CN117477822A - Rotor assembly, variable frequency motor and compressor - Google Patents

Abstract

The invention discloses a rotor assembly, a variable frequency motor and a compressor, wherein the rotor assembly comprises a rotor iron core, permanent magnets, a rotor end plate and a connecting piece, the rotor iron core is provided with a magnet groove, and the permanent magnets are arranged in the magnet groove; the rotor iron core comprises a first iron core section and a second iron core section, wherein the first iron core section is provided with a first shaft hole used for being connected with a crankshaft pipe section of the crankshaft seat, the second iron core section is provided with a second shaft hole used for being connected with the crankshaft, the aperture of the first shaft hole is larger than that of the second shaft hole, the second iron core section is provided with a contact end face contacted with the end face of the crankshaft pipe section, and the contact end face is provided with an oil storage structure; the connecting piece passes through the rotor end plate and the rotor core to connect the rotor end plate, the rotor core and the permanent magnets together. According to the technical scheme, the friction between the rotor assembly and the crankcase can be reduced, the lubrication effect between the rotor assembly and the crankcase is optimized, and the friction loss of the compressor can be effectively reduced.

Description

Rotor assembly, variable frequency motor and compressor

Technical Field

The invention relates to the technical field of motors, in particular to a rotor assembly, a variable frequency motor and a compressor.

Background

In the related art, a crank shaft pipe section of a crank case is arranged in a rotor, a friction pair exists between the lower end face of the crank shaft pipe section and the rotor, and the lubrication condition of the friction pair between the crank case and the rotor is relatively insufficient, so that the friction loss of a compressor can be increased, and the overall efficiency of the compressor is affected.

Disclosure of Invention

The invention mainly aims to provide a rotor assembly, which aims to reduce friction between the rotor assembly and a crank case, optimize lubrication effect between the rotor assembly and the crank case, effectively reduce friction loss of a compressor, reduce abnormal abrasion risk, ensure stable operation of the compressor and further improve overall efficiency of the compressor.

To achieve the above object, the present invention provides a rotor assembly comprising:

the rotor iron core is provided with a magnet groove, the rotor iron core comprises a first iron core section and a second iron core section, the first iron core section is provided with a first shaft hole used for being connected with a crankshaft section of a crankshaft seat, the second iron core section is provided with a second shaft hole used for being connected with a crankshaft, the aperture of the first shaft hole is larger than that of the second shaft hole, the second iron core section is provided with a contact end face contacted with the end face of the crankshaft section, and the contact end face is provided with an oil storage structure;

the permanent magnet is arranged in the magnet groove; and

a rotor end plate and a connecting member passing through the rotor end plate and the rotor core to connect the rotor end plate, the rotor core, and the permanent magnets together.

Optionally, the oil storage structure includes a plurality of oil storage holes provided on the contact end face.

Optionally, the rotor core further includes a third core segment, the second core segment is located between the first core segment and the third core segment, the first core segment the second core segment and the third core segment are a plurality of core lamination layers, the oil storage hole axially penetrates through the second core segment, and one side of the third core segment, which is close to the second core segment, is closed the oil storage hole.

Optionally, the plurality of oil storage holes are arranged on the contact end surface in an annular array with the center of the second shaft hole as the center.

Alternatively, the spacing angle θ between any adjacent two oil storage holes satisfies 15°+.θ+.180°.

Optionally, the distance L between the center of the oil storage hole and the edge of the second shaft hole is 1 mm-13 mm.

Optionally, the diameter d of the oil storage hole is 1mm less than or equal to d less than or equal to 5mm.

Optionally, the depth h of the oil storage hole is more than or equal to 2mm and less than or equal to 21mm.

Optionally, the oil storage holes are identical in shape and size.

Optionally, the cross-sectional shape of the oil storage hole is one or more of a circle, a triangle, a rectangle, and a star.

Optionally, the oil storage hole is configured as a laser etched hole, or an ultrasonic etched hole, or an electrochemical etched hole or an electric spark machined hole.

Optionally, the height H1 of the rotor core and the height H2 of the permanent magnet satisfy 0.90.ltoreq.h1/h2.ltoreq.0.99.

Optionally, the rotor end plate includes first end plate and second end plate, first end plate and second end plate are located respectively the axial both ends of rotor core, first end plate is close to first iron core section, first end plate with the second end plate will the rotor core with the permanent magnet centre gripping is fixed through the connecting piece.

