Compressor and refrigeration equipment

Abstract

The utility model discloses a compressor and refrigeration equipment and relates to the technical field of compressors, the compressor comprises a motor, a stator and a rotor, the rotor is rotatably arranged on the stator, the outer diameter and the inner diameter of the stator are R1 and R2 respectively, and a pump body assembly comprises a crankshaft. The crankshaft comprises a main shaft part, an auxiliary shaft part and an eccentric part arranged between the main shaft part and the auxiliary shaft part, the end, away from the eccentric part, of the main shaft part is connected with the rotor, the outer diameter of the main shaft part is D1, and the formula that D1 * R1 / R2 is larger than or equal to 15 and smaller than or equal to 30 is met. The outer diameter of the stator, the inner diameter of the stator and the outer diameter of the main shaft part of the crankshaft are reasonably set according to the ratio, on one hand, the split ratio of the motor can be improved to improve the efficiency of the motor so as to improve the energy efficiency of the compressor, and on the other hand, the rigidity of the crankshaft can be improved to improve the rigidity of the pump body assembly so as to reduce the noise during operation of the compressor.

Description

Technical Field

[0001] The utility model relates to the technical field of compressors, and particularly relates to a compressor and a refrigeration device. Background Art

[0002] A rotary compressor is composed of components such as an upper cover, a lower cover, a housing, a pump body assembly, and a motor. Among them, the motor includes a stator and a rotor, and the pump body assembly includes components such as a crankshaft, an upper flange, a cylinder, a roller, a sliding vane, and a lower flange. The cylinder is provided with a compression chamber. The eccentric part of the crankshaft is sleeved on the roller to drive the roller to roll in the compression chamber. The main shaft part of the crankshaft is connected to the rotor of the motor to make the crankshaft rotate.

[0003] Since the efficiency of the motor is positively correlated with the split ratio of the motor, the split ratio of the motor is small, resulting in low efficiency of the motor. However, when the outer diameter of the stator is constant, the larger the split ratio of the motor, the larger the outer diameter of the rotor, and the larger the distance between the center of gravity of the rotor and the center of the main shaft part of the crankshaft. When the rotor rotates, the bending force on the main shaft part of the crankshaft is larger, resulting in weakened stiffness of the pump body assembly, reduced energy efficiency of the compressor, and increased noise during compressor operation. 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 purpose, the utility model provides a compressor that can not only increase the split ratio of the motor but also improve the stiffness of the pump body assembly.

[0005] The utility model also provides a refrigeration device having the above compressor.

[0006] According to the compressor of the first aspect embodiment of the utility model, the compressor includes:

[0007] A motor, including a stator and a rotor, the rotor is rotatably arranged in the stator, and the maximum outer diameter and maximum inner diameter of the stator are R1 and R2 respectively;

[0008] A pump body assembly, including a crankshaft, the crankshaft includes a main shaft part, a sub-shaft part, and an eccentric part arranged between the main shaft part and the sub-shaft part. One end of the main shaft part away from the eccentric part is connected to the rotor, and the outer diameter of the main shaft part is D1, satisfying: 15 ≤ D1×R1 / R2 ≤ 30.

[0009] The compressor according to the embodiment of the utility model has at least the following beneficial effects:

[0010] By correlating the maximum outer diameter of the stator, the maximum inner diameter of the stator, and the outer diameter of the main shaft portion of the crankshaft, a rational ratio setting is adopted for the maximum outer diameter of the stator, the maximum inner diameter of the stator, and the outer diameter of the main shaft portion of the crankshaft. On the one hand, the split ratio of the motor can be increased to improve the efficiency of the motor, thereby improving the energy efficiency of the compressor. On the other hand, the stiffness of the crankshaft can be increased to improve the stiffness of the pump body assembly, thereby reducing the noise during the operation of the compressor.

[0011] According to some embodiments of the present invention, the pump body assembly further includes a cylinder and an upper flange connected to the cylinder. The cylinder is provided with a compression chamber, the eccentric portion is accommodated in the compression chamber, the upper flange is provided with a first shaft hole, the main shaft portion passes through the first shaft hole. Along the axial direction of the main shaft portion, the maximum height of the upper flange is H1, and the maximum thickness of the rotor is T, satisfying: 0.5 ≤ H1 / T ≤ 1.5.

[0012] According to some embodiments of the present invention, the pump body assembly further includes a lower flange. The lower flange is connected to the side of the cylinder away from the upper flange. The lower flange is provided with a second shaft hole, the secondary shaft portion passes through the second shaft hole. Along the axial direction of the main shaft portion, the maximum height of the lower flange is H2, satisfying: 0.3 ≤ H2 / T ≤ 1.5.

