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, a motor, a liquid storage tank and a sealing piece, a first mounting groove is formed around a first shaft hole of a first shaft neck part, the annular sealing piece is arranged in the first mounting groove, and the sealing piece has elasticity and can deform under the pressure action of a lower silencer and the first shaft neck part; therefore, the sealing performance between the lower silencer and the first shaft neck part is improved, the situation that air suction of the first air cylinder is overheated is reduced, and the performance of the compressor is improved. The sealing performance can be influenced by the perimeter of the sealing pieces, the width of the first mounting groove and the number of the sealing pieces. In order to better guide the type selection of the sealing element and avoid the situation that the cost is increased due to insufficient sealing performance or overlarge sealing allowance, the value of t * n / L is limited to be within the range of 0.055-0.32 through a formula, and it can be ensured that the sealing performance of the sealing element meets related requirements.

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 body assembly of the compressor is provided with multiple cylinders to realize multi-stage compression, which can reduce the compression ratio of each cylinder and improve the volumetric efficiency. In the related art, the pump body assembly includes a crankshaft, an upper muffler, an upper bearing, a secondary cylinder, a primary cylinder, a lower bearing and a lower muffler. The primary cylinder discharges medium-pressure gas after suction and compression. The medium-pressure gas is discharged to the lower muffler, and enters the secondary cylinder after passing through the lower bearing and the primary cylinder to be compressed into high-pressure gas, and finally discharged from the pump body assembly through the upper muffler. The bottom wall of the lower muffler needs to be sealed with the lower end of the lower bearing to prevent the high-temperature and high-pressure refrigerant outside the pump body assembly from entering the lower muffler. Since the outside of the pump body assembly is a high-temperature and high-pressure refrigerant, and the inside of the lower muffler is a medium-pressure refrigerant, there is a pressure difference, and due to the manufacturing precision problem of the lower bearing, the sealing is general, and the high-temperature and high-pressure refrigerant is easy to enter the lower muffler, resulting in the suction of the secondary cylinder overheating and the performance of the compressor is reduced. 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 improving the sealing performance between a muffler and a bearing.

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

[0005] A compressor according to a first embodiment of the present invention comprises: a housing; A pump body assembly is arranged in the housing, the pump body assembly includes a crankshaft, a first cylinder, a second cylinder, a lower muffler and a lower bearing, the first cylinder is located above the second cylinder, the second cylinder is connected to the upper end of the lower bearing, the lower muffler is connected to the side of the lower bearing away from the second cylinder, the lower bearing includes a first shaft neck protruding in a direction away from the second cylinder, the first shaft neck is provided with a first shaft hole for the crankshaft to pass through, the pump body assembly is provided with at least one first mounting groove, the first mounting groove is provided on the lower muffler or the first shaft neck and is arranged around the first shaft hole; The invention relates to a machine, which is arranged in the housing and is drivingly connected to the crankshaft; a liquid storage tank, including an intake pipe, which is connected to the second cylinder; at least one annular seal, the number of which is the same as the number of the first mounting grooves, the seals are correspondingly arranged in the first mounting grooves and arranged around the first shaft hole, and the seals are sealingly connected between the lower muffler and the first shaft neck; wherein, in one group of the first mounting grooves and the seals installed in the first mounting grooves, the central circumference of the seals is L, the maximum width of the first mounting grooves is t, the number of the seals is n, and the following conditions are satisfied: .

[0006] The compressor according to the embodiment of the present invention has at least the following beneficial effects: By setting the pump body assembly in the housing, the crankshaft of the pump body assembly is arranged in the first cylinder, the second cylinder, the lower bearing and the lower muffler, and the motor and the crankshaft are connected in driving. Therefore, when the crankshaft rotates, the refrigerant in the second cylinder can be compressed, and the compressed refrigerant first enters the lower muffler and then enters the first cylinder to continue compression, and then discharges the pump body assembly. After the refrigerant is discharged from the pump body assembly, it needs to pass through the motor and flow upward, and finally discharge from the housing. Since the first mounting groove is arranged around the first axial hole of the first shaft neck, and the annular seal is arranged in the first mounting groove, the lower muffler and the first shaft neck are sealed against the seal together, and the seal has elasticity and can be deformed under the pressure of the lower muffler and the first shaft neck, thereby improving the sealing between the lower muffler and the first shaft neck, effectively avoiding the high temperature and high pressure refrigerant from entering the lower muffler, resulting in the overheating of the suction of the first cylinder, and can improve the performance of the compressor. Since the circumference of the seal, the width of the first mounting groove and the number of seals will affect the sealing. In order to better guide the selection of seals and avoid insufficient sealing or excessive sealing margin leading to increased costs, the value of t×n / L is limited to the range of 0.055 to 0.32 through the formula, which can ensure that the sealing of the seal meets the relevant requirements.

[0007] According to some embodiments of the present invention, the first mounting groove is provided on the end wall of the first journal portion, and the sealing member is sealingly abutted between the end wall of the first journal portion and the inner wall of the lower muffler.

[0008] According to some embodiments of the present invention, the first mounting groove is arranged on the end wall of the first shaft neck portion, the lower muffler includes a surrounding plate and a cover plate, the surrounding plate is connected to the edge of the lower bearing and extends in a direction away from the second cylinder, the surrounding plate and the first shaft neck portion are spaced apart, the cover plate is connected to the lower end of the surrounding plate, and is sealed to the sealing member.

[0009] According to some embodiments of the present invention, the lower muffler includes a surrounding plate and a cover plate, the surrounding plate is connected to the edge of the lower bearing and extends in a direction away from the second cylinder, the surrounding plate and the first shaft neck are spaced apart, the cover plate is connected to the lower end of the surrounding plate, the cover plate is provided with a first through hole for the first shaft neck to pass through, the inner wall of the first through hole is surrounded by the first mounting groove, and the inner wall of the first through hole is arranged toward the side wall of the first shaft neck, and the seal is sealingly connected to the inner wall of the first through hole and the side wall of the first shaft neck.