Optionally, the height H1 of the rotor core and the thickness B1 of the first end plate satisfy B1 Σ 0.015H1.

Optionally, the height H of the rotor core and the thickness B2 of the second end plate satisfy B2 ≡ 0.015H1.

Optionally, the total length K of the connecting piece is 1.05-1.ltoreq.K/(H1+B1+B2) -1.2.

The invention also provides a variable frequency motor, which comprises the rotor assembly.

The invention also provides a compressor comprising the variable frequency motor.

The technical scheme of the invention is that a rotor iron core, a permanent magnet, a rotor end plate and a connecting piece are adopted, wherein the rotor iron core is provided with a magnet groove, and the permanent magnet is arranged in the magnet groove; the rotor core comprises a first core section and a second core section, wherein the first core section is provided with a first shaft hole used for being connected with a crankshaft section of the crankshaft seat, the second core section is provided with a second shaft hole used for being connected with the crankshaft, the aperture of the first shaft hole is larger than that of the second shaft hole, the second core section is provided with a contact end face contacted with the end face of the crankshaft section, and the contact end face is provided with an oil storage structure; the connecting piece passes through the rotor end plate and the rotor core to connect the rotor end plate, the rotor core and the permanent magnet together. In the related art, a crank shaft pipe section of a crank case is arranged in a rotor, a friction pair exists between the lower end face of the crank shaft pipe section and the rotor, the lubrication condition between the crank case and the rotor is relatively insufficient, and the phenomenon of dry grinding is easy to occur. Through arranging the oil storage structure at the contact terminal surface of second iron core section, oil storage structure can store a certain amount of lubricating oil, and lubricating oil in the oil storage structure can splash out in the rotation, perhaps because the rotor beats and throws away to can lubricate rotor and bent axle, rotor and crankcase, guarantee lubrication condition between crankcase and the rotor subassembly, reduce the friction between rotor subassembly and the crankcase, optimize lubrication effect between the two, can effectively reduce the friction loss of compressor, alleviate abnormal wear risk, guarantee that the compressor operates steadily, and then promote the complete machine efficiency of compressor.

Drawings

In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings that are required in the embodiments or the description of the prior art will be briefly described, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and other drawings may be obtained according to the structures shown in these drawings without inventive effort for a person skilled in the art.

FIG. 1 is a schematic view of a rotor assembly according to an embodiment of the present invention;

FIG. 2 is a cross-sectional view taken at A-A of FIG. 1;

FIG. 3 is an enlarged view of a portion of the portion I of FIG. 2;

FIG. 4 is an exploded view of the rotor assembly of FIG. 1;

fig. 5 is a schematic structural view of the second core segment of fig. 4;

fig. 6 is a schematic structural view of the third core segment of fig. 4.

Reference numerals illustrate:

the achievement of the objects, functional features and advantages of the present invention will be further described with reference to the accompanying drawings, in conjunction with the embodiments.

Detailed Description

The following description of the embodiments of the present invention will be made clearly and fully with reference to the accompanying drawings, in which it is evident that the embodiments described are only some, but not all embodiments of the invention. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.

It should be noted that all directional indicators (such as up, down, left, right, front, and rear … …) in the embodiments of the present invention are merely used to explain the relative positional relationship, movement, etc. between the components in a particular posture (as shown in the drawings), and if the particular posture is changed, the directional indicator is changed accordingly.

Furthermore, the description of "first," "second," etc. in this disclosure is for descriptive purposes only and is not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include at least one such feature. In addition, the technical solutions of the embodiments may be combined with each other, but it is necessary to base that the technical solutions can be realized by those skilled in the art, and when the technical solutions are contradictory or cannot be realized, the combination of the technical solutions should be considered to be absent and not within the scope of protection claimed in the present invention.

Because of domestic occasion, it is steady that the compressor is required to operate, and the noise is little, efficient, and energy efficiency ratio is high. With the increasing market demands of the compressor of the variable frequency refrigerator, the performance requirements of the motor in the refrigerator compressor are also higher and higher. The compressor inevitably vibrates during operation, and even causes up-and-down movement of the rotor, and abnormal wear exists between the lower end of the crank tube of the crankcase and the rotor.