[0013] According to some embodiments of the present invention, the pump body assembly further includes a cylinder, an upper flange, and a lower flange. The upper flange is connected to one side in the thickness direction of the cylinder, and the lower flange is connected to the other side in the thickness direction of the cylinder. The cylinder is provided with a compression chamber, the eccentric portion is accommodated in the compression chamber, the upper flange is provided with a first shaft hole, the main shaft portion passes through the first shaft hole. Along the axial direction of the main shaft portion, the maximum height of the upper flange is H1, and the maximum height of the lower flange is H2, satisfying: 1 ≤ H1 / H2 ≤ 5.

[0014] According to some embodiments of the present invention, the ratio between the maximum inner diameter and the maximum outer diameter of the stator is R2 / R1, satisfying: 0.2 ≤ R2 / R1 ≤ 0.8.

[0015] According to some embodiments of the present invention, the outer diameter of the secondary shaft portion is D2, and the ratio between the outer diameter of the main shaft portion and the outer diameter of the secondary shaft portion is D1 / D2, satisfying: 1 ≤ D1 / D2 ≤ 1.5.

[0016] According to some embodiments of the present invention, the weight of the crankshaft is W1, and the weight of the rotor is W2, satisfying: 2 ≤ W2 / W1 ≤ 15.

[0017] According to some embodiments of the present utility model, the rotor includes a rotor core and a plurality of permanent magnets. The rotor core is provided with a plurality of mounting grooves corresponding to the permanent magnets one by one. The plurality of mounting grooves are arranged at intervals along the circumferential direction of the rotor core, and the permanent magnets are accommodated in the corresponding mounting grooves.

[0018] According to some embodiments of the present utility model, the maximum outer diameter of the rotor is R3, satisfying: 1 mm ≤ R2 - R3 ≤ 2 mm.

[0019] The refrigeration device according to the embodiment of the second aspect of the present utility model includes the pump body assembly described in the above embodiments.

[0020] The refrigeration device according to the embodiment of the second aspect of the present utility model has at least the following beneficial effects:

[0021] By adopting the compressor of the first aspect embodiment, by correlating the outer diameter of the stator, the inner diameter of the stator, and the outer diameter of the main shaft portion of the crankshaft, and setting a reasonable ratio for the outer diameter of the stator, the inner diameter of the stator, and the outer diameter of the main shaft portion of the crankshaft. On the one hand, it can improve the split ratio of the motor to improve the efficiency of the motor, thereby improving the energy efficiency of the compressor. On the other hand, it can improve the stiffness of the crankshaft to improve the stiffness of the pump body assembly, thereby reducing the noise during the operation of the compressor.

[0022] The additional aspects and advantages of the present utility model will be partially given in the following description, partially become obvious from the following description, or be understood through the practice of the present utility model. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] The following further describes the present utility model in conjunction with the drawings and embodiments, where:

[0024] Figure 1 is a schematic internal structure diagram of a compressor according to an embodiment of the present utility model;

[0025] Figure 2 is a schematic internal structure diagram of a pump body assembly according to an embodiment of the present utility model;

[0026] Figure 3 is a schematic internal structure diagram of a crankshaft according to an embodiment of the present utility model;

[0027] Figure 4 is an assembly schematic diagram of a motor according to an embodiment of the present utility model;

[0028] Figure 5 is a line graph of the motor efficiency at different values of D1 × R1 / R2;

[0029] Figure 6 is a line graph of the noise of the compressor at different values of D1 × R1 / R2.

[0030] Reference numerals in the drawings:

[0031] Motor 100, stator 110, stator core 111, stator slots 1111, winding 112, rotor 120, rotor core 121, mounting slots 1211, permanent magnet 122, pump body assembly 200, crankshaft 210, main shaft portion 211, auxiliary shaft portion 212, eccentric portion 213, cylinder 220, compressor 221, upper flange 230, first shaft hole 231, lower flange 240, second shaft hole 241, roller 250, housing 300, accommodation chamber 310. Detailed implementation manners

[0032] Embodiments of the present utility model will be described in detail below. Examples of the embodiments are shown in the accompanying drawings, where the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary only for explaining the present utility model and should not be construed as limiting the present utility model.

[0033] In the description of the present utility model, it should be understood that for orientation descriptions, such as up, down, etc., the orientation or positional relationship indicated is based on the orientation or positional relationship shown in the drawings. This 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 limiting the present utility model.

