Rotary compressor

Abstract

The utility model discloses a rotary compressor. The rotary compressor comprises a motor and a crankshaft, the motor is provided with a rotor iron core, a magnet groove is formed in the rotor iron core, a magnetic isolation bridge is formed between the magnet groove and the outer edge of the rotor iron core, the thickness t of the magnetic isolation bridge is smaller than or equal to 0.5 mm, and a shaft hole is formed in the rotor iron core; the crankshaft is matched with the shaft hole; an interval groove is formed in at least one of the inner surface of the shaft hole and the outer surface of the crankshaft, and a space for separating the outer surface of the crankshaft from the inner wall of the shaft hole is formed in the interval groove. According to the rotary compressor, the rotor core with the magnetic isolation bridge thickness t smaller than or equal to 0.5 mm is arranged, the crankshaft is assembled in the rotor core, the interval groove for separating the inner wall of the shaft hole of the rotor core from the outer surface of the crankshaft is formed in at least one of the rotor core and the crankshaft, friction between the rotor core and the crankshaft can be reduced through the arrangement of the interval groove, and the service life of the compressor is prolonged. Deformation of the crankshaft is reduced, safety of the rotary compressor is improved, and the service life of the rotary compressor is prolonged.

Description

Technical Field

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

[0002] The motor of a rotary compressor directly drives a rotary piston to rotate to compress the refrigerant. This type of rotary compressor is more suitable for small air conditioners, especially widely used in household air conditioners. The rotary compressor has the advantages of fewer components, simple structure, fewer vulnerable parts, and reliable operation.

[0003] In related technologies, in order to improve the demagnetization ability of the motor of a rotary refrigeration compressor, the number of rotor poles can be increased. However, increasing the number of rotor poles will cause the thickness of the magnetic bridge to decrease, and the connection rigidity at the magnetic bridge becomes poor. For example, in some rotary compressors with a rotor magnetic bridge thickness < 0.5 mm, using the conventional hot sleeve process to assemble the rotor and the crankshaft easily causes the magnetic bridge to be deformed and fractured by heat. Therefore, a cold sleeve process needs to be used to assemble the rotor and the crankshaft. At the same time, in order to reduce the deformation of the crankshaft during the cold pressing assembly of the crankshaft and the rotor and ensure that the holding force between the crankshaft and the rotor meets the requirements, the effective contact length between the rotor and the crankshaft needs to be redesigned. Summary of the Utility Model

[0004] The utility model aims to solve at least one of the technical problems existing in the prior art. For this reason, an object of the utility model is to provide a rotary compressor. The rotary compressor according to the utility model is provided with a rotor core with a magnetic isolation bridge thickness t ≤ 0.5 mm. A crankshaft is assembled inside the rotor core. At least one of the rotor core and the crankshaft is provided with a spacer groove that separates the inner wall of the shaft hole of the rotor core from the outer surface of the crankshaft. The provision of the spacer groove can reduce the friction between the rotor core and the crankshaft, reduce the deformation of the crankshaft, and improve the safety and service life of the rotary compressor.

[0005] The rotary compressor according to the utility model includes a motor and a crankshaft. The number of poles of the motor is P and satisfies: 10 ≤ P ≤ 12. The motor is provided with a rotor core. Magnet slots are formed on the rotor core. A magnetic isolation bridge is formed between the magnet slots and the outer edge of the rotor core. The thickness of the magnetic isolation bridge is t and satisfies: t ≤ 0.5 mm. A shaft hole is provided on the rotor core. The crankshaft is fitted with the shaft hole. Wherein, at least one of the inner surface of the shaft hole and the outer surface of the crankshaft is formed with a spacer groove, and a space that separates the outer surface of the crankshaft from the inner wall of the shaft hole is formed inside the spacer groove.

[0006] According to the rotary compressor of the present utility model, a rotor core with a magnetic isolation bridge thickness t ≤ 0.5 mm is provided. An axial hole for cooperating with the crankshaft is arranged inside the rotor core. At least one of the inner surface of the axial hole and the outer surface of the crankshaft is formed with spaced grooves. The arrangement of the spaced grooves can reduce the contact area between the crankshaft and the rotor core, reduce the friction between the crankshaft and the inner wall of the axial hole, thereby reducing the deformation of the crankshaft and the rotor core when the crankshaft and the rotor core are assembled, reducing the risk of damage to the motor and the crankshaft, and thus improving the safety and service life of the rotary compressor.

[0007] According to an embodiment of the present utility model, the fitting area between the inner surface of the axial hole and the outer surface of the crankshaft is S1, the area of the inner surface of the axial hole is S, and it satisfies: 0.5 ≤ S1 / S ≤ 0.95.

[0008] According to an embodiment of the present utility model, the length of the axial fitting between the crankshaft and the inner surface of the axial hole is L, the length of the rotor core in the axial direction is L1, and it satisfies: 0.6 ≤ L / L1 ≤ 0.9.

[0009] According to an embodiment of the present utility model, at least one end of the rotor core in the axial direction is further formed with a counterbore, and the axial hole extends to the counterbore.

[0010] According to an embodiment of the present utility model, the spaced grooves are formed on the inner wall of the axial hole and the length in the axial direction is L2. First and second counterbores are respectively arranged at both ends of the rotor core in the axial direction. The length of the first counterbore in the axial direction is L3, and the length of the second counterbore in the axial direction is L4; and it satisfies: L = L1 - L2 - L3 - L4.

[0011] According to an embodiment of the present utility model, the diameter of the axial hole is D1, the diameter of the spaced grooves is D2, and it satisfies: 0.1 mm ≤ D1 - D2 ≤ 10 mm.

[0012] According to an embodiment of the present utility model, the spaced grooves are formed on the outer surface of the crankshaft.