In the related art, a crank shaft pipe section of a crank case is arranged in a rotor, a friction pair exists between the lower end face of the crank shaft pipe section and the rotor, the lubrication condition between the crank case and the rotor is relatively insufficient, and the phenomenon of dry grinding is easy to occur.

Therefore, the invention provides the rotor assembly, which aims to reduce friction between the rotor assembly and the crankcase, optimize the lubrication effect between the rotor assembly and the crankcase, effectively reduce friction loss of the compressor, reduce abnormal abrasion risk, ensure stable operation of the compressor and further improve the overall efficiency of the compressor.

Referring to fig. 1 to 6, in an embodiment of the present invention, the rotor assembly 100 includes a rotor core 10, permanent magnets 60, a rotor end plate 40, and a connection member 50, the rotor core 10 is provided with a magnet slot 20, and the permanent magnets 60 are disposed in the magnet slot 20; the rotor core 10 comprises a first core section 11 and a second core section 12, wherein the first core section 11 is provided with a first shaft hole 111 for being connected with a crankshaft section of a crankshaft seat, the second core section 12 is provided with a second shaft hole 121 for being connected with a crankshaft, the aperture of the first shaft hole 111 is larger than that of the second shaft hole 121, the second core section 12 is provided with a contact end face 122 contacted with the end face of the crankshaft section, and the contact end face 122 is provided with an oil storage structure 30; the connection member 50 passes through the rotor end plate 40 and the rotor core 10 to connect the rotor end plate 40, the rotor core 10, and the permanent magnets 60 together.

During assembly, the crankshaft section of the crankshaft seat extends into the first shaft hole 111 of the rotor core 10, the lower end face of the crankshaft section contacts with the edge between the second shaft hole 121, namely the contact end face 122, when the crankshaft drives the rotor core 10 to rotate at high height, the lower end face of the crankshaft section rubs with the contact end face 122 of the second core section 12, in addition, the compressor inevitably vibrates in the running process, the rotor can move up and down, and related technologies in the industry mainly reduce abrasion by adding lubrication, and the cost is high. Through arranging the oil storage structure 30 at the contact end face 122 of the second iron core segment 12, a certain amount of lubricating oil can be stored in the oil storage structure 30, and the lubricating oil in the oil storage structure 30 can splash out in the rotation, so that the rotor, the crankshaft, the rotor and the crankcase can be lubricated, the lubrication condition between the crankcase and the rotor assembly 100 is ensured, the abnormal abrasion caused by rotor jumping is reduced, the abnormal abrasion risk is reduced, the running stability of the compressor is ensured, and the overall efficiency of the compressor is further improved.

The primary function of the rotor core 10 is to provide a magnetic flux path that enables the conversion of electrical energy into mechanical energy. The design and manufacture of the rotor core 10 has a great influence on the efficiency, power and noise level of the motor. There are two ways of manufacturing the rotor core 10: the monolithic core and the punched sheet are laminated to form the core.

The whole iron core is formed by casting or forging and the like. The magnetic circuit has the advantages of stable structure, good mechanical property, small magnetic circuit loss and the like, but the manufacturing cost is higher.

The lamination of the punching sheets to form the iron core is formed by superposing a plurality of thin iron sheets together, blanking the iron sheets into a required shape and then stacking the iron sheets. The magnetic circuit has the advantages of low manufacturing cost, high material utilization rate, small magnetic circuit loss and the like.

In one embodiment, the first core segment 11 and the second core segment 12 are formed of a plurality of monolithic cores, each monolithic core having a corresponding flange and slot for ease of assembly. This design may make the rotor core 10 stronger and more durable, while also being easier to repair and replace. The oil reservoir structure 30 is arranged on a monolithic core.

In another embodiment, the first core segment 11 and the second core segment 12 are formed by stacking a plurality of silicon steel sheets, and the specific selection is comprehensively considered according to the application scene and the requirements.

A rotor end plate 40 and a connecting member 50 to connect the rotor end plate 40, the rotor core 10, and the permanent magnets 60 together to form a unit. When in installation, the permanent magnets 60 are arranged in the magnet slots 20, the rotor end plate 40 prevents the permanent magnets 60 from being separated from the magnet slots 20, and the overall stability of the rotor core 10 is ensured.

The connection member 50 is usually fastened to the rotor core 10 and the end plates by using a plurality of rivets, and ensures that the permanent magnets 60 are positioned in the rotor core 10. In some arrangements the connection may also be secured using bolts and nuts.