[0010] According to some embodiments of the present invention, the deformation amount of the seal is e, which satisfies: 0.5≤e≤1.5.

[0011] According to some embodiments of the present invention, the pump body assembly further includes an upper muffler and an upper bearing, the upper bearing is connected to the upper end of the first cylinder, the upper muffler is connected to the upper end of the upper bearing, the motor includes a rotor assembly and a stator assembly sleeved on the outside of the rotor assembly, the rotor assembly includes a lower balancing block and a rotor, the lower balancing block is connected to the lower end of the rotor, 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 L1, 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, 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: .

[0012] According to some embodiments of the present invention, the motor includes a rotor assembly and a stator assembly sleeved on the outside of the rotor assembly, the rotor assembly includes a rotor core, the rotor core is provided with a plurality of flow holes, the flow holes 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, the plurality of guide channels respectively penetrate the stator assembly axially, and the plurality of guide channels are arranged at intervals along the circumference of the stator assembly.

[0013] 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 of the stator assembly is S2, and the sum of the flow areas of all the flow guide channels is S4, satisfying: .

[0014] A compressor according to a second aspect of the present invention includes: a housing; A pump body assembly is arranged in the housing, and the pump body assembly includes a crankshaft, a first cylinder, a second cylinder, a lower muffler and a lower bearing, the first cylinder is located above the second cylinder, the second cylinder is connected to the upper end of the lower bearing, the lower muffler is connected to the side of the lower bearing away from the second cylinder, the lower bearing includes a first shaft neck protruding in a direction away from the second cylinder, the first shaft neck is provided with a first shaft hole for the crankshaft to pass through; a motor is arranged in the housing and is drivingly connected to the crankshaft; a liquid storage tank includes an intake pipe, the intake pipe and connected to the second cylinder; a sealing member connected to the pump body assembly, the sealing member comprising an annular sheet located between the end of the first shaft neck and the lower muffler, at least one end surface of the annular sheet being provided with an annular protrusion arranged around the first shaft hole, the annular protrusion being sealingly connected between the end of the first shaft neck and the lower muffler; wherein the central circumference of the annular protrusion closest to the first shaft hole is L, along the radial direction of the crankshaft, the maximum contact width between the annular sheet and the first shaft neck is t, the number of the annular protrusions is n, and the following is satisfied: .

[0015] The compressor according to the embodiment of the present invention has at least the following beneficial effects: The pump body assembly is arranged in the housing, the crankshaft of the pump body assembly is arranged through the first cylinder, the second cylinder, the lower bearing and the lower muffler, and the motor and the crankshaft are connected in driving. Therefore, when the crankshaft rotates, the refrigerant in the second cylinder can be compressed, and the compressed refrigerant first enters the lower muffler and then enters the first cylinder for further compression, and then discharges the pump body assembly. After the refrigerant is discharged from the pump body assembly, it needs to pass through the motor and flow upward, and finally discharge from the housing. The circumference of the annular protrusion, the maximum contact width between the annular sheet and the first shaft neck, and the number of annular protrusions will affect the sealing. The longer the circumference of the annular protrusion, the worse the sealing; the larger the maximum contact width between the annular sheet and the first shaft neck, and the more the number of annular protrusions, the better the sealing. Therefore, when the value of t×n / L is less than 0.055, the sealing between the lower muffler and the lower bearing is insufficient, and air leakage is likely to occur. When the value of t×n / L is greater than 0.32, the sealing margin between the lower muffler and the lower bearing is too large, and the cost increases. Therefore, a reasonable design of the value of t×n / L within the range of 0.055 to 0.32 can better guide the structural design of the seal, avoid insufficient sealing or excessive sealing margin leading to increased costs, and ensure that the sealing of the seal meets relevant requirements.

[0016] According to some embodiments of the present invention, two annular protrusions are provided and spaced apart along the radial direction of the crankshaft, wherein one of the annular protrusions protrudes toward the end of the first journal portion, and the other annular protrusion protrudes toward the lower muffler.

[0017] A compressor according to a third aspect of the present invention includes: a housing; A pump body assembly is arranged in the housing, the pump body assembly includes a crankshaft, an upper muffler, an upper bearing, a first cylinder and a second cylinder, the first cylinder is connected to the lower end of the upper bearing and is located above the second cylinder, the upper muffler is connected to the side of the upper bearing away from the first cylinder, the upper end surface of the upper muffler is provided with a second through hole, the upper bearing includes a second shaft neck protruding in a direction away from the first cylinder and passing through the second through hole, the second shaft neck is provided with a second shaft hole for the crankshaft to pass through, and the pump body assembly is provided with at least one second mounting groove, the second mounting groove is located on the inner wall of the second through hole or the second shaft neck facing the second through hole The side wall of the hole is arranged around the second shaft hole; the motor is arranged in the housing and is drivingly connected to the crankshaft; the liquid storage tank includes an intake pipe, and the intake pipe is connected to the first cylinder; at least one annular seal, the number of the seals is the same as the number of the second mounting grooves, the seals are correspondingly arranged in the second mounting grooves and arranged around the second shaft hole, and the seals are sealingly connected between the upper muffler and the second shaft neck; wherein, in one group of the second mounting grooves and the seals installed in the second mounting grooves, the central circumference of the seals is L, the maximum width of the second mounting grooves is t, and the number of the seals is n, which satisfies: .

[0018] The compressor according to the embodiment of the present invention has at least the following beneficial effects: The pump body assembly is arranged in the housing, and the crankshaft of the pump body assembly is arranged through the upper muffler, the upper bearing, the first cylinder and the second cylinder, and the motor is connected to the crankshaft drive. Therefore, when the crankshaft rotates, the refrigerant in the first cylinder can be compressed, and the compressed refrigerant first enters the upper muffler and then enters the second cylinder to continue compression, and then discharges the pump body assembly. The circumference of the seal, the width of the second mounting groove and the number of seals will affect the sealing. The longer the circumference of the seal, the worse the sealing; the larger the width of the second mounting groove and the more the number of seals, the better the sealing. Therefore, when the value of t×n / L is less than 0.055, the sealing between the upper muffler and the upper bearing is insufficient, and air leakage is likely to occur. When the value of t×n / L is greater than 0.32, the sealing margin between the upper muffler and the upper bearing is too large, and the cost increases. Therefore, a reasonable design of the value of t×n / L within the range of 0.055 to 0.32 can better guide the selection of seals, avoid insufficient sealing or excessive sealing margin leading to increased costs, and ensure that the sealing of the seals meets relevant requirements.