[0013] According to an embodiment of the present utility model, the crankshaft includes a connected first section and a second section. The diameter of the first section is larger than that of the second section, and the spaced grooves are defined between the outer surface of the second section and the end face of the first section; the diameter of the first section is D3, the diameter of the second section is D4, and it satisfies 0.1 mm ≤ D3 - D4 ≤ 1 mm.

[0014] According to an embodiment of the present utility model, a through-flow hole extending axially is formed on the rotor core. The through-flow hole is arranged on the outer periphery of the shaft hole, and the area of the through-flow hole is S2. The cross-sectional area between the inner wall of the shaft hole and the outer peripheral wall of the rotor core is S3, and it satisfies: 0.04 ≤ S2 / S3 ≤ 0.12.

[0015] According to an embodiment of the present utility model, there is no through-flow hole on the rotor core and it satisfies: 0.35 ≤ L / L1 ≤ 0.7.

[0016] According to an embodiment of the present utility model, the crankshaft is formed with a secondary shaft section, and a bearing is sleeved on the secondary shaft section. Wherein, the axial dimension of the bearing is L5, the length of the secondary shaft section is L6, and the end of the secondary shaft section protrudes from the bearing and satisfies: 1 mm ≤ L6 - L5 ≤ 6 mm.

[0017] According to an embodiment of the present utility model, stator slots are formed on the stator of the motor, and the number of stator slots is Q and it satisfies: 15 ≤ Q ≤ 18.

[0018] In summary, a rotor core, a crankshaft and a stator are provided on the motor of the rotary compressor. The number of stator slots Q is preferably 15, and the number of poles P is preferably 10. Magnet slots and magnetic isolation bridges are provided on the rotor core, and the thickness t of the magnetic isolation bridge satisfies t≤0.5mm. Among them, a shaft hole is provided on the rotor core, and the crankshaft can pass through the shaft hole and be assembled with the rotor core. During processing, through holes are usually provided on the rotor core, which can reduce the weight of the rotor core and improve the heat dissipation efficiency of the motor. When the rotor core is fitted with the crankshaft, the contact area between the inner surface of the shaft hole and the outer surface of the crankshaft is S1, and the area of the inner surface of the shaft hole is S, and 0.5≤S1 / S≤0.95 is satisfied. The value range of S1 / S is limited to the range of 0.5 to 0.95, which can ensure the stable assembly of the crankshaft and the rotor core while reducing the wear during the assembly of the crankshaft and the rotor core, and improving the safety and service life of the rotary compressor. Similarly, the length of the rotor core is L1, and the contact area between the crankshaft and the inner surface of the shaft hole in the axial direction is S1, and 0.6≤L / L1≤0.9 is satisfied. The value of L / L1 is set in the range of 0.6 to 0.9, which can ensure the stable assembly of the crankshaft and the rotor core while reducing the friction during the assembly of the crankshaft and the rotor core, and improving the safety and service life of the rotary compressor. It should be noted that when the rotor core is not provided with through holes, 0.35≤L / L1≤0.7; when the rotor core is provided with through holes, the total area of the through holes is S2, and the cross-sectional area between the inner wall of the shaft hole and the outer peripheral wall of the rotor core is S3, and 0.04≤S2 / S3≤0.12 is satisfied. Setting the value of S2 / S3 in the range of 0.04 to 0.12 can take into account the requirements of the rotor core structure strength while realizing the functions of heat dissipation and weight reduction of the through holes. First and second sinking grooves can also be provided at both axial ends of the rotor core. The length of the first sinking groove in the axial direction is L3, and the length of the second sinking groove in the axial direction is L4. When the spacer groove is formed on the inner wall of the shaft hole and the length in the axial direction is L2, L = L1 - L2 - L3 - L4. The setting of the first and second sinking grooves reduces the friction during the assembly of the rotor core and the crankshaft, and can reduce the deformation of the crankshaft. When the spacer groove is provided on the inner wall of the shaft hole, the diameter of the shaft hole is D1, and the diameter of the spacer groove is D2 and satisfies: 0.1mm≤D1 - D2≤10mm, which can ensure the structure strength of the rotor core while reducing the wear during the assembly of the crankshaft and the rotor core; when the spacer groove is provided on the crankshaft, the diameter of the first section is D3, and the diameter of the second section is D4, and 0.1mm≤D3 - D4≤1mm, which can ensure the structure strength of the rotor crankshaft while reducing the wear during the assembly of the crankshaft and the rotor core. In addition, a secondary shaft section is provided at the bottom of the crankshaft, and a bearing is sleeved on the outer periphery of the secondary shaft section. The length of the bearing in the axial direction is L5, and the length of the secondary shaft section is L6, and 1mm≤L6 - L5≤6mm is satisfied, which can reduce the space occupied by the secondary shaft section on the premise of ensuring that the assembly of the rotor core and the crankshaft will not damage the bearing, and is convenient for arranging other structures of the rotary compressor.

[0019] Additional aspects and advantages of the present utility model will be given in part in the following description, become apparent in part from the following description, or be learned through the practice of the present utility model. Description of the Drawings

[0020] The above and / or additional aspects and advantages of the present utility model will become apparent and be readily understood from the description of the embodiments in conjunction with the following drawings, wherein:

[0021] Figure 1 is a schematic structural view of a rotary compressor according to an embodiment of the utility model;

[0022] Figure 2 is a schematic view of the cooperation between a motor and a crankshaft according to an embodiment of the utility model;

[0023] Figure 3 is a schematic view of the cooperation between a rotor core and a crankshaft according to an embodiment of the utility model;

[0024] Figure 4 is a partial schematic view of the cooperation between a rotor core and a crankshaft according to an embodiment of the utility model;

[0025] Figure 5 is a schematic structural view of a rotor core according to an embodiment of the utility model;

[0026] Figure 6 is a schematic simplified view of a rotor core according to an embodiment of the present utility model.