In one embodiment, the rotor end plate 40 includes a first end plate 41, the magnet slots 20 of the second core segment 12 are closed at one end, the permanent magnets 60 are disposed in the magnet slots 20, the first end plate 41 is disposed on the first core segment 11, and the first end plate 41 and the second core segment 12 are clamped by the connecting members 50, thereby fixedly forming the entire rotor assembly 100.

Referring to fig. 2 and 4, in another embodiment, the rotor end plate 40 includes a first end plate 41 and a second end plate 42, the first end plate 41 and the second end plate 42 are respectively located at two ends of the rotor core 10 in the axial direction, the first end plate 41 is close to the first core segment 11, and the first end plate 41 and the second end plate 42 clamp and fix the rotor core 10 and the permanent magnets 60 through the connection members 50. The first end plate 41 and the second end plate 42 can fix the permanent magnet 60, thereby improving the reliability of fixing the permanent magnet 60, and ensuring the reliability and safety of assembling the rotor assembly 100, so as to reduce or avoid abnormal sound generated by shaking of the permanent magnet 60 during the operation of the compressor. Meanwhile, the permanent magnet 60 can be prevented from being broken due to shaking of the permanent magnet 60, so that the performance of the permanent magnet 60 is ensured.

Referring to fig. 1 and 5, in particular, the oil storage structure 30 includes a plurality of oil storage holes 31 provided on the contact end surface 122. The plurality of oil storage holes 31 are arranged at intervals, so that the lubrication area is increased, the influence of the oil storage holes 31 intersecting with each other on the oil storage capacity is avoided, the weakening of the strength of the contact surface is avoided, the bearing capacity of the contact surface is reduced, and the deformation is easy to generate.

Further, referring to fig. 2, 4 and 6, the rotor core 10 further includes a third core segment 13, the second core segment 12 is located between the first core segment and the third core segment 13, the first core segment 11, the second core segment 12 and the third core segment 13 are all formed by stacking a plurality of core laminations, the oil storage hole 31 axially penetrates through the second core segment 12, and one side of the third core segment 13, which is close to the second core segment 12, seals the oil storage hole 31.

In this scheme, first iron core section 11, second iron core section 12 and third iron core section 13 are a plurality of iron core punching lamination and form, have low in manufacturing cost, material utilization height, advantage such as magnetic circuit loss are little, oil storage hole 31 runs through along the axial second iron core section 12, third iron core section 13 is close to one side of second iron core section 12 seals oil storage hole 31.

In another aspect, the first core segment 11 and the second core segment 12 are formed by stacking a plurality of core punched sheets, the oil storage hole 31 axially penetrates through the second core segment 12, and the side, close to the second core segment 12, of the second end plate 42 closes the oil storage hole 31.

In one embodiment, the plurality of oil storage holes 31 are arranged in rows and columns, such as rectangular, circular, etc., on the portion of the contact end face 122.

Specifically, the plurality of oil storage holes 31 are arranged in an annular array on the contact end surface 122 with the center of the second shaft hole 121 as the center. The plurality of oil storage holes 31 are arranged in a single circle, a double circle, or the like on the contact end face 122.

Specifically, referring to fig. 5, the spacing angle θ between any adjacent two of the oil storage holes 31 satisfies 15+.θ+.180 °. The too dense oil storage holes 31 may not significantly improve the actual lubrication effect, except for the increase in processing difficulty, and the relatively sparsely distributed oil storage holes 31 may not sufficiently uniform lubrication between the contact end face 122 and the lower end face of the crankcase, and the relatively weak lubrication effect may be achieved, so that the evenly spaced portions of the oil storage structures 30 between the friction pairs may be more convenient to process, and the lubrication effect may be relatively superior.

At 180 ° θ, the oil storage holes 31 are symmetrically arranged on the diameter of the second shaft hole 121, and the symmetrical arrangement ensures uniformity of lubrication and uniform stress of the rotor on the contact end face 122 because the crankshaft rotates in the axial direction.

Referring to fig. 3 and 5, in order to prevent the edge of the second shaft hole 121 from being easily deformed and to reduce the strength of the bearing edge, the distance L between the center of the oil storage hole 31 and the edge of the second shaft hole 121 satisfies 0.5mm L8 mm. Alternatively, the wall thickness s between the oil reservoir hole 31 and the second shaft hole 121 satisfies 1 mm.ltoreq.s.ltoreq.13 mm.