[0019] A refrigeration device according to an embodiment of the fourth aspect of the present invention comprises the compressor described in the above embodiment.

[0020] 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 embodiment, the compressor is located in the housing by setting the pump body assembly, the crankshaft of the pump body assembly is passed through the first cylinder, the second cylinder, the lower bearing and the lower muffler, and the motor is connected to the crankshaft. Therefore, when the crankshaft rotates, the refrigerant in the second cylinder can be compressed, and the compressed refrigerant first enters the lower muffler and then enters the first cylinder to continue compression, and then discharges the pump body assembly. After the refrigerant is discharged from the pump body assembly, it needs to pass through the motor and flow upward, and finally discharge from the housing. Since the first mounting groove is arranged around the first axial hole of the first shaft neck, and the annular seal is arranged in the first mounting groove, the lower muffler and the first shaft neck are sealed against the seal together, and the seal has elasticity and can be deformed under the pressure of the lower muffler and the first shaft neck, thereby improving the sealing between the lower muffler and the first shaft neck, effectively avoiding the high temperature and high pressure refrigerant from entering the lower muffler, resulting in the situation of overheating of the suction of the secondary cylinder, and improving the performance of the compressor. Since the circumference of the seal, the width of the first mounting groove and the number of seals will affect the sealing. In order to better guide the selection of seals and avoid insufficient sealing or excessive sealing margin leading to increased costs, the value of t×n / L is limited to the range of 0.055 to 0.32 through the formula, which can ensure that the sealing of the seal meets the relevant requirements.

[0021] 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

[0022] The present invention will be further described below with reference to the accompanying drawings and embodiments, wherein: Figure 1 is a structural cross-sectional view of a compressor according to an embodiment of the present invention; Figure 2 is a structural cross-sectional view of a pump body assembly according to a first embodiment of the present invention; Figure 3 yes Figure 2 The enlarged view of point A in the middle; Figure 4 is a structural cross-sectional view of a lower bearing and a lower muffler according to a second embodiment of the present invention; Figure 5 is a structural cross-sectional view of a lower bearing and a lower muffler according to a third embodiment of the present invention; Figure 6 is a structural cross-sectional view of a lower bearing and a lower muffler according to a fourth embodiment of the present invention; Figure 7 yes Figure 6 The enlarged view of point B in the middle; Figure 8 is a structural cross-sectional view of a sealing member according to an embodiment of the present invention; Fig. 9 is a structural cross-sectional view of an upper bearing and an upper muffler according to a fifth embodiment of the present invention; Fig.10 is a cross-sectional schematic diagram of a compressor according to another embodiment of the present invention; Fig.11 is a cross-sectional view of a compressor according to an embodiment of the present invention; Fig.12 is a cross-sectional schematic diagram of a rotor assembly according to an embodiment of the present invention; Fig.13 is a cross-sectional schematic diagram of a rotor assembly according to another embodiment of the present invention; Fig.14 It is a relationship curve diagram of the oil discharge rate of an embodiment of the present invention and the value of the formula L1×H / (H1×D).

[0023] 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; second mounting groove 221; second through hole 222; upper bearing 230; second axial neck 231; second axial hole 232; first cylinder 240; first piston 241; partition assembly 250; second cylinder 260; second piston 261; lower bearing 270; first axial neck 271; first mounting groove 272; first axial hole 273; lower muffler 280; enclosure 281; cover plate 282; first through hole 283; 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; Sealing member 500 ; annular sheet 510 ; annular protrusion 511 ; folded edge 520 . DETAILED DESCRIPTION

[0024] 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.

[0025] 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.

[0026] 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.

[0027] 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.

[0028] The pump body assembly of the compressor is provided with multiple cylinders to achieve multi-stage compression, which can reduce the compression ratio of each cylinder and improve the volumetric efficiency. In the related art, the pump body assembly includes a crankshaft, an upper muffler, an upper bearing, a secondary cylinder, a primary cylinder, a lower bearing and a lower muffler. The primary cylinder discharges medium-pressure gas after suction and compression. The medium-pressure gas is discharged to the lower muffler, passes through the lower bearing and the primary cylinder, enters the secondary cylinder and is compressed into high-pressure gas, and finally discharged from the pump body assembly through the upper muffler. Since the crankshaft is a hollow structure and the crankshaft is provided with oil guide holes at the positions corresponding to the upper bearing and the lower bearing, the lubricating oil in the compressor can enter the crankshaft and lubricate the upper bearing and the lower bearing through the oil guide holes. In order to facilitate the discharge of the lubricating oil in the crankshaft and avoid the accumulation of lubricating oil inside the crankshaft, the lower end of the crankshaft cannot be closed.

[0029] Therefore, a hole is usually provided in the bottom wall of the lower muffler to facilitate the passage of lubricating oil. In order to avoid direct communication between the inner cavity of the lower muffler and the inner cavity of the shell, the bottom wall of the lower muffler needs to be sealed with the lower end of the lower bearing to prevent the high-temperature and high-pressure refrigerant outside the pump body assembly from entering the lower muffler. A commonly used sealing method is to stamp an annular protrusion on the bottom wall of the lower muffler, and the annular protrusion is sealed with the lower end wall of the lower bearing. When the annular protrusion is used, there is a pressure difference because the outside of the pump body assembly is a high-temperature and high-pressure refrigerant, while the inside of the lower muffler is a medium-pressure refrigerant. In addition, due to the manufacturing precision of the lower bearing, the sealing is general, and the high-temperature and high-pressure refrigerant can easily enter the lower muffler, causing the suction air of the secondary cylinder to overheat and the performance of the compressor to decrease.