[0027] Reference Signs:

[0028] Rotary compressor 1;

[0029] Rotor core 11, magnet slot 111, shaft hole 112, magnetic isolation bridge 113, current through hole 114;

[0030] Crankshaft 12, first section 121, second section 122;

[0031] Spacer groove 13;

[0032] First sink 141, second sink 142;

[0033] Bearing 15, auxiliary shaft section 16. Detailed Description of the Embodiment

[0034] The embodiments of the present utility model will be described in detail below. The examples of the embodiments are shown in the drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below by referring to the drawings are exemplary and are only used to explain the present utility model and should not be construed as a limitation to the present utility model.

[0035] In the related art, in order to improve the demagnetization ability of the motor of a rotary refrigeration rotary compressor, the number of rotor poles can be increased. However, increasing the number of rotor poles will result in a decrease in the thickness of the magnetic bridge and a poor connection rigidity at the magnetic bridge. For example, in some rotary compressors with a rotor magnetic bridge thickness < 0.5 mm, using a conventional hot sleeve process to assemble the rotor and the crankshaft easily causes the magnetic bridge to be deformed and fractured by heat. Therefore, a cold sleeve process needs to be used to assemble the rotor and the crankshaft. At the same time, in order to reduce the deformation of the crankshaft during the cold press fitting of the crankshaft and the rotor and ensure that the holding force between the crankshaft and the rotor meets the requirements, the effective contact length between the rotor and the crankshaft needs to be redesigned.

[0036] Next, refer to Figures 1-6 to describe a rotary compressor according to an embodiment of the present invention.

[0037] The rotary compressor 1 according to the present invention includes a motor and a crankshaft 12. The number of motor poles is P and satisfies: 10 ≤ P ≤ 12. The motor is provided with a rotor core 11. A magnet groove 111 is formed on the rotor core 11. A magnetic isolation bridge 113 is formed between the magnet groove 111 and the outer edge of the rotor core 11. The thickness of the magnetic isolation bridge 113 is t and satisfies: t ≤ 0.5 mm. A shaft hole 112 is provided on the rotor core 11; the crankshaft 12 is fitted with the shaft hole 112; wherein, at least one of the inner surface of the shaft hole 112 and the outer surface of the crankshaft 12 is formed with a spaced groove 13, and a space for separating the outer surface of the crankshaft 12 from the inner wall of the shaft hole 112 is formed in the spaced groove 13.

[0038] The rotary compressor 1 according to the present invention is provided with a motor. The number of motor poles P satisfies: 10 ≤ P ≤ 12, that is, the motor of the present invention can be a 10-pole motor or a 12-pole motor, and among them, a 10-pole motor can be preferably selected. A rotor core 11 is provided inside the motor. A magnet groove 111 for assembling a permanent magnet is provided on the rotor core 11. A magnetic isolation bridge 113 is formed between the magnet groove 111 and the outer edge of the rotor core 11. The magnetic isolation bridge 113 can limit magnetic leakage and improve the utilization rate of the permanent magnet. At the same time, in order to improve the demagnetization ability of the rotary compressor 1, the structural dimensions such as the number of poles of the rotor core 11 and the thickness of the magnetic isolation bridge 113 need to be reasonably designed. For example, the rotary compressor 1 in the present invention can adopt a rotor core 11 with a magnetic isolation bridge 113 thickness t ≤ 0.5 mm. In the rotary compressor 1 of the present invention, the number of rotor poles is large and the thickness of the magnetic isolation bridge 113 is small, which can improve the demagnetization ability of the rotary compressor 1.

[0039] The rotor core 11 is provided with a shaft hole 112, and the crankshaft 12 can be assembled into the shaft hole 112 and has an interference fit with at least a part of the inner wall of the shaft hole 112 so as to facilitate the linkage between the crankshaft 12 and the rotor core 11. In the rotor core 11 with t ≤ 0.5 mm, the assembly of the crankshaft 12 and the rotor core 11 can adopt the cold fitting process. As Figure 2 shown, the rotor core 11 can be sleeved on the outer periphery of the crankshaft 12 axially from top to bottom through the cold fitting process. During the cold fitting process of the rotor core 11, the crankshaft 12 will generate a resistance from bottom to top on the rotor core 11, which can also be understood as friction force. Correspondingly, the rotor core 11 will generate a pressure from top to bottom on the crankshaft 12. At the same time, there will also be a normal contact pressure between the crankshaft 12 and the rotor core 11, and the interaction force between the crankshaft 12 and the rotor core 11 will affect the assembly of the crankshaft 12 and the rotor core 11, and even affect the use of the entire rotary compressor 1. Specifically, an interval groove 13 can be formed between the inner wall of the shaft hole 112 and the crankshaft 12 to form a space for separating the crankshaft 12 and the inner wall of the shaft hole 112, so as to reduce the friction force between the crankshaft 12 and the inner wall of the shaft hole 112. For example, the interval groove 13 can be formed on the crankshaft 12, or on the inner wall of the shaft hole 112, or on both the crankshaft 12 and the inner wall of the shaft hole 112. The specific setting position and size of the interval groove 13 and other designs can be determined according to the actual specifications of the crankshaft 12 and the rotor core 11. The setting of the interval groove 13 can reduce the contact area between the crankshaft 12 and the rotor core 11, reduce the friction between the crankshaft 12 and the inner wall of the shaft hole 112, and further reduce the deformation of the crankshaft 12 and the rotor core 11 during the assembly of the crankshaft 12 and the rotor core 11, reducing the risk of damage to the motor and the crankshaft 12, and thus improving the safety and service life of the rotary compressor 1.