[0034] In the description of the present utility model, "a plurality of" refers to more than two. If there is a description of first and second, it is only for the purpose of distinguishing technical features and should not be construed as indicating or implying relative importance or implicitly indicating the quantity of the indicated technical features or the sequence of the indicated technical features.

[0035] In the description of the present utility model, unless otherwise clearly defined, terms such as "arrangement", "installation", "connection", etc. should be understood in a broad sense. Those skilled in the relevant technical field can reasonably determine the specific meanings of the above terms in the present utility model in combination with the specific content of the technical solution.

[0036] In the related art, a rotary compressor is composed of components such as an upper cover, a lower cover, a housing, a pump body assembly, and a motor. Among them, the motor includes a stator and a rotor, and the pump body assembly includes components such as a crankshaft, an upper flange, a cylinder, a roller, a sliding vane, and a lower flange. The cylinder is provided with a compression chamber, and the eccentric portion of the crankshaft is sleeved on the roller to drive the roller to roll in the compression chamber. The main shaft portion of the crankshaft is connected to the rotor of the motor to rotate the crankshaft.

[0037] Since the efficiency of the motor is positively correlated with the split ratio of the motor, and the split ratio of the motor is small, the efficiency of the motor is low. However, when the outer diameter of the stator is constant, the larger the split ratio of the motor, the larger the outer diameter of the rotor, and the larger the distance between the center of gravity of the rotor and the center of the main shaft portion of the crankshaft. When the rotor rotates, the bending force on the main shaft portion of the crankshaft is greater, resulting in a weakened stiffness of the pump body assembly, reduced energy efficiency of the compressor, and increased noise during compressor operation.

[0038] It should be noted that the split ratio of the motor is defined as the ratio of the inner diameter of the stator to the outer diameter of the stator, that is, R2 / R1. The size of the split ratio of the motor is positively correlated with the efficiency of the motor, that is, the larger the split ratio of the motor, the higher the efficiency of the motor. For example, when the outer diameter of the stator is constant, the larger the split ratio of the motor, the larger the inner diameter of the stator, that is, the larger the outer diameter of the rotor. The increase in the outer diameter of the rotor causes the center of mass of the rotor to shift outward, resulting in an increase in the distance between the center of mass of the rotor and the center of the main shaft portion. When the rotor rotates, the force exerted by the rotor on the main shaft portion along the radial direction of the main shaft portion increases, and the flexural deformation of the main shaft portion is large, resulting in a weakened stiffness of the pump body assembly and increased noise during compressor operation.

[0039] It should be pointed out that flexural deformation refers to the deformation of an object under force, and the property that the object cannot return to its original shape after the acting force is removed is called flexibility.

[0040] It should be noted that if the outer diameter of the main shaft portion increases, the weight of the crankshaft increases, the load on the rotor increases, resulting in a decrease in the efficiency of the motor and a decrease in the energy efficiency during compressor operation.

[0041] Based on this, an embodiment of the present invention provides a compressor. By correlating the maximum outer diameter of the stator 110, the maximum inner diameter of the stator 110, and the outer diameter of the main shaft portion 211 of the crankshaft 210, and setting a reasonable ratio for the maximum outer diameter of the stator 110, the maximum inner diameter of the stator 110, and the outer diameter of the main shaft portion 211 of the crankshaft 210, on the one hand, it can increase the split ratio of the motor 100 to improve the efficiency of the motor 100, thereby improving the energy efficiency of the compressor. On the other hand, it can increase the stiffness of the crankshaft 210 to improve the stiffness of the pump body assembly 200, thereby reducing the noise during compressor operation.

[0042] Refer to Figures 1 to 4 , Figure 1 is a schematic diagram of the internal structure of a compressor according to an embodiment of the present invention, Figure 2 is a schematic diagram of the internal structure of a pump body assembly 200 according to an embodiment of the present invention, Figure 3 is a schematic diagram of the internal structure of a crankshaft 210 according to an embodiment of the present invention, Figure 4 is an assembly schematic diagram of a motor 100 according to an embodiment of the present invention. For example Figure 1 , Figure 2As shown, the compressor of this embodiment includes a motor 100 and a pump body assembly 200. The motor 100 includes a stator 110 and a rotor 120. The rotor 120 is rotatably arranged inside the stator 110. The maximum outer diameter and maximum inner diameter of the stator 110 are R1 and R2 respectively. The pump body assembly 200 includes a crankshaft 210. The crankshaft 210 includes a main shaft portion 211, a sub-shaft portion 212, and an eccentric portion 213 arranged between the main shaft portion 211 and the sub-shaft portion 212. One end of the main shaft portion 211 away from the eccentric portion 213 is connected to the rotor 120. By correlating the maximum outer diameter of the stator 110, the maximum inner diameter of the stator 110, and the outer diameter of the main shaft portion 211 of the crankshaft 210, a rational ratio setting is adopted for the maximum outer diameter of the stator 110, the maximum inner diameter of the stator 110, and the outer diameter of the main shaft portion 211 of the crankshaft 210, that is, 15 ≤ D1×R1 / R2 ≤ 30, so as to ensure that compressors of different sizes can improve the efficiency of the motor 100 while increasing the stiffness of the pump body assembly 200, thereby improving the energy efficiency during the operation of the compressor and reducing the noise during the operation of the compressor.