If s is smaller than 0.5mm, the strength between the second axial hole 121 and the oil reservoir hole 31 is insufficient, and the core sheet of the second core segment 12 is easily broken there, and the quality is not ensured.

If s is greater than 8mm, the oil storage amount and effective lubrication area of the oil storage hole 31 are reduced although the strength is secured, and it is understood that the annular width between the first shaft hole 111 and the second shaft hole 121 is the contact end face 122, and the larger s is, the closer the oil storage hole 31 is to the inner wall of the first shaft hole 111.

Specifically, referring to FIGS. 2 and 3, the diameter d of the oil storage hole 31 satisfies 1 mm.ltoreq.d.ltoreq.5 mm, and the depth h of the oil storage hole 31 satisfies 2 mm.ltoreq.h.ltoreq.21 mm.

When the oil storage hole 31 is a non-circular hole, the diameter d refers to the equivalent diameter of the oil storage hole 31, and the equivalent diameter refers to the diameter of the oil storage hole 31 similar in shape and size to a sphere of the same volume.

The oil reservoir hole 31 excessively large or excessively small as described above does not enhance the oil reservoir effect, and the oil reservoir hole 31 acts microscopically, and by defining the diameter d and the depth h of the oil reservoir hole 31, the second core segment 12 is not excessively adversely affected while improving the friction problem between the contact end face 122 and the crankcase. In order to ensure the machining precision, the friction pair, that is, the relative movement of the second shaft hole 121 and the crankcase is prevented from being affected by the residual sharp edges, burrs, etc. after machining, and the oil storage hole 31 is configured as a laser etched hole, an ultrasonic etched hole, an electrochemical etched hole, or an electric spark machined hole.

It will be appreciated that since the rotor core 10 is formed by laminating core laminations, the oil reservoir 31 extends through the second core segment 12 when the core laminations are machined.

In this embodiment, the plurality of oil storage holes 31 are identical in shape and size for convenience of manufacturing. Specifically, the cross-sectional shape of the oil reservoir hole 31 is a regular planar geometry. Such as circular, triangular, rectangular, star-shaped, etc.

In other embodiments, the shape and size of the plurality of oil storage holes 31 may be different.

If multiple groups of different oil storage holes 31 are arranged in different areas of the contact end face 122, the shapes and sizes of the oil storage holes 31 in each area are different.

Specifically, referring to fig. 2, in order to avoid magnetic leakage and to avoid abnormal sounds generated by the shaking of the permanent magnet 60 during the operation of the compressor, the height H1 of the rotor core 10 and the height H2 of the permanent magnet 60 satisfy 0.90.ltoreq.h1/h2.ltoreq.0.99. The situation that the permanent magnets 60 are not tightly riveted after the rotor assembly 100 is assembled can be avoided, and abnormal sounds generated in the operation process of the rotor assembly 100 are avoided.

Further, the height H1 of the rotor core 10 and the thickness B1 of the first end plate 41 satisfy B1 not less than 0.015H1, and the height H of the rotor core 10 and the thickness B2 of the second end plate 42 satisfy B2 not less than 0.015H1. Thereby facilitating assembly of various components within the rotor assembly 100, ensuring reliability and safety of assembly of the rotor assembly 100, so as to reduce or avoid abnormal sounds generated by shaking of the permanent magnets 60 during operation of the compressor.

Further, the total length K of the connecting piece 50 satisfies 1.05.ltoreq.K/(H1+B1+B2). Ltoreq.1.2.

Wherein the total length of the connecting member 50 is the total length of the connecting member 50 before riveting. Thereby facilitating the connection of the first end plate 41, the rotor core 10 and the second end plate 42 by the connection member 50, ensuring the reliability and safety of the rotor component assembly, so as to reduce or avoid abnormal sounds generated by the shaking of the permanent magnets 60 during the operation of the compressor.

In one embodiment, the tail of the connector 50 is provided with a groove. After the rotor assembly 100 is assembled, the tail portions of the connector 50 may be swaged to deform the tail portions, effectively bringing the parts of the rotor assembly 100 together.