[0040] According to an embodiment of the present invention, the fitting area between the inner surface of the shaft hole 112 and the outer surface of the crankshaft 12 is S1, and the area of the inner surface of the shaft hole 112 is S, and it satisfies: 0.5 ≤ S1 / S ≤ 0.95. The setting of the interval groove 13 can reduce the friction between the crankshaft 12 and the inner wall of the shaft hole 112. However, when the area of the interval groove 13 is too large, it will also affect the stability of the assembly of the crankshaft 12 and the rotor core 11. Therefore, it is necessary to reasonably design the area of the interval groove 13, or the fitting area between the crankshaft 12 and the inner wall of the shaft hole 112.

[0041] Specifically, the fitting area between the inner surface of the shaft hole 112 and the outer surface of the crankshaft 12 is S1, and the area of the inner surface of the shaft hole 112 is S. At this time, the area of the spacer groove 13 can be understood as S - S1. To balance the two requirements of stable assembly of the crankshaft 12 and the rotor core 11 and small deformation between the crankshaft 12 and the rotor core 11, it is necessary to satisfy: 0.5 ≤ S1 / S ≤ 0.95. It can be simply understood that when S1 / S < 0.5, the area of the spacer groove 13 at this time is too large, and the fitting area between the crankshaft 12 and the inner wall of the shaft hole 112 is too small. The assembly of the rotating shaft and the rotor core 11 is unstable, and there is a risk of the crankshaft 12 and the rotor core 11 separating during the operation of the rotary compressor 1, seriously affecting the safety of the rotary compressor 1; when S1 / S > 0.95, the area of the spacer groove 13 is too small at this time, and the fitting area between the crankshaft 12 and the inner wall of the shaft hole 112 is close to the total area of the inner surface of the shaft hole 112. At this time, the assembly of the crankshaft 12 and the rotor core 11 is stable. However, the friction between the rotor core 11 and the crankshaft 12 during assembly is large, and the crankshaft 12 and the rotor core 11 are deformed greatly under force and are easily damaged, which will affect the safety and service life of the rotary compressor 1. Therefore, setting the ratio between the fitting area of the crankshaft 12 and the shaft hole 112 and the total area of the inner wall of the shaft hole 112 within the range of 0.5 to 0.95 can ensure the stable assembly of the crankshaft 12 and the rotor core 11 while reducing the wear between the crankshaft 12 and the rotor core 11 during assembly, improving the safety and service life of the rotary compressor 1.

[0042] According to an embodiment of the present invention, the length of the axial fit between the crankshaft 12 and the inner surface of the shaft hole 112 is L, and the length of the rotor core 11 in the axial direction is L1 and satisfies: 0.6 ≤ L / L1 ≤ 0.9. The setting of the spacer groove 13 can reduce the friction between the crankshaft 12 and the inner wall of the shaft hole 112. However, when the length of the spacer groove 13 in the axial direction is too large, it will also affect the stability of the assembly of the crankshaft 12 and the rotor core 11. Therefore, it is necessary to reasonably design the length of the spacer groove 13, or the length of the axial fit between the crankshaft 12 and the inner wall of the shaft hole 112.

[0043] Specifically, the length of the axial fit between the inner surface of the shaft hole 112 and the outer surface of the crankshaft 12 is L, and the total length of the inner surface of the shaft hole 112 in the axial direction is L1. It can also be understood that the length of the rotor core 11 in the axial direction is L1. At this time, the length of the spacer groove 13 in the axial direction can be understood as L1 - L. To balance the two requirements of stable assembly of the crankshaft 12 and the rotor core 11 and small deformation between the crankshaft 12 and the rotor core 11, it is necessary to satisfy: 0.6 ≤ L / L1 ≤ 0.9. It can be simply understood that when L / L1 < 0.6, the length of the spacer groove 13 in the axial direction is too large at this time, and the length of the axial fit between the crankshaft 12 and the inner wall of the shaft hole 112 is too small. The assembly of the rotating shaft and the rotor core 11 is unstable, and there is a risk of the crankshaft 12 separating from the rotor core 11 during the operation of the rotary compressor 1, seriously affecting the safety of the rotary compressor 1; when L / L1 > 0.9, the length of the spacer groove 13 in the axial direction is too small at this time, and the length L of the axial fit between the crankshaft 12 and the inner wall of the shaft hole 112 is close to the total length of the inner surface of the shaft hole 112 in the axial direction (the length of the rotor core 11 in the axial direction) L1. At this time, the assembly of the crankshaft 12 and the rotor core 11 is stable. However, the friction during the assembly of the rotor core 11 and the crankshaft 12 is large, and the deformation of the crankshaft 12 and the rotor core 11 under force is large, which is easy to damage and will affect the safety and service life of the rotary compressor 1. Therefore, setting the ratio between the length L of the axial fit between the crankshaft 12 and the shaft hole 112 and the total length of the inner wall of the shaft hole 112 in the axial direction (the length of the rotor core 11 in the axial direction) L1 within the range of 0.6 to 0.9 can ensure the stable assembly of the crankshaft 12 and the rotor core 11 while reducing the wear during the assembly of the crankshaft 12 and the rotor core 11, improving the safety and service life of the rotary compressor 1.

[0044] According to an embodiment of the present invention, at least one end of the rotor core 11 in the axial direction is further formed with a counterbore, and the shaft hole 112 extends to the counterbore. As Figure 2 shown, during actual processing, at least one end of the rotor core 11 in the axial direction can be provided with a counterbore. The design of the counterbore can reduce the resistance when the rotor core 11 is sleeved on the crankshaft 12, reduce the friction between the crankshaft 12 and the inner wall of the shaft hole 112, reduce the deformation of the crankshaft 12 and the rotor core 11 during assembly, and thus improve the safety and service life of the rotary compressor 1. In addition, the design of the counterbore can also reduce the weight of the rotor core 11 and achieve the lightweight design of the rotary compressor 1.