[0030] In order to improve the sealing performance between the lower muffler 280 and the lower bearing 270, refer to Figure 1 and Figure 2 As shown, a compressor 1000 according to an embodiment of the present invention can be used in refrigeration equipment, such as refrigerators, air conditioners and the like. The compressor 1000 according to the embodiment of the present invention comprises a housing 100, a pump assembly 200, a motor 300 and a liquid storage tank 400. The housing 100 comprises an upper housing portion 120, a middle housing portion 130 and a lower housing portion 140 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. An exhaust pipe 110 is provided at the upper end of the upper housing portion 120. The inner cavity of the exhaust pipe 110 is connected to the inner cavity of the housing 100. The refrigerant discharged from the pump assembly 200 is discharged from the housing 100 through the exhaust pipe 110. 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 below the upper bearing 230 at an interval. The upper muffler 220 is connected to the side of the upper bearing 230 away from the first cylinder 240. 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, and the second cylinder 260 is connected to the upper end of 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. The lower muffler 280 is connected to the side of the lower bearing 270 away from the second cylinder 260. The lower muffler 280 contains medium-pressure refrigerant, and the pump body assembly 200 contains high-pressure refrigerant. The pressure of the high-pressure refrigerant is greater than that of the medium-pressure refrigerant.

[0031] 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, the lower bearing 270 and the annular seal 500. 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 with the inner cavity of the lower muffler 280 and the compression chamber of the first cylinder 240.

[0032] The motor 300 is arranged in the housing 100 and above the pump body assembly 200, and the motor 300 is drivingly 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 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 both 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 drivingly connected to the crankshaft 210.

[0033] Reference Figure 2 and Figure 3 As shown, the lower bearing 270 includes a first shaft neck 271 protruding in a direction away from the second cylinder 260, and the first shaft neck 271 is provided with a first shaft hole 273 for the crankshaft 210 to pass through. The lower muffler 280 or the first shaft neck 271 is provided with at least one first mounting groove 272 arranged around the first shaft hole 273, for example, only the lower muffler 280 is provided with the first mounting groove 272, or only the first shaft neck 271 is provided with the first mounting groove 272. The number of the sealing member 500 is provided with at least one and the number is the same as the number of the first mounting groove 272, for example, the number of the sealing member 500 and the number of the first mounting groove 272 are both one, two or three. The sealing member 500 is correspondingly arranged in the first mounting groove 272 and arranged around the first shaft hole 273. The sealing member 500 is elastic and is sealed and connected between the lower muffler 280 and the first shaft neck 271. It should be noted that the sealing member 500 of the present embodiment is a sealing ring, which can be made of materials such as rubber or silicone. The sealing ring is suitable for occasions with a narrow sealing width.

[0034] Since the first mounting groove 272 is arranged around the first axial hole 273 of the first axial neck portion 271, and the annular seal 500 is arranged in the first mounting groove 272, the lower muffler 280 and the first axial neck portion 271 are jointly sealed and abutted against the seal 500. The seal 500 is elastic and can be deformed under the pressure of the lower muffler 280 and the first axial neck portion 271, thereby improving the sealing between the lower muffler 280 and the first axial neck portion 271, effectively preventing high-temperature and high-pressure refrigerant from entering the lower muffler 280 and causing the first cylinder 240 to overheat, which can improve the compression efficiency of the refrigerant and the volumetric efficiency, thereby improving the performance of the compressor 1000.

[0035] In order to quickly select a suitable seal 500 for different compressors 1000, in an embodiment of the present invention, in one group of first mounting grooves 272 and a seal 500 installed in the first mounting groove 272, the central circumference of the seal 500 is L, the maximum width of the first mounting groove 272 is t, and the number of seals 500 is n, satisfying: 0.055≤t×n / L≤0.32, for example, the value of t×n / L can be 0.055, 0.12, 0.21, 0.25, 0.3, 0.32, etc.

[0036] It is understandable that the central circumference of the seal 500, the width of the first mounting groove 272 and the number of seals 500 will affect the sealing. The longer the central circumference of the seal 500, the worse the sealing; the larger the width of the first mounting groove 272 and the more the number of seals 500, the better the sealing. Therefore, when the value of t×n / L is less than 0.055, the sealing between the lower muffler 280 and the lower bearing 270 is insufficient, and air leakage is likely to occur. When the value of t×n / L is greater than 0.32, the sealing margin between the lower muffler 280 and the lower bearing 270 is too large, and the cost increases. Therefore, a reasonable design of the value of t×n / L within the range of 0.055 to 0.32 can better guide the selection of the seal 500, avoid the situation where the sealing is insufficient or the sealing margin is too large to increase the cost, and ensure that the sealing of the seal 500 meets the relevant requirements.

[0037] In an embodiment of the present invention, the deformation of the seal 500 is e, which satisfies: 0.5≤e≤1.5. For example, the value of e can be 0.5, 0.7, 0.8, 1, 1.2, 1.5, etc. The deformation of the seal 500 can be calculated by the formula: deformation = (original diameter-compressed diameter) / original diameter×thickness. When e is less than 0.5, the deformation is insufficient, the sealing performance deteriorates, and the high-temperature and high-pressure refrigerant easily enters the lower muffler 280, resulting in overheating of the first cylinder 240 suction, a reduction in compression ratio, and a reduction in energy efficiency. When e is greater than 1.5, the seal 500 is excessively deformed and easily fails, which also leads to reduced sealing performance. Therefore, the value of e is reasonably designed to be within the range of 0.5 to 1.5, and the seal 500 forms a uniform contact stress zone after compression, which can improve the sealing between the lower muffler 280 and the first shaft neck 271.