Further, in order to avoid the shaking of the permanent magnets 60, in one embodiment, the magnet slots 20 are provided in the rotor core 10, and the rotor core 10 is higher than the permanent magnets 60 in the magnet slots 20. The first end plate 41 and the second end plate 42 are respectively clamped at two ends of the rotor core 10, and the first end plate 41 is provided with a limiting boss for stopping the permanent magnet 60 so as to realize axial limiting of the permanent magnet 60, thereby preventing the permanent magnet 60 from shaking in the magnet groove 20, improving the reliability of fixing the permanent magnet 60, reducing the noise of the rotor assembly 100, reducing the noise of the compressor, preventing the permanent magnet 60 from shaking to cause the permanent magnet 60 to crack, and ensuring the performance of the permanent magnet 60.

According to the technical scheme, a rotor core 10, a permanent magnet 60, a rotor end plate 40 and a connecting piece 50 are adopted, wherein the rotor core 10 is provided with a magnet groove 20, and the permanent magnet 60 is arranged in the magnet groove 20; the rotor core 10 comprises a first core section 11 and a second core section 12, wherein the first core section 11 is provided with a first shaft hole 111 for being connected with a crankshaft section of a crankshaft seat, the second core section 12 is provided with a second shaft hole 121 for being connected with a crankshaft, the aperture of the first shaft hole 111 is larger than that of the second shaft hole 121, the second core section 12 is provided with a contact end face 122 contacted with the end face of the crankshaft section, and the contact end face 122 is provided with an oil storage structure 30; the connection member 50 passes through the rotor end plate 40 and the rotor core 10 to connect the rotor end plate 40, the rotor core 10, and the permanent magnets 60 together. In the related art, a crank shaft pipe section of a crank case is arranged in a rotor, a friction pair exists between the lower end face of the crank shaft pipe section and the rotor, the lubrication condition between the crank case and the rotor is relatively insufficient, and the phenomenon of dry grinding is easy to occur. Through arranging oil storage structure 30 at the contact terminal surface 122 of second iron core section 12, oil storage structure 30 can store a certain amount of lubricating oil, and lubricating oil in the oil storage structure 30 can splash out in the rotation, perhaps because the rotor beats and throws away to can lubricate rotor and bent axle, rotor and crankcase, guarantee the lubrication condition between crankcase and rotor subassembly 100, reduce the friction between rotor subassembly 100 and the crankcase, optimize the lubrication effect between the two, can effectively reduce the friction loss of compressor, alleviate the risk of abnormal wear, guarantee that the compressor operates steadily, and then promote the complete machine efficiency of compressor.

The invention also provides a variable frequency motor, which comprises a rotor assembly 100, wherein the specific structure of the rotor assembly 100 refers to the embodiment, and as the variable frequency motor adopts all the technical schemes of all the embodiments, the variable frequency motor at least has all the beneficial effects brought by the technical schemes of the embodiments, and the description is omitted herein. The variable frequency motor is a motor capable of controlling the rotation speed of the motor by changing the frequency of a power supply. The working principle is that an alternating current power supply is converted into a direct current power supply through a frequency converter, and then the direct current power supply is converted into an alternating current power supply with adjustable frequency through an inverter, so that the rotating speed of a motor is controlled. The variable frequency motor has the advantages of high efficiency, energy saving, precise control, high reliability and the like, and is widely applied to various industrial fields such as fans, water pumps, compressors, conveyors and the like. In addition, the variable frequency motor can also enable the motor to operate under different loads by changing the power frequency, so that higher efficiency and lower energy consumption are realized.

The invention also provides a compressor comprising the variable frequency motor.

The variable frequency motor is adopted in the refrigeration compressor to realize the rotation speed control of the motor, thereby realizing the self-adaptive operation of the refrigeration system. The variable frequency motor consists of a motor body and a frequency converter, wherein the motor body comprises a rotor, a stator, a bearing and the like, the frequency converter is a key component for controlling the rotating speed of the motor, and the variable frequency motor can adjust the output voltage and the frequency according to an external control signal so as to control the rotating speed of the motor. The variable frequency motor has the advantages that the rotating speed can be automatically adjusted according to load change, and the efficiency and the stability of the refrigerating system are improved.