[0045] It should be noted that when a counterbore is provided on the rotor core 11, the area of the spacer groove 13 in the above embodiment is no longer S - S1, and the length of the spacer groove 13 in the axial direction is no longer L1 - L.

[0046] According to an embodiment of the present utility model, a spacer groove 13 is formed on the inner wall of the shaft hole 112 and has an axial length of L2. First and second counterbores 141 and 142 are respectively provided at both axial ends of the rotor core 11. The first counterbore 141 has an axial length of L3, and the second counterbore 142 has an axial length of L4; and it satisfies: L = L1 - L2 - L3 - L4.

[0047] First and second counterbores 141 and 142 are respectively provided at both axial ends of the rotor core 11. The design of the first and second counterbores 141 and 142 can reduce the assembly difficulty between the rotor core 11 and the crankshaft 12 and reduce the deformation during the assembly of the crankshaft 12 and the rotor core 11. When the rotor core 11 and the crankshaft 12 are assembled, the spacer groove 13 can be provided on the inner wall of the shaft hole 112. At this time, the axial length of the spacer groove 13 is L2, and the axial lengths of the first and second counterbores 141 and 142 are L3 and L4 respectively, then L = L1 - L2 - L3 - L4, that is, the axial fitting length between the crankshaft 12 and the inner wall of the shaft hole 112 is the axial length of the rotor core 11 minus the axial lengths of the first counterbore 141, the second counterbore 142, and the spacer groove 13. L = L1 - L2 - L3 - L4 clarifies the relationship between the axial fitting length between the crankshaft 12 and the rotor core 11 and the lengths of various parts on the rotor core 11. By clarifying the clear data relationship, the consistency and product quality during the production of the rotor core 11 and the crankshaft 12 can be improved. At the same time, it is also convenient for subsequent analysis and improvement of the rotary compressor 1.

[0048] According to an embodiment of the present utility model, the diameter of the shaft hole 112 is D1, and the diameter of the spacing groove 13 is D2, and they satisfy: 0.1 mm ≤ D1 - D2 ≤ 10 mm. Since the spacing groove 13 is provided on the inner wall of the shaft hole 112, therefore, the size of the spacing groove 13 will affect the structural strength of the rotor core 11 itself. Specifically, when machining the spacing groove 13 on the inner wall of the shaft hole 112, the diameter of the spacing groove 13 is D2, and the diameter of the shaft hole 112 is D1, and it is required to satisfy: 0.1 mm ≤ D1 - D2 ≤ 10 mm. It can be understood that: when D1 - D2 < 0.1 mm, the diameter of the spacing groove 13 is close to the diameter of the shaft hole 112, that is, the diameter of the spacing groove 13 is relatively too large with respect to the diameter of the shaft hole 112 at this time, and the strength of the rotor core 11 is low. When the rotary compressor 1 operates, the rotor core 11 is easily damaged; when D1 - D2 > 10 mm, the diameter of the spacing groove 13 is relatively too small with respect to the diameter of the shaft hole 112. Since the crankshaft 12 and the rotor core 11 are in interference fit in diameter, it is difficult to achieve the function of reducing the friction between the crankshaft 12 and the inner wall of the shaft hole 112 when the diameter of the spacing groove 13 is too small, and thus it is easy to cause damage to the crankshaft 12 during the assembly with the rotor core 11. Therefore, setting the difference between the diameter D1 of the shaft hole 112 and the diameter D2 of the spacing groove 13 within the range of 0.1 mm to 10 mm can ensure the structural strength of the rotor core 11 while reducing the wear during the assembly of the crankshaft 12 and the rotor core 11.

[0049] According to an embodiment of the present utility model, a spacing groove 13 is formed on the outer surface of the crankshaft 12. Different from the above embodiment in which the spacing groove 13 is provided on the inner wall (inner surface) of the shaft hole 112, the spacing groove 13 in this embodiment can be provided on the crankshaft 12.

[0050] According to an embodiment of the present utility model, the crankshaft 12 includes a first section 121 and a second section 122 connected to each other. The diameter of the first section 121 is larger than that of the second section 122, and a spacing groove 13 is defined between the outer surface of the second section 122 and the end surface of the first section 121; the diameter of the first section 121 is D3, the diameter of the second section 122 is D4, and they satisfy 0.1 mm ≤ D3 - D4 ≤ 1 mm.

[0051] When the spacing groove 13 is provided on the crankshaft 12, the structure of the crankshaft 12 is different from that of the crankshaft 12 in the above embodiment in which the spacing groove 13 is provided on the inner wall of the shaft hole 112. Specifically, the crankshaft 12 is provided with a first section 121 and a second section 122 connected to each other, as Figure 3As shown, the diameter of the first section 12 is greater than that of the second section 122. One second section 122 is connected between two first sections 12 to define an interval groove 13. Among them, the diameter of the first section 12 is D3, and the diameter of the second section 122 is D4, and the following is satisfied: 0.1mm ≤ D3 - D4 ≤ 1mm. It can be understood that when D3 - D4 < 0.1mm, the diameter of the interval groove 13 is close to the diameter of the crankshaft 12, that is, the diameter of the interval groove 13 is relatively too large compared to the diameter of the crankshaft 12 at this time, and the strength of the crankshaft 12 is low. When the rotary compressor 1 operates, the crankshaft 12 is easily damaged; when D3 - D4 > 1mm, the diameter of the interval groove 13 is relatively too small compared to the diameter of the shaft hole 112. Since the crankshaft 12 and the rotor core 11 are in an interference fit in diameter, it is difficult to achieve the function of reducing the friction between the crankshaft 12 and the inner wall of the shaft hole 112 with a too small diameter of the interval groove 13, and thus it is easy to cause damage to the crankshaft 12 during the assembly with the rotor core 11. Therefore, setting the difference between the diameter D3 of the first section 12 and the diameter D4 of the second section 122 within the range of 0.1mm to 1mm can ensure the structural strength of the rotor crankshaft 12 while reducing the wear during the assembly of the crankshaft 12 and the rotor core 11.