[0038] Reference Figure 3As shown, in the first embodiment of the present invention, the lower muffler 280 is stamped from sheet metal, which is simple and convenient to manufacture and has lower cost. The first mounting groove 272 is provided on the lower end wall of the first axial neck portion 271, and the sealing member 500 is sealed and abutted between the end wall of the first axial neck portion 271 and the inner wall of the lower muffler 280. By arranging the sealing member 500 on the lower end wall of the first axial neck portion 271, assembly is more convenient, and the high-pressure refrigerant outside the pump body assembly 200 is effectively prevented from entering the lower muffler 280. In addition, the elasticity of the sealing member 500 can absorb the vibration energy transmitted from the lower muffler 280 to the lower bearing 270, thereby reducing the noise generated by the resonance of the lower bearing 270.

[0039] Reference Figure 4 As shown, in the second embodiment of the present invention, the first mounting groove 272 is provided on the end wall of the first journal 271, and the lower muffler 280 includes a shroud 281 and a cover plate 282, the shroud 281 surrounds and is connected to the edge of the lower bearing 270 and extends in a direction away from the second cylinder 260, and the shroud 281 and the first journal 271 are arranged at intervals. The shroud 281 can be integrally formed with the lower bearing 270 to improve the stability and reliability of the connection of the shroud 281, and effectively prevent the high-pressure refrigerant from entering the lower muffler 280 through the connection between the shroud 281 and the lower bearing 270. The cover plate 282 is in the shape of an annular plate and is connected to the lower end of the shroud 281, and the cover plate 282 is also sealed and connected to the sealing member 500. It can be understood that the processing accuracy of the lower end surface of the shroud 281 is easier to control, so the processing accuracy is higher, and it can effectively seal with the cover plate 282 to improve the sealing performance. At the same time, compared with the lower muffler 280 stamped from sheet metal, the overall thickness of the enclosure 281 and the cover plate 282 can be thicker, with better heat insulation effect, which can effectively improve the situation where the high-temperature refrigerant outside the pump body assembly 200 heats the medium-temperature refrigerant in the lower muffler 280 and reduce temperature rise.

[0040] Reference Figure 5As shown, in the third embodiment of the present invention, the lower muffler 280 includes a shroud 281 and a cover plate 282, the shroud 281 is connected to the edge of the lower bearing 270 and extends in the direction away from the second cylinder 260, and the shroud 281 and the first shaft neck 271 are arranged at intervals. The shroud 281 can be integrally formed with the lower bearing 270 to improve the stability and reliability of the connection of the shroud 281, and effectively prevent the high-pressure refrigerant from entering the lower muffler 280 through the connection between the shroud 281 and the lower bearing 270. The cover plate 282 is connected to the lower end of the shroud 281, and is provided with a first through hole 283 for the first shaft neck 271 to pass through. The inner wall of the first through hole 283 is surrounded by a first mounting groove 272, and the inner wall of the first through hole 283 is arranged toward the side wall of the first shaft neck 271, and the sealing member 500 is sealingly connected to the inner wall of the first through hole 283 and the side wall of the first shaft neck 271. It is understandable that the processing accuracy of the lower end surface of the enclosure 281 is easier to control, so the processing accuracy is higher, and it can effectively seal with the cover plate 282 to improve the sealing. At the same time, the overall thickness of the enclosure 281 and the cover plate 282 can be thicker than the lower silencer 280 stamped from the sheet metal, and the heat insulation effect is better, which effectively improves the situation where the high-temperature refrigerant outside the pump body assembly 200 heats the medium-temperature refrigerant in the lower silencer 280 and reduces the temperature rise.

[0041] Reference Figure 6 , Figure 7 and Figure 8As shown, in the fourth embodiment of the present invention, the compressor 1000 includes a shell 100, a pump body assembly 200, a motor 300 and a liquid storage tank 400, and an exhaust pipe 110 is provided at the upper end of the shell 100, and the inner cavity of the exhaust pipe 110 is connected to the inner cavity of the shell 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, a lower bearing 270 and a seal 500. The upper bearing 230 is fixedly connected to the inner wall of the housing 100, and the lower bearing 270 is arranged below the upper bearing 230 at an interval. The upper muffler 220 is connected to the side of the upper bearing 230 away from the first cylinder 240. 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, and the second cylinder 260 is connected to the upper end of 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. The lower muffler 280 is connected to the side of the lower bearing 270 away from the second cylinder 260. The lower muffler 280 contains medium-pressure refrigerant, and the pump body assembly 200 contains high-pressure refrigerant. The pressure of the high-pressure refrigerant is greater than that of the medium-pressure refrigerant.

[0042] 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, the lower bearing 270 and the annular seal 500. 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 with the inner cavity of the lower muffler 280 and the compression chamber of the first cylinder 240.

[0043] The motor 300 is arranged in the housing 100 and above the pump body assembly 200, and the motor 300 is drivingly 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 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 both 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 drivingly connected to the crankshaft 210.

[0044] The lower bearing 270 includes a first axial neck portion 271 protruding in a direction away from the second cylinder 260, and the first axial neck portion 271 is provided with a first axial hole 273 for the crankshaft 210 to pass through. The seal 500 is a metal part, and the seal 500 is connected to the pump body assembly 200. The seal 500 includes an annular sheet 510 located between the end of the first axial neck portion 271 and the lower muffler 280, and at least one end surface of the annular sheet 510 is provided with an annular protrusion 511, and the annular protrusion 511 protrudes toward the end of the first axial neck portion 271, or toward the lower muffler 280. The annular protrusion 511 is arranged around the first axial hole 273, and is sealed and connected between the end of the first axial neck portion 271 and the lower muffler 280. The central circumference of the annular protrusion 511 closest to the first axial hole 273 is L. Along the radial direction of the crankshaft 210, the maximum contact width between the annular plate 510 and the first shaft neck 271 is t. The number of annular protrusions 511 is n, satisfying: 0.055≤t×n / L≤0.32. For example, the value of t×n / L can be 0.055, 0.12, 0.21, 0.25, 0.3, 0.32, etc. It should be noted that the maximum contact width between the annular plate 510 and the first shaft neck portion 271 refers to: when the inner hole diameter of the annular plate 510 is larger than the hole diameter of the first shaft hole 273, the maximum contact width is the maximum distance between the inner wall of the annular plate 510 along the radial direction of the crankshaft 210 and the outer wall of the annular plate 510; when the inner hole diameter of the annular plate 510 is less than or equal to the hole diameter of the first shaft hole 273, the maximum contact width is the maximum distance between the hole wall of the first shaft hole 273 along the radial direction of the crankshaft 210 and the outer wall of the annular plate 510.