[0043] For example, in order to ensure the efficiency of the motor 100 and increase the stiffness of the pump body assembly 200, while increasing the split ratio of the motor 100, it is necessary to increase the outer diameter of the main shaft portion 211. By correlating the maximum outer diameter of the stator 110, the maximum inner diameter of the stator 110, and the outer diameter of the main shaft portion 211 of the crankshaft 210, a rational ratio setting is adopted, that is, 15 ≤ D1×R1 / R2 ≤ 30. Within this range, both the split ratio of the motor 100 can be increased and the outer diameter of the main shaft portion 211 can be increased, so that the efficiency of the motor 100 and the stiffness of the pump body assembly 200 are increased, thereby improving the energy efficiency during the operation of the compressor and reducing the noise during the operation of the compressor.

[0044] Refer to Figure 5 , Figure 5 is a line graph of the efficiency of the motor 100 at different values of D1×R1 / R2. For example Figure 5 As shown, through experiments, it can be known that when the value range of D1×R1 / R2 is between 15 and 30, the efficiency of the motor 100 is at the peak. When the value range of D1×R1 / R2 is less than 15, the efficiency of the motor 100 is at the trough. When the value range of D1×R1 / R2 is greater than 30, the efficiency of the motor 100 is at the trough. Therefore, the value range of D1×R1 / R2 is set between 15 and 30 to ensure the efficiency of the motor 100, thereby improving the energy efficiency of the compressor.

[0045] Refer to Figure 6 , Figure 6A line graph of the noise of the compressor at different values of D1×R1 / R2. Through experiments, it can be known that when the value range of D1×R1 / R2 is between 15 and 30, the noise of the compressor is at the trough value; when the value range of D1×R1 / R2 is less than 15, the noise of the compressor is at the peak value; when the value range of D1×R1 / R2 is greater than 30, the noise of the compressor is at the peak value. Therefore, the value range of D1×R1 / R2 is set between 15 and 30 to reduce the noise of the compressor.

[0046] It should be noted that, for example Figure 4 As shown, the stator 110 includes a stator core 111 and a winding 112. The stator core 111 is provided with a plurality of stator slots 1111. Along the circumferential direction of the stator core 111, the plurality of stator slots 1111 are arranged at intervals. The winding 112 is wound in the corresponding stator slots 1111 so that the stator 110 can drive the rotor 120 to rotate. The rotor 120 includes a rotor core 121 and a permanent magnet 122. The rotor core 121 is provided with a plurality of mounting slots 1211. The plurality of mounting slots 1211 are arranged at intervals along the circumferential direction of the rotor core 121. The permanent magnet 122 is mounted in the corresponding mounting slots 1211, so as to drive the rotor 120 to rotate through the interaction between the magnetic field generated by the permanent magnet 122 and the magnetic field generated by the winding 112.

[0047] It can be understood that the stator core 111 includes a plurality of first silicon steel sheets. The plurality of first silicon steel sheets are stacked to form the stator core 111, which can improve the production efficiency of the stator core 111. Similarly, the rotor core 121 includes a plurality of second silicon steel sheets. The plurality of second silicon steel sheets are stacked to form the rotor core 121, which can improve the production efficiency of the rotor core 121.

[0048] For example Figure 1 、 Figure 2 As shown, in this embodiment, the pump body assembly 200 further includes a cylinder 220, an upper flange 230 and a lower flange 240. The cylinder 220 is provided with a compression chamber 221 for compressing the refrigerant. Along the axial direction of the cylinder 220, the upper flange 230 and the lower flange 240 are oppositely arranged. The upper flange 230 is connected to one side of the axial direction of the cylinder 220, and the lower flange 240 is connected to the side of the cylinder 220 far from the upper flange 230. The upper flange 230 is provided with a first shaft hole 231, and the lower flange 240 is provided with a second shaft hole 241. The eccentric part 213 of the crankshaft 210 is rotatably received in the compression chamber 221, the main shaft part 211 is rotatably passed through the first shaft hole 231, and the auxiliary shaft part 212 is rotatably passed through the second shaft hole 241. The upper flange 230 and the lower flange 240 support the crankshaft 210 to ensure that the rotor 120 and the crankshaft 210 rotate smoothly during the rotation process, and the rotor 120 will not have a large swing, which can improve the service life of the compressor.