[0052] According to an embodiment of the present invention, a through-flow hole 114 extending axially is formed on the rotor core 11. The through-flow hole 114 is provided on the outer periphery of the shaft hole 112, and the area of the through-flow hole 114 is S2. The cross-sectional area between the inner wall of the shaft hole 112 and the outer peripheral wall of the rotor core 11 is S3, and the following is satisfied: 0.04 ≤ S2 / S3 ≤ 0.12.

[0053] During actual processing, flow holes 114 can be formed in the rotor core 11. The flow holes 114 can penetrate the rotor core 11 axially. The flow holes 114 can be used to allow a cooling medium to flow through, which is beneficial to heat dissipation, can reduce the temperature during the operation of the motor, extend the service life of the motor. At the same time, the flow holes 114 can also play a role in reducing the weight of the rotor core 11. However, the design of the flow holes 114 needs to be determined according to the actual size of the rotor core 11 to avoid insufficient structural strength of the rotor core 11 caused by the setting of the flow holes 114 and not meeting the requirements of the rotary compressor 1. Specifically, the flow holes 114 can be arranged on the outer periphery of the shaft hole 112. The area of the flow holes 114 is S2. It should be noted that the area of the flow holes 114 here refers to the sum of the axial cross-sectional areas of all the flow holes 114 on the entire rotor core 11; the axial cross-sectional area of the rotor core 11 is S3. It should be noted that the axial cross-sectional area of the rotor core 11 here refers to the annular cross-section between the inner wall of the shaft hole 112 and the outer peripheral wall of the rotor core 11, and satisfies: 0.04 ≤ S2 / S3 ≤ 0.12. It can be understood that when S2 / S3 < 0.04, the area S2 of the flow holes 114 is too small relative to the axial cross-sectional area S3 of the rotor core 11, and it is difficult to achieve the functions of heat dissipation, weight reduction, noise reduction, etc. of the required flow holes 114; when S2 / S3 > 0.12, the area S2 of the flow holes 114 is too large relative to the axial cross-sectional area S3 of the rotor core 11, and setting the flow holes 114 with such a size will greatly reduce the structural strength of the rotor core 11, and further reduce the safety of the rotary compressor 1. Therefore, setting the value of S2 / S3 between 0.04 and 0.12 can take into account the structural strength of the rotor core 11 meeting the requirements while realizing the functions of heat dissipation, weight reduction, etc. of the flow holes 114.

[0054] According to an embodiment of the present utility model, there is no current-carrying hole 114 on the rotor core 11 and it satisfies: 0.35 ≤ L / L1 ≤ 0.7. The current-carrying hole 114 may not be provided on the rotor core 11 either. However, different from the rotor core 11 provided with the current-carrying hole 114, the length L of the fit between the crankshaft 12 and the inner wall of the shaft hole 112 in the axial direction and the length L1 of the rotor core 11 in the axial direction should satisfy: 0.35 ≤ L / L1 ≤ 0.7. It can be simply understood that when L / L1 < 0.35, the length of the spacer groove 13 in the axial direction is too large at this time, and the length of the fit between the crankshaft 12 and the inner wall of the shaft hole 112 in the axial direction is too small. The assembly of the rotating shaft and the rotor core 11 is unstable, and there is a risk of the crankshaft 12 separating from the rotor core 11 during the operation of the rotary compressor 1, seriously affecting the safety of the rotary compressor 1; when L / L1 > 0.7, the length of the spacer groove 13 in the axial direction is too small at this time, and the length L of the fit between the crankshaft 12 and the inner wall of the shaft hole 112 in the axial direction is close to the total length (the length of the rotor core 11 in the axial direction) L1 of the inner surface of the shaft hole 112 in the axial direction. At this time, the assembly of the crankshaft 12 and the rotor core 11 is stable. However, the friction during the assembly of the rotor core 11 and the crankshaft 12 is large, the force deformation of the crankshaft 12 and the rotor core 11 is large, and it is easy to be damaged, which will affect the safety and service life of the rotary compressor 1.

[0055] It should be noted that, since there is no current-carrying hole 114 on the rotor core 11 in this embodiment, compared with the 0.6 ≤ L / L1 ≤ 0.9 satisfied in the embodiment where the rotor core 11 is provided with the current-carrying hole 114, there is no current-carrying hole 114 in this embodiment, and there is no space in the rotor core 11 to facilitate the deformation of the rotor core 11. Therefore, it is necessary to increase the length of the spacer groove 13 (that is, the value of L is appropriately reduced, for example, L / L1 = 0.35) to reduce the assembly difficulty between the rotor core 11 and the crankshaft 12. Since there is no current-carrying hole 114 inside the rotor core 11 at this time, the structural strength of the rotor core 11 still meets the requirements; similarly, the value of L / L1 cannot exceed 0.7. For example: in this embodiment, the value of L / L1 cannot be 0.9 as in the embodiment where the rotor core 11 is provided with the current-carrying hole 114, otherwise the assembly resistance between the rotor core 11 and the crankshaft 12 is still too large, and the crankshaft 12 will be damaged.