Insufficient lubrication of a refrigeration compressor can affect several aspects: compressor noise increases: insufficient lubrication can lead to increased friction and thus increased compressor noise. The compressor temperature increases: insufficient lubrication can lead to increased frictional heat, thereby increasing compressor temperature and possibly even causing compressor overheating and damage. The compressor efficiency decreases: insufficient lubrication can cause an increase in resistance inside the compressor, thereby reducing the energy efficiency of the compressor and increasing the energy consumption. The life of the compressor is shortened: insufficient lubrication can exacerbate surface wear of components within the compressor, thereby shortening the life of the compressor. Therefore, by adopting the compressor of the rotor assembly 100, the friction between the rotor assembly 100 and the crankcase can be reduced, the lubrication effect between the rotor assembly 100 and the crankcase is optimized, the friction loss of the compressor can be effectively reduced, the abnormal abrasion risk is reduced, the stable operation of the compressor is ensured, and the overall efficiency of the compressor is further improved.

The invention also provides refrigeration equipment comprising the variable frequency motor or the compressor.

The foregoing description is only of the preferred embodiments of the present invention and is not intended to limit the scope of the invention, and all equivalent structural changes made by the description of the present invention and the accompanying drawings or direct/indirect application in other related technical fields are included in the scope of the invention.

Claims (14)

1. A rotor assembly, comprising:

the rotor iron core is provided with a magnet groove, the rotor iron core comprises a first iron core section and a second iron core section, the first iron core section is provided with a first shaft hole used for being connected with a crankshaft section of a crankshaft seat, the second iron core section is provided with a second shaft hole used for being connected with a crankshaft, the aperture of the first shaft hole is larger than that of the second shaft hole, the second iron core section is provided with a contact end face contacted with the end face of the crankshaft section, and the contact end face is provided with an oil storage structure;

the permanent magnet is arranged in the magnet groove; and

a rotor end plate and a connecting member passing through the rotor end plate and the rotor core to connect the rotor end plate, the rotor core, and the permanent magnets together.

2. The rotor assembly of claim 1 wherein the oil reservoir structure comprises a plurality of oil reservoir holes provided in the contact end face.

3. The rotor assembly of claim 2 wherein the rotor core further comprises a third core segment, the second core segment is located between the first core segment and the third core segment, the first core segment, the second core segment, and the third core segment are each a plurality of core laminations stacked, the oil storage hole extends axially through the second core segment, and a side of the third core segment adjacent to the second core segment closes the oil storage hole.

4. The rotor assembly of claim 2 wherein a plurality of oil storage holes are arranged in an annular array on the contact end face centered about the center of the second shaft hole.

5. The rotor assembly of claim 4 wherein the spacing angle θ between any adjacent two oil storage holes satisfies 15 ° or less θ or less 180 °.

6. The rotor assembly of claim 2 wherein the distance L of the center of the oil storage hole from the edge of the second shaft hole is 1mm +.l +.13 mm.

7. The rotor assembly of claim 2 wherein the diameter d of the oil storage hole satisfies 1mm < d < 5mm;

and/or the depth h of the oil storage hole is more than or equal to 2mm and less than or equal to 21mm.

8. The rotor assembly of claim 2 wherein the oil storage holes are the same shape and size;

and/or the cross section of the oil storage hole is one or more of a circle, a triangle, a rectangle and a star;

and/or the oil storage hole is configured as a laser etched hole, or an ultrasonic etched hole, or an electrochemical etched hole or an electric spark machined hole.

9. The rotor assembly of claim 1 wherein the height H1 of the rotor core and the height H2 of the permanent magnets satisfy 0.90 +.h1/h2 +.0.99.

10. The rotor assembly of claim 1 wherein the rotor end plates include first and second end plates located at respective axial ends of the rotor core, the first end plates being adjacent the first core segment, the first and second end plates clamping the rotor core, the permanent magnets, via connectors.

11. The rotor assembly of claim 10 wherein the height H1 of the rotor core and the thickness B1 of the first end plate satisfy B1 ≡ 0.015H1;

and/or the height H of the rotor core and the thickness B2 of the second end plate meet the requirement that B2 is larger than or equal to 0.015H1.

12. The rotor assembly of claim 1 wherein the total length K of the connector satisfies 1.05 +.k/(h1+b1+b2) +.1.2.

13. A variable frequency motor comprising a rotor assembly as claimed in any one of claims 1 to 12.

14. A compressor comprising a variable frequency motor as claimed in claim 13.