[0049] It should be noted that the pump body assembly 200 further includes a roller 250 and a sliding vane. The roller 250 is sleeved on the eccentric portion 213, and the outer peripheral surface of the roller 250 is in rolling connection with the inner peripheral wall of the compression chamber 221. The cylinder 220 is provided with a sliding vane groove communicating with the compression chamber 221. The sliding vane is arranged in the sliding vane groove and can slide along the direction of entering or exiting the compression chamber 221. One end of the sliding vane abuts against the outer peripheral surface of the roller 250 to divide the compression chamber 221 into a high-pressure chamber and a low-pressure chamber.

[0050] It should be pointed out that the compressor further includes a housing 300. The housing 300 is provided with a receiving chamber 310. The pump body assembly 200 and the motor 100 are both installed in the receiving chamber 310. The stator core 111 is fixedly connected to the inner peripheral wall of the receiving chamber 310. The upper flange 230 is fixedly welded to the inner peripheral wall of the receiving chamber 310. The main shaft portion 211 and the rotor 120 are connected by interference fit. The crankshaft 210 and the rotor 120 can be regarded as a whole. During rotation, the main shaft portion 211 contacts the side wall of the first shaft hole 231, and the auxiliary shaft portion 212 contacts the side wall of the second shaft hole 241. Both the upper flange 230 and the lower flange 240 play a role in supporting the crankshaft 210 and the rotor 120.

[0051] For example Figure 1 、 Figure 2 As shown, in order to improve the stiffness of the pump body assembly 200, by correlating the maximum height H1 of the upper flange 230 and the maximum thickness T of the rotor 120 and adopting a reasonable ratio setting, that is, 0.5 ≤ H1 / T ≤ 1.5. Within this range, the contact area between the main shaft portion 211 and the upper flange 230 can be ensured, so that the upper flange 230 can effectively support the main shaft portion 211 to reduce the flexural deformation of the main shaft portion 211, thereby improving the stiffness of the pump body assembly 200.

[0052] It should be noted that the maximum height of the upper flange 230 refers to the distance between the upper surface and the lower surface of the upper flange 230 along the axial direction of the main shaft portion 211, that is, the length of the first shaft hole 231.

[0053] It should be noted that the rotor 120 further includes a balance weight, a first oil baffle, and a second oil baffle. Both the first oil baffle and the second oil baffle are in a ring structure. The first oil baffle is connected to one end of the rotor core 121 in the thickness direction, and the second oil baffle is connected to the other end of the rotor core 121 in the thickness direction. The main shaft portion 211 passes through the first oil baffle and the second oil baffle. The balance weight is arranged on the first oil baffle or the second oil baffle. Along the circumferential direction of the crankshaft 210, the eccentric portion 213 and the balance weight are symmetrically arranged to improve the dynamic balance performance of the whole crankshaft 210 and rotor 120.

[0054] It should be noted that the maximum thickness of the rotor 120 refers to the distance between the upper surface and the lower surface of the rotor core 121 along the axial direction of the main shaft portion 211, excluding the thickness of the balance weight, the thickness of the first oil baffle, and the thickness of the second oil baffle.

[0055] For example, when the maximum thickness T of the rotor 120 is constant, if H1 / T is less than 0.5, the contact area between the upper flange 230 and the main shaft portion 211 is too small, resulting in the main shaft portion 211 being prone to bending, the stiffness of the crankshaft 210 being reduced, and the stiffness of the pump body assembly 200 being reduced; if H1 / T is greater than 1.5, the height H1 of the upper flange 230 is too high. On the one hand, the contact area between the first shaft hole 231 and the main shaft portion 211 is too large, and under the condition of the high-speed operation of the crankshaft 210, the wear amount of the main shaft portion 211 increases, resulting in the reduction of the mechanical efficiency of the pump body assembly 200. On the other hand, the production cost of the upper flange 230 increases, resulting in the increase of the production cost of the compressor.

[0056] It should be noted that H1 / T can be 0.5, 0.6, 0.7, 0.8, 0.9, 1.0, 1.1, 1.2, 1.3, 1.4, 1.5, as long as the contact area between the main shaft portion 211 and the upper flange 230 can be ensured, and there is no limitation here.