[0056] According to an embodiment of the present utility model, the crankshaft 12 is formed with a secondary shaft section 16, and a bearing 15 is sleeved on the secondary shaft section 16; wherein, the dimension of the bearing 15 in the axial direction is L5, the length of the secondary shaft section 16 is L6, and the end of the secondary shaft section 16 protrudes from the bearing 15 and satisfies: 1 mm ≤ L6 - L5 ≤ 6 mm. As Figure 2As shown, a countershaft section 16 is formed at the bottom of the crankshaft 12, and a bearing 15 is sleeved on the outer periphery of the countershaft section 16. Since the rotor core 11 is assembled with the crankshaft 12 by being sleeved onto the crankshaft 12 from top to bottom, the rotor core 11 will apply a force from top to bottom to the crankshaft 12, and the end of the countershaft section 16 will be deformed by the force. Therefore, the length of the countershaft section 16 needs to be greater than the axial length of the bearing 15 to avoid damaging the bearing 15 due to pressure during assembly. Specifically, the length of the countershaft section 16 is L6, and the axial dimension of the bearing 15 is L5, and the following is satisfied: 1 mm ≤ L6 - L5 ≤ 6 mm. It can be understood that when L6 - L5 < 1 mm, the distance between the bearing 15 and the end of the countershaft section 16 is too close, and the bearing 15 is easily damaged when the rotor core 11 is assembled with the crankshaft 12; when L6 - L5 > 6 mm, the distance between the bearing 15 and the end of the countershaft section 16 is too far. At this time, the length of the countershaft section 16 is relatively long, which will affect the assembly of other structures of the rotary compressor 1 and increase the cost at the same time.

[0057] According to an embodiment of the present invention, stator slots are formed on the stator of the motor, and the number of stator slots is Q and satisfies: 15 ≤ Q ≤ 18. The stator slots are suitable for the structure of assembling windings. A larger number of stator slots can increase the magnetic field strength, but at the same time, it will reduce the structural strength of the stator. Motors with a larger number of poles can usually provide a larger starting torque. Therefore, the number of stator slots and the number of poles of the motor need to be reasonably planned. For example, the number of stator slots Q is preferably 15, and the number of poles P of the motor is preferably 10, which can balance the structural strength of the stator and improve the performance of the motor at the same time.

[0058] In summary, the motor of the rotary compressor 1 is provided with a rotor core 11, a crankshaft 12 and a stator, the number of stator slots Q is preferably 15, the number of stages P is preferably 10, the rotor core 11 is provided with a magnet slot 111 and a magnetic isolation bridge 113, and the thickness of the magnetic isolation bridge 113 is t≤0.5mm. Among them, the rotor core 11 is provided with an axial hole 112, and the crankshaft 12 can be assembled with the rotor core 11 after passing through the axial hole 112. During processing, a flow hole 114 can usually be provided on the rotor core 11, and the flow hole 114 can reduce the weight of the rotor core 11 and improve the heat dissipation efficiency of the motor. When the rotor core 11 is matched with the crankshaft 12, the area of the inner surface of the shaft hole 112 and the outer surface of the crankshaft 12 is S1, the area of the inner surface of the shaft hole 112 is S, and 0.5≤S1 / S≤0.95 is satisfied, and the value range of S1 / S is limited to the range of 0.5 to 0.95, which can ensure that the crankshaft 12 and the rotor core 11 are stably assembled while reducing the wear of the crankshaft 12 and the rotor core 11 during assembly, thereby improving the safety and service life of the rotary compressor 1. Similarly, the length of the rotor core 11 is L1, the area of the crankshaft 12 and the inner surface of the shaft hole 112 in the axial direction is S1, and 0.6≤L / L1≤0.9 is satisfied, and the value of L / L1 is set in the range of 0.6 to 0.9, which can ensure that the crankshaft 12 and the rotor core 11 are stably assembled while reducing the friction of the crankshaft 12 and the rotor core 11 during assembly, thereby improving the safety and service life of the rotary compressor 1. It should be noted that when the rotor core 11 is not provided with the flow holes 114, 0.35≤L / L1≤0.7; when the rotor core 11 is provided with the flow holes 114, the total area of the flow holes 114 is S2, the cross-sectional area between the inner wall of the shaft hole 112 and the outer peripheral wall of the rotor core 11 is S3, and 0.04≤S2 / S3≤0.12 is satisfied. Setting the value of S2 / S3 to 0.04-0.12 can take into account the structural strength of the rotor core 11 meeting the requirements while realizing the heat dissipation, weight reduction and other functions of the flow holes 114. A first recessed groove 141 and a second recessed groove 142 may be further provided at both ends of the rotor core 11 in the axial direction. The axial length of the first recessed groove 141 is L3, and the axial length of the second recessed groove 142 is L4. When the spacing groove 13 is formed on the inner wall of the shaft hole 112 and the axial length is L2, L=L1-L2-L3-L4. The provision of the first recessed groove 141 and the second recessed groove 142 reduces the friction when the rotor core 11 and the crankshaft 12 are assembled, and can reduce the deformation of the crankshaft 12.When the spacing groove 13 is arranged on the inner wall of the shaft hole 112, the diameter of the shaft hole 112 is D1, and the diameter of the spacing groove 13 is D2, and they satisfy: 0.1 mm ≤ D1 - D2 ≤ 10 mm, which can ensure the structural strength of the rotor core 11 while reducing the wear during the assembly of the crankshaft 12 and the rotor core 11; when the spacing groove 13 is arranged on the crankshaft 12, the diameter of the first section 121 is D3, the diameter of the second section 122 is D4, and they satisfy: 0.1 mm ≤ D3 - D4 ≤ 1 mm, which can ensure the structural strength of the rotor crankshaft 12 while reducing the wear during the assembly of the crankshaft 12 and the rotor core 11. In addition, a secondary shaft section 16 is arranged at the bottom of the crankshaft 12, a bearing 15 is sleeved on the outer periphery of the secondary shaft section 16, the axial length of the bearing 15 is L5, the length of the secondary shaft section 16 is L6, and they satisfy: 1 mm ≤ L6 - L5 ≤ 6 mm, which can reduce the space occupied by the secondary shaft section 16 on the premise of ensuring that the assembly of the rotor core 11 and the crankshaft 12 will not damage the bearing 15, and is convenient for arranging other structures of the rotary compressor 1.