[0045] Since the annular protrusion 511 is arranged around the first axial hole 273 of the first axial neck portion 271 and is sealed and connected between the end of the first axial neck portion 271 and the lower muffler 280, the annular protrusion 511 is elastic and can be deformed under the pressure of the lower muffler 280 and the first axial neck portion 271, thereby improving the sealing between the lower muffler 280 and the first axial neck portion 271, effectively preventing high-temperature and high-pressure refrigerant from entering the lower muffler 280 and causing the first cylinder 240 to overheat, which can improve the compression efficiency of the refrigerant and the volumetric efficiency, thereby improving the performance of the compressor 1000.

[0046] It is understandable that the circumference of the annular protrusion 511, the maximum contact width between the annular sheet 510 and the first shaft neck portion 271, and the number of the annular protrusions 511 will affect the sealing performance. The longer the circumference of the annular protrusion 511, the worse the sealing performance; the larger the maximum contact width between the annular sheet 510 and the first shaft neck portion 271, and the more the number of the annular protrusions 511, the better the sealing performance. Therefore, when the value of t×n / L is less than 0.055, the sealing performance between the lower muffler 280 and the lower bearing 270 is insufficient, and air leakage is likely to occur. When the value of t×n / L is greater than 0.32, the sealing margin between the lower muffler 280 and the lower bearing 270 is too large, and the cost increases. Therefore, a reasonable design of the value of t×n / L within the range of 0.055 to 0.32 can better guide the structural design of the seal 500, avoid the situation where the sealing performance is insufficient or the sealing margin is too large, resulting in increased costs, and ensure that the sealing performance of the seal 500 meets the relevant requirements. Meanwhile, the metal seal 500 is suitable for occasions with a longer sealing width and has better sealing performance.

[0047] Reference Figure 8 As shown, in the embodiment of the present invention, two annular protrusions 511 are provided and spaced apart along the radial direction of the crankshaft 210, wherein one annular protrusion 511 protrudes toward the end of the first journal portion 271, and the other annular protrusion 511 protrudes toward the lower muffler 280. The two annular protrusions 511 can form two contact surfaces between the lower muffler 280 and the first journal portion 271, and a bidirectional seal is formed by the double contact surfaces, which effectively prevents the high-temperature and high-pressure refrigerant from entering the lower muffler 280, and prevents the first cylinder 240 from overheating due to suction, thereby improving the compression efficiency of the compressor 1000.

[0048] Reference Figure 7 and Figure 8 As shown, in the embodiment of the present invention, the sealing member 500 further includes a folded edge 520, which surrounds and is connected to the edge of the annular sheet 510 and extends upward, and the folded edge 520 is sealed and connected to the side wall of the first axial neck portion 271. Therefore, by providing the folded edge 520 and the annular protrusion 511, the path that the refrigerant needs to pass through is extended, the sealing effect can be further improved, and the high-temperature and high-pressure refrigerant outside the pump body assembly 200 can be effectively prevented from entering the inner cavity of the lower muffler 280 through the gap between the sealing member 500 and the first axial neck portion 271.

[0049] Since it is to prevent the high temperature and high pressure refrigerant from entering the medium temperature and medium pressure cavity, when the cylinder for medium pressure compression is the first cylinder 240, refer to Fig. 9As shown, in the fifth embodiment of the present invention, the compressor 1000 includes a housing 100, a pump assembly 200, a motor 300 and a liquid storage tank 400. The upper end of the housing 100 is provided with an exhaust pipe 110, and the inner cavity of the exhaust pipe 110 is connected to the inner cavity of the housing 100. The pump assembly 200 is arranged inside the housing 100, and the pump 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, a lower bearing 270 and a sealing member 500. The upper bearing 230 is fixedly connected to the inner wall of the housing 100, and the lower bearing 270 is arranged below the upper bearing 230 at intervals. The upper muffler 220 is connected to the side of the upper bearing 230 away from the first cylinder 240. The upper muffler 220 is filled with medium-pressure refrigerant, and the pump assembly 200 is filled with high-pressure refrigerant. The pressure of the high-pressure refrigerant is greater than that of the medium-pressure refrigerant. 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, and the second cylinder 260 is connected to the upper end of 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. The lower muffler 280 is connected to the side of the lower bearing 270 that is away from the second cylinder 260.

[0050] The crankshaft 210 is inserted through the upper muffler 220, the upper bearing 230, the first cylinder 240, the partition assembly 250, the second cylinder 260, the lower bearing 270 and the annular seal 500. 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 first cylinder 240 through the intake pipe 410.

[0051] The motor 300 is arranged in the housing 100 and above the pump body assembly 200, and the motor 300 is drivingly 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 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 both 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 drivingly connected to the crankshaft 210.

[0052] The upper muffler 220 is provided with a second through hole 222, the upper bearing 230 includes a second shaft neck 231 protruding in a direction away from the first cylinder 240 and passing through the second through hole 222, the second shaft neck 231 is provided with a second shaft hole 232 for the crankshaft 210 to pass through, and the inner wall of the second through hole 222 and / or the side wall of the second shaft neck 231 facing the second through hole 222 is provided with at least one second mounting groove 221 arranged around the second shaft hole 232, for example, the second mounting groove 221 is arranged on the upper muffler 220. The number of the sealing member 500 is the same as the number of the second mounting groove 221, for example, one, two or three. The sealing member 500 is annular and is correspondingly arranged in the second mounting groove 221 and arranged around the second shaft hole 232, and the sealing member 500 is sealingly connected between the upper muffler 220 and the second shaft neck 231. In one set of second mounting grooves 221 and the sealing member 500 mounted in the second mounting grooves 221, the central perimeter of the sealing member 500 is L, the maximum width of the second mounting groove 221 along the axial direction of the crankshaft 210 is t, and the number of the sealing members 500 is n, which satisfies: 0.055≤t×n / L≤0.32. For example, the value of t×n / L can be 0.055, 0.12, 0.21, 0.25, 0.3, 0.32, etc.