[0057] In this embodiment, in order to improve the stiffness of the pump body assembly 200, by correlating the maximum height H2 of the lower flange 240 and the maximum thickness T of the rotor 120, a reasonable ratio is set, that is, 0.3 ≤ H2 / T ≤ 1.5. Within this range, the contact area between the auxiliary shaft portion 212 and the lower flange 240 can be ensured, so that the lower flange 240 can effectively support the auxiliary shaft portion 212, reducing the occurrence of the situation where the auxiliary shaft portion 212 is bent due to force, and improving the stiffness of the pump body assembly 200.

[0058] It should be noted that the maximum height of the lower flange 240 refers to the distance between the upper surface and the lower surface of the lower flange 240, that is, the length of the second shaft hole 241, which will not be elaborated here.

[0059] For example, when the maximum thickness T of the rotor 120 is constant, if H2 / T is less than 0.3, the contact area between the lower flange 240 and the auxiliary shaft portion 212 is too small, resulting in the auxiliary shaft portion 212 being prone to bending, the stiffness of the crankshaft 210 being reduced, and the stiffness of the pump body assembly 200 being reduced; if H2 / T is greater than 1.5, the height H2 of the lower flange 240 is too high. On the one hand, the contact area between the second shaft hole 241 and the auxiliary shaft portion 212 is too large, and under the condition of the high-speed operation of the crankshaft 210, the wear amount of the auxiliary shaft portion 212 increases, resulting in the reduction of the mechanical efficiency of the pump body assembly 200. On the other hand, the production cost of the lower flange 240 increases, resulting in the increase of the production cost of the compressor.

[0060] In this embodiment, in order to improve the efficiency of the motor 100, by reasonably setting the maximum thickness of the rotor 120, that is, 15 mm ≤ T ≤ 90 mm, so as to ensure that motors 100 of different sizes can improve the stiffness of the rotor 120 to extend the service life of the motor 100.

[0061] For example, the value of T can be 15 mm, 20 mm, 25 mm, 30 mm, 35 mm, 40 mm, 45 mm, 50 mm, 55 mm, 60 mm, 65 mm, 70 mm, 75 mm, 80 mm, 85 mm, 90 mm, which will not be elaborated here.

[0062] If the maximum thickness T of the rotor 120 is less than 15 mm, the maximum thickness of the rotor 120 is too small, the iron loss and copper loss of the motor 100 increase, and the efficiency of the motor 100 decreases. If the maximum thickness of the rotor 120 is greater than 90 mm, the maximum thickness of the rotor 120 is too large, the saturation current of the rotor iron core 121 increases, the magnetic resistance rises, and the efficiency of the motor 100 also decreases. Based on this, by reasonably setting the thickness of the rotor 120, both the iron loss and copper loss of the motor 100 can be reduced, and the magnetic resistance of the rotor iron core 121 can be reduced, thereby improving the efficiency of the motor 100.

[0063] For example Figure 1 As shown, the rotor 120 is located at one end of the main shaft portion 211 away from the upper flange 230. When the rotor 120 drives the crankshaft 210 to rotate, the force on the upper flange 230 is greater than the force on the lower flange 240. Therefore, the height of the upper flange 230 is designed to be greater than or equal to the height of the lower flange 240. In this embodiment, by correlating the maximum height H1 of the upper flange 230 and the maximum height H2 of the lower flange 240 and adopting a reasonable ratio setting, that is, 1 ≤ H1 / H2 ≤ 5, the flexural deformation of the crankshaft 210 can be reduced to reduce the swing amplitude when the rotor 120 rotates, and it can ensure that the rotor 120 and the crankshaft 210 rotate more smoothly, thereby reducing the noise during the operation of the compressor. For example, the value of H1 / H2 can be 1, 1.2, 1.4, 1.6, 1.8, 2, 2.2, 2.4, 2.6, 2.8, 3, 3.2, 3.4, 3.6, 6.8, 4, 4.2, 4.4, 4.6, 4.8, 5, etc., which is not limited here.