[0059] In the description of the present utility model, it should be understood that the orientation or positional relationship indicated by the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc. is the orientation or positional relationship based on the orientation or positional relationship shown in the drawings. It is only for the convenience of describing the present utility model and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus should not be construed as a limitation to the present utility model.

[0060] In the description of the present utility model, the "first feature" and "second feature" may include one or more of such features.

[0061] In the description of the present utility model, the meaning of "a plurality of" is two or more.

[0062] In the description of the present utility model, the first feature being "above" or "below" the second feature may include the first and second features being in direct contact, or may include the first and second features not being in direct contact but being in contact through other features therebetween.

[0063] In the description of the present utility model, the first feature being "above", "above the" and "on the" second feature includes the first feature being directly above and obliquely above the second feature, or merely indicating that the horizontal height of the first feature is higher than that of the second feature.

[0064] In the description of this specification, the descriptions referring to terms such as "one embodiment", "some embodiments", "schematic embodiments", "examples", "specific examples", or "some examples", etc. mean that the specific features, structures, materials, or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present utility model. In this specification, the schematic expressions of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials, or characteristics described can be combined in a suitable manner in any one or more embodiments or examples.

[0065] Although the embodiments of the present utility model have been shown and described, those of ordinary skill in the art can understand that various changes, modifications, substitutions, and variations can be made to these embodiments without departing from the principles and spirit of the present utility model, and the scope of the present utility model is defined by the claims and their equivalents.

Claims

1. A rotary compressor, characterized in that, Including: A motor, the number of poles of the motor is P and satisfies: 10 ≤ P ≤ 12. The motor is provided with a rotor core, magnet slots are formed on the rotor core, a magnetic isolation bridge is formed between the magnet slots and the outer edge of the rotor core, the thickness of the magnetic isolation bridge is t and satisfies: t ≤ 0.5 mm, and a shaft hole is provided on the rotor core; A crankshaft, the crankshaft is fitted with the shaft hole; wherein Spaced grooves are formed on at least one of the inner surface of the shaft hole and the outer surface of the crankshaft, and a space for spacing the outer surface of the crankshaft from the inner wall of the shaft hole is formed in the spaced grooves; Wherein The fitting area between the inner surface of the shaft hole and the outer surface of the crankshaft is S1, the area of the inner surface of the shaft hole is S, and satisfies: 0.5 ≤ S1 / S ≤ 0.

95.

2. The rotary compressor according to claim 1, wherein The length of the axial fit between the crankshaft and the inner surface of the shaft hole is L, the length of the rotor core in the axial direction is L1 and satisfies: 0.6 ≤ L / L1 ≤ 0.

9.

3. The rotary compressor according to claim 2, wherein At least one end of the rotor core in the axial direction is further formed with a counterbore, and the shaft hole extends to the counterbore.

4. The rotary compressor according to claim 3, wherein, The spaced groove is formed on the inner wall of the shaft hole and the length in the axial direction is L2. The two ends of the rotor core in the axial direction are respectively provided with a first counterbore and a second counterbore. The length of the first counterbore in the axial direction is L3, and the length of the second counterbore in the axial direction is L4; and satisfies: L = L1 - L2 - L3 - L4.

5. The rotary compressor according to claim 4, characterized in that, The diameter of the shaft hole is D1, the diameter of the spaced groove is D2 and satisfies: 0.1 mm ≤ D1 - D2 ≤ 10 mm.

6. The rotary compressor according to claim 1, characterized in that, The spaced groove is formed on the outer surface of the crankshaft.

7. The rotary compressor according to claim 6, wherein, The crankshaft includes a connected first section and a second section. The diameter of the first section is larger than that of the second section, and a spaced groove is defined between the outer surface of the second section and the end face of the first section; the diameter of the first section is D3, the diameter of the second section is D4, and satisfies 0.1 mm ≤ D3 - D4 ≤ 1 mm.

8. The rotary compressor according to claim 1, wherein, A through-flow hole extending in the axial direction is formed on the rotor core. The through-flow hole is arranged on the outer periphery of the shaft hole, and the area of the through-flow hole is S2. The cross-sectional area between the inner wall of the shaft hole and the outer peripheral wall of the rotor core is S3, and satisfies: 0.04 ≤ S2 / S3 ≤ 0.

12.

9. The rotary compressor according to claim 1, wherein, There is no through-flow hole on the rotor core and satisfies: 0.35 ≤ L / L1 ≤ 0.

7.

10. The rotary compressor according to claim 1, characterized in that, The crankshaft is formed with a sub-shaft section, and a bearing is sleeved on the sub-shaft section; wherein The axial dimension of the bearing is L5, the length of the sub-shaft section is L6, and the end of the sub-shaft section protrudes from the bearing and satisfies: 1 mm ≤ L6 - L5 ≤ 6 mm.

11. The rotary compressor according to any one of claims 1 to 10, characterized in that, Stator slots are formed on the stator of the motor, the number of stator slots is Q and satisfies: 15 ≤ Q ≤ 18.

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