[0053] Since the second mounting groove 221 is arranged around the second axial hole 232 of the second axial neck portion 231, and the annular seal 500 is arranged in the second mounting groove 221, the upper muffler 220 and the second axial neck portion 231 are jointly sealed and abutted against the seal 500. The seal 500 is elastic and can be deformed under the pressure of the upper muffler 220 and the second axial neck portion 231, thereby improving the sealing between the upper muffler 220 and the second axial neck portion 231, effectively preventing high-temperature and high-pressure refrigerant from entering the upper muffler 220 and causing the second cylinder 260 to overheat, which can improve the compression efficiency of the refrigerant and the volumetric efficiency, thereby improving the performance of the compressor 1000.

[0054] It is understandable that the sealing performance is affected by the central circumference of the seal 500, the width of the second mounting groove 221 and the number of seals 500. The longer the central circumference of the seal 500, the worse the sealing performance; the larger the width of the second mounting groove 221 and the more the number of seals 500, the better the sealing performance. Therefore, when the value of t×n / L is less than 0.055, the sealing performance between the upper muffler 220 and the upper bearing 230 is insufficient, and air leakage is likely to occur. When the value of t×n / L is greater than 0.32, the sealing margin between the upper muffler 220 and the upper bearing 230 is too large, and the cost increases. Therefore, a reasonable design of the value of t×n / L within the range of 0.055 to 0.32 can better guide the selection of the seal 500, avoid the situation where the sealing performance is insufficient or the sealing margin is too large, resulting in increased costs, and ensure that the sealing performance of the seal 500 meets the relevant requirements.

[0055] Reference Fig.10 , Fig.11 and Fig.12 As shown, in an embodiment of the present invention, the intake pipe 410 of the liquid storage tank 400 is connected to the second cylinder 260. The rotor assembly 320 includes a rotor and a lower balancing block 330. The rotor is provided with a flow hole 322, which penetrates the rotor axially and is configured to allow the refrigerant to flow. The lower balancing block 330 is connected to the lower end of the rotor. 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 L1, 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 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, which satisfies: .

[0056] 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. 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.

[0057] Since the height of the lower balancing block 330 is higher and closer to the upper muffler 220, that is, the shortest distance L1 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. However, if H is too large, the height of the shell 100 will increase. For example, referring to Fig.14 As shown, Fig.14The horizontal axis represents the oil discharge rate, and the vertical axis represents the value of L1×H / (H1×D). Fig.14 The points in the figure represent the size of the oil discharge rate corresponding to the specific value of L1×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 L1×H / (H1×D). The value of L1×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 L1×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 L1×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.

[0058] Reference Fig.11 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.

[0059] Reference Fig.11As 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.

[0060] Reference Fig.10 As shown, in the embodiment of the present invention, the shortest distance L1 between the lower end surface of the rotor assembly 320 and the upper end surface of the upper muffler 220 satisfies: L1 ≥ 5mm, for example, the value of L1 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 L1 is less than 5mm, the shortest distance L1 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 L1 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.

[0061] In order to further reduce the disturbance of the lower balancing block 330 to the refrigerant, refer to Fig.10 and Fig.12As 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 .

[0062] Reference Fig.11 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.

[0063] Continue to refer to Fig.11As 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.

[0064] Reference Fig.12 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.

[0065] Continue to refer to Fig.12 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.

[0066] Continue to refer to Fig.12As 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.

[0067] Reference Fig.13 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.

[0068] Continue to refer to Fig.13 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.

[0069] A refrigeration device according to an embodiment of the present invention includes the compressor 1000 according to the above embodiment, and the refrigeration device may be an air conditioner, a refrigerator, or other equipment. 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 inside the housing 100, and the crankshaft 210 of the pump body assembly 200 is passed through the first cylinder 240, the second cylinder 260, the lower bearing 270, and the lower muffler 280, and the motor 300 is connected to the crankshaft drive 210. Therefore, when the crankshaft 210 rotates, the refrigerant in the second cylinder 260 can be compressed, and the compressed refrigerant first enters the lower muffler 280 and then enters the first cylinder 240 to continue compression, and then is discharged from the pump body assembly 200. After the refrigerant is discharged from the pump body assembly 200, it needs to pass through the motor 300 and flow upward, and finally be discharged from the housing 100. Since the first mounting groove 272 is arranged around the first shaft hole 273 of the first shaft neck portion 271, and the annular seal 500 is arranged in the first mounting groove 272, the lower muffler 280 and the first shaft neck portion 271 are sealed against the seal 500 together, and the seal 500 is elastic and can be deformed under the pressure of the lower muffler 280 and the first shaft neck portion 271, thereby improving the sealing between the lower muffler 280 and the first shaft neck portion 271, effectively preventing the high-temperature and high-pressure refrigerant from entering the lower muffler 280, resulting in the overheating of the suction air of the secondary cylinder, and improving the performance of the compressor 1000. Since the central circumference of the seal 500, the width of the first mounting groove 272 and the number of seals 500 will affect the sealing. In order to better guide the selection of seal 500 and avoid insufficient sealing or excessive sealing margin leading to increased costs, the value of t×n / L is limited to the range of 0.055 to 0.32 through the formula, which can ensure that the sealing of seal 500 meets the relevant requirements.

[0070] 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.