[0064] For example, if H1 / H2 is less than 1, when ensuring that the lower flange 240 can support the secondary shaft portion 212, since the force on the upper flange 230 is greater than the force on the lower flange 240, the upper flange 230 cannot effectively support the main shaft portion 211. When the rotor 120 drives the crankshaft 210 to rotate, the main shaft portion 211 is prone to bending, resulting in an increase in the wear amount of the main shaft portion 211 and affecting the mechanical efficiency of the pump body assembly 200;

[0065] If H1 / H2 is greater than 5, when ensuring that the lower flange 240 can effectively support the secondary shaft portion 212, the maximum height of the upper flange 230 is too high, resulting in too large a contact area between the side wall of the first shaft hole 231 and the main shaft portion 211, and still causing an increase in the wear amount of the main shaft portion 211, and the mechanical efficiency of the pump body assembly 200 is reduced.

[0066] In order to improve the efficiency of the motor 100, the stator 110 of this embodiment adopts a large split ratio design, that is, 0.2 ≤ R2 / R1 ≤ 0.8, which can increase the maximum outer diameter of the rotor 120, so that the rotor 120 can install a permanent magnet 122 with a larger volume to improve the magnetic performance of the permanent magnet 122, which is beneficial to improving the efficiency of the motor 100. As the split ratio increases, the most significant change is the increase in the inner diameter of the stator 110. The maximum inner diameter of the stator 110 is positively correlated with the torque of the motor 100. When the maximum inner diameter of the stator 110 increases, the torque of the motor 100 increases accordingly, and the efficiency of the motor 100 can be improved.

[0067] For example Figure 3 As shown, in this embodiment, by correlating the outer diameter D1 of the main shaft portion 211 and the outer diameter of the secondary shaft portion 212 as D2, and adopting a rational ratio setting, that is, 1 ≤ D1 / D2 ≤ 1.5, the stiffness of the crankshaft 210 can be improved to improve the operating stiffness of the pump body assembly 200.

[0068] Compared with the traditional crankshaft 210 made of cast iron, the material of the crankshaft 210 in this embodiment is selected as steel, and the steel can be No. 45 steel or No. 20 steel, etc. Compared with cast iron, steel has better yield strength, which enhances the ability of the crankshaft 210 to resist bending deformation, can reduce the swing amplitude of the rotor 120, and thus improve the operating stability of the rotor 120 and the crankshaft 210.

[0069] In this embodiment, on the basis that the material of the crankshaft 210 is steel, by correlating the weight W1 of the crankshaft 210 and the weight of the rotor 120 as W2, and adopting a reasonable ratio setting, that is, 2 ≤ W2 / W1 ≤ 15, the dynamic balance performance during the operation of the compressor can be improved, and the overall vibration of the compressor can be effectively reduced. For example, W2 / W1 can be 2, 3, 4, 5, 6, 7, 8, 9, 10, 11, 12, 13, 14, 15, etc., as long as the dynamic balance performance during the operation of the compressor can be improved, and there is no limitation here.

[0070] It should be noted that the weight of the rotor 120 refers to the sum of the weight of the rotor core 121 and the weight of the permanent magnet 122.

[0071] It should be noted that the crankshaft 210 and the rotor 120 are connected by an interference fit. When the crankshaft 210 and the rotor 120 are regarded as a whole, the center of mass of the whole of the crankshaft 210 and the rotor 120 mainly depends on the refrigeration of the rotor 120. Especially when the thickness of the rotor 120 increases, the center of mass of the whole of the crankshaft 210 and the rotor 120 gets closer to the rotor 120. At this time, the distance between the center of mass of the whole of the crankshaft 210 and the rotor 120 and the upper flange 230 increases. During the high-speed rotation of the crankshaft 210, the flexural deformation of the crankshaft 210 is greater, resulting in lower stiffness of the pump body assembly 200.

[0072] It should be noted that if W2 / W1 is less than 2, the mass of the crankshaft 210 is too large, the load of the rotor 120 increases, resulting in a decrease in the efficiency of the motor 100. If W2 / W1 is greater than 15, the distance between the center of mass of the whole of the crankshaft 210 and the rotor 120 and the upper flange 230 is too large. During the high-speed rotation of the crankshaft 210, the flexural deformation of the crankshaft 210 is large, the crankshaft 210 is prone to bending, resulting in lower stiffness of the pump body assembly 200 and an increase in the wear amount of the crankshaft 210.

[0073] In this embodiment, the maximum outer diameter of the rotor 120 is R3. By correlating the maximum inner diameter of the stator 110 and the maximum outer diameter of the rotor 120 and adopting a reasonable difference setting, that is, 1mm ≤ R2 - R3 ≤ 2mm. Under the condition of ensuring a reasonable gap between the outer peripheral surface of the rotor 120 and the inner peripheral surface of the stator 110, the maximum outer diameter of the rotor 120 can be increased, so that a larger-volume permanent magnet 122 can be installed in the installation groove 1211, so as to improve the magnetic performance of the permanent magnet 122, which is beneficial to improving the efficiency of the motor 100.

