Compressor assembly and rotor type compressor

Abstract

The invention provides a compressor assembly and a rotor type compressor, and belongs to the technical field of compressors. The crankshaft is arranged in the shell; the motor assembly is arranged in the shell and comprises a plurality of motors, the multiple motors are arranged on the crankshaft at intervals in the axial direction of the crankshaft, stators of the multiple motors are fixedly connected with the shell, and rotors of the multiple motors are fixedly connected with the crankshaft; and the supporting plate is fixed between the two adjacent motors, a shaft hole is formed in the supporting plate, and the crankshaft penetrates through the shaft hole and is in clearance fit with the shaft hole. According to the embodiment, the large-displacement requirement is met, and meanwhile operation stability can still be kept under the high-load working condition.

Description

Technical Field

[0001] This invention relates to the field of compressor technology, and more particularly to a compressor assembly and a rotary compressor. Background Technology

[0002] Rotary rotary compressors are widely used in commercial air conditioning systems due to their high efficiency and low cost, especially in large commercial air conditioning units where demand is increasing. With market demand and technological advancements, the development of large-displacement rotary compressors has become a key focus of the industry. To increase compressor displacement, existing technologies mainly achieve this by increasing the number of cylinders, increasing cylinder height, or increasing inner diameter; however, this design approach leads to a significant increase in the gas pressure and mechanical stress borne by the cylinder block.

[0003] As compressor displacement continues to increase, in order to cope with the high load demands of large-displacement rotary compressors, the motor must have sufficient power output to ensure stable operation of the compressor under high loads. In related technologies, refer to... Figure 1 The compressor's stable operation under high load is ensured by continuously increasing the height of the motor stack. However, excessively high motor stack height can easily lead to heat accumulation under high load, causing excessive temperature rise, reduced motor efficiency, and affecting overall energy efficiency. Furthermore, excessively high motor stack height will significantly aggravate vibration and noise during operation due to increased inertial torque, reducing user experience and increasing the risk of mechanical wear.

[0004] In view of this, the present invention is hereby proposed. Summary of the Invention

[0005] The embodiments of this application are based on the inventor's discovery and understanding of the following problems and facts: The embodiments of this application are based on ensuring the reliable operation of a large-displacement rotary compressor by continuously stacking motors. The embodiments of this application aim to solve at least one of the above-mentioned technical problems to a certain extent.

[0006] According to a first aspect of the embodiments of this application, a compressor assembly is provided, the compressor assembly comprising: case; A crankshaft, which is disposed within the housing; A motor assembly is disposed within the housing. The motor assembly includes multiple motors, which are spaced apart along the axial direction of the crankshaft. The stators of the multiple motors are all fixedly connected to the housing, and the rotors of the multiple motors are all fixedly connected to the crankshaft. A support plate is fixed between two adjacent motors. The support plate has a shaft hole through which the crankshaft passes and is clearance-fitted with the shaft hole.

[0007] In this embodiment, the crankshaft is driven by multiple motor systems and