[0071] 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 includes a crankshaft, a first cylinder, a second cylinder, a lower muffler and a lower bearing, the first cylinder is located above the second cylinder, the second cylinder is connected to the upper end of the lower bearing, the lower muffler is connected to the side of the lower bearing away from the second cylinder, the lower bearing includes a first axial neck protruding in a direction away from the second cylinder, the first axial neck is provided with a first axial hole for the crankshaft to pass through, the pump body assembly is provided with at least one first mounting groove, the first mounting groove is provided on the lower muffler or the first axial neck and is arranged around the first axial hole; A motor, disposed in the housing and drivingly connected to the crankshaft; A liquid storage tank, comprising an intake pipe, wherein the intake pipe is connected to the second cylinder; At least one annular seal, the number of the seals is the same as the number of the first mounting grooves, the seals are correspondingly arranged in the first mounting grooves and arranged around the first shaft hole, and the seals are sealingly connected between the lower muffler and the first shaft neck; Among them, in one set of the first mounting grooves and the sealing member installed in the first mounting grooves, the central perimeter of the sealing member is L, the maximum width of the first mounting groove is t, the number of the sealing members is n, and the following conditions are satisfied: .

2. The compressor according to claim 1, characterized in that: The first mounting groove is provided on the end wall of the first journal portion, and the sealing member is sealingly abutted between the end wall of the first journal portion and the inner wall of the lower muffler.

3. The compressor according to claim 1, characterized in that: The first mounting groove is arranged on the end wall of the first shaft neck portion, and the lower muffler includes a surrounding plate and a cover plate. The surrounding plate is connected to the edge of the lower bearing and extends in the direction away from the second cylinder. The surrounding plate and the first shaft neck portion are spaced apart, and the cover plate is connected to the lower end of the surrounding plate and is sealed to the sealing member.

4. The compressor according to claim 1, characterized in that: The lower muffler includes a surrounding plate and a cover plate, the surrounding plate is connected to the edge of the lower bearing and extends in the direction away from the second cylinder, the surrounding plate and the first shaft neck portion are spaced apart, the cover plate is connected to the lower end of the surrounding plate, the cover plate is provided with a first through hole for the first shaft neck portion to pass through, the inner wall of the first through hole is surrounded by the first mounting groove, and the inner wall of the first through hole is arranged toward the side wall of the first shaft neck portion, and the sealing member is sealingly connected to the inner wall of the first through hole and the side wall of the first shaft neck portion.

5. The compressor according to claim 1, characterized in that: The deformation amount of the sealing member is e, which satisfies: 0.5≤e≤1.

5.

6. The compressor according to claim 1, characterized in that: The pump body assembly also includes an upper muffler and an upper bearing, the upper bearing is connected to the upper end of the first cylinder, the upper muffler is connected to the upper end of the upper bearing, the motor includes a rotor assembly and a stator assembly sleeved on the outside of the rotor assembly, the rotor assembly includes a lower balancing block and a rotor, the lower balancing block is connected to the lower end of the rotor, 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 L1, 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, 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 it satisfies: .

7. The compressor according to claim 1, characterized in that: The motor includes a rotor assembly and a stator assembly sleeved on the outside of the rotor assembly, the rotor assembly includes a rotor core, the rotor core is provided with a plurality of flow holes, the flow holes 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, the plurality of guide channels respectively penetrate the stator assembly axially, and the plurality of guide channels are arranged at intervals along the circumference of the stator assembly.

8. The compressor according to claim 7, characterized in that: The rotor core is provided with a mounting hole 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 of the stator assembly is S2, and the sum of the flow areas of all the flow guide channels is S4, satisfying: .

9. A compressor, characterized in that include: case; A pump body assembly is arranged in the housing, the pump body assembly includes a crankshaft, a first cylinder, a second cylinder, a lower muffler and a lower bearing, the first cylinder is located above the second cylinder, the second cylinder is connected to the upper end of the lower bearing, the lower muffler is connected to the side of the lower bearing away from the second cylinder, the lower bearing includes a first shaft neck protruding in a direction away from the second cylinder, the first shaft neck is provided with a first shaft hole for the crankshaft to pass through; A motor, disposed in the housing and drivingly connected to the crankshaft; A liquid storage tank, comprising an intake pipe, wherein the intake pipe is connected to the second cylinder; A seal connected to the pump body assembly, the seal comprising an annular sheet located between the end of the first shaft neck and the lower muffler, at least one end surface of the annular sheet being provided with an annular protrusion arranged around the first shaft hole, the annular protrusion being sealingly connected between the end of the first shaft neck and the lower muffler; The central circumference of the annular protrusion closest to the first shaft hole is L, the maximum contact width between the annular sheet and the first shaft neck along the radial direction of the crankshaft is t, the number of the annular protrusions is n, and the following is satisfied: .

10. The compressor according to claim 9, characterized in that: Two annular protrusions are provided and are spaced apart in the radial direction of the crankshaft, wherein one of the annular protrusions protrudes toward the end of the first journal portion, and the other annular protrusion protrudes toward the lower muffler.

11. A compressor, characterized in that include: case; A pump body assembly is arranged in the housing, the pump body assembly includes a crankshaft, an upper muffler, an upper bearing, a first cylinder and a second cylinder, the first cylinder is connected to the lower end of the upper bearing and is located above the second cylinder, the upper muffler is connected to the side of the upper bearing away from the first cylinder, the upper end surface of the upper muffler is provided with a second through hole, the upper bearing includes a second shaft neck portion protruding in a direction away from the first cylinder and passing through the second through hole, the second shaft neck portion is provided with a second shaft hole for the crankshaft to pass through, the pump body assembly is provided with at least one second mounting groove, the second mounting groove is located on the inner wall of the second through hole or the side wall of the second shaft neck portion facing the second through hole, and is arranged around the second shaft hole; A motor, disposed in the housing and drivingly connected to the crankshaft; A liquid storage tank, comprising an air intake pipe, wherein the air intake pipe is connected to the first cylinder; At least one annular seal, the number of the seal is the same as the number of the second mounting grooves, the seal is correspondingly arranged in the second mounting groove and arranged around the second shaft hole, and the seal is sealingly connected between the upper muffler and the second shaft neck; Among them, in one set of the second mounting grooves and the sealing member installed in the second mounting grooves, the central perimeter of the sealing member is L, the maximum width of the second mounting groove is t, the number of the sealing members is n, and the following is satisfied: .

12. Refrigeration equipment, characterized in that: Comprising the compressor according to any one of claims 1 to 11.

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