[0074] The refrigeration device according to the second aspect embodiment of the present utility model includes the compressor of the above embodiment.

[0075] The refrigeration device according to the embodiment of the present utility model adopts the compressor of the first aspect embodiment. By correlating the outer diameter of the stator 110, the inner diameter of the stator 110, and the outer diameter of the main shaft portion 211 of the crankshaft 210, and adopting a rationalized ratio setting for the outer diameter of the stator 110, the inner diameter of the stator 110, and the outer diameter of the main shaft portion 211 of the crankshaft 210. On the one hand, it can improve the split ratio of the motor 100 to improve the efficiency of the motor 100, thereby improving the energy efficiency of the compressor. On the other hand, it can improve the stiffness of the crankshaft 210 to improve the stiffness of the pump body assembly 200, thereby reducing the noise during the operation of the compressor.

[0076] Since the compressor adopts all the technical solutions of the pump body assembly 200 of the above embodiment, it at least has all the beneficial effects brought by the technical solutions of the above embodiment, which will not be elaborated here.

[0077] The embodiments of the present utility model have been described in detail above in conjunction with the accompanying drawings. However, the present utility model is not limited to the above embodiments, and various changes can be made without departing from the spirit of the present utility model within the scope of knowledge possessed by those of ordinary skill in the relevant art.

Claims

1. Compressor, characterized in that, Comprising: A motor, including a stator and a rotor, the rotor being rotatably disposed within the stator, the maximum outer diameter and the minimum inner diameter of the stator being R1 and R2 respectively; A pump body assembly, including a crankshaft, the crankshaft including a main shaft portion, a sub-shaft portion, and an eccentric portion disposed between the main shaft portion and the sub-shaft portion, one end of the main shaft portion remote from the eccentric portion being connected to the rotor, the outer diameter of the main shaft portion being D1, satisfying: 15 ≤ D1 × R1 / R2 ≤ 30.

2. The compressor according to claim 1, wherein: The pump body assembly further includes a cylinder and an upper flange connected to the cylinder, the cylinder having a compression chamber, the eccentric portion being received within the compression chamber, the upper flange having a first shaft hole, the main shaft portion passing through the first shaft hole, along the axial direction of the main shaft portion, the maximum height of the upper flange being H1, the maximum thickness of the rotor being T, satisfying: 0.5 ≤ H1 / T ≤ 1.

5.

3. The compressor according to claim 2, characterized in that: The pump body assembly further includes a lower flange, the lower flange being connected to a side of the cylinder remote from the upper flange, the lower flange having a second shaft hole, the sub-shaft portion passing through the second shaft hole, along the axial direction of the main shaft portion, the maximum height of the lower flange being H2, satisfying: 0.3 ≤ H2 / T ≤ 1.

5.

4. The compressor according to claim 1, characterized in that: The pump body assembly further includes a cylinder, an upper flange, and a lower flange, the upper flange being connected to one side in the thickness direction of the cylinder, the lower flange being connected to the other side in the thickness direction of the cylinder, the cylinder having a compression chamber, the eccentric portion being received within the compression chamber, the upper flange having a first shaft hole, the main shaft portion passing through the first shaft hole, along the axial direction of the main shaft portion, the maximum height of the upper flange being H1, the maximum height of the lower flange being H2, satisfying: 1 ≤ H1 / H2 ≤ 5.

5. The compressor according to claim 1, characterized in that: The ratio between the maximum inner diameter and the maximum outer diameter of the stator is R2 / R1, satisfying: 0.2 ≤ R2 / R1 ≤ 0.

8.

6. The compressor according to claim 1, wherein: The outer diameter of the sub-shaft portion is D2, satisfying: 1 ≤ D1 / D2 ≤ 1.

5.

7. The compressor according to claim 1, characterized in that: The weight of the crankshaft is W1, the weight of the rotor is W2, satisfying: 2 ≤ W2 / W1 ≤ 15.

8. The compressor according to claim 1, characterized in that: The rotor includes a rotor core, the rotor core being provided with a plurality of mounting grooves (1211), the plurality of mounting grooves (1211) being spaced apart circumferentially along the rotor core, and permanent magnets being provided within the mounting grooves (1211).

9. The compressor according to claim 1, characterized in that: The maximum outer diameter of the rotor is R3, satisfying: 1 mm ≤ R2 - R3 ≤ 2 mm.

10. Refrigeration equipment, characterized in that: Including the compressor according to any one of claims 1 to 9.

Images