balancing block is H4, satisfying: H3≥H4.

10. The compressor according to claim 1, characterized in that: The rotor assembly also includes a baffle and an upper balancing block, wherein the upper balancing block is connected to the upper end of the rotor, the rotor is provided with a plurality of flow holes, and the flow holes penetrate the rotor axially, the baffle is connected to the upper end of the upper balancing block, and an air outlet connected to the flow holes is formed between the baffle and the rotor, and the air outlet is extended along the circumference of the rotor assembly.

11. The compressor according to claim 10, characterized in that: At least part of the edge of the baffle is provided with a flange, and the flange is extended in a direction away from the upper balancing 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, satisfying: 1mm≤H5≤20mm.

13. Refrigeration equipment, characterized in that: Comprising a compressor as claimed in any one of claims 1 to 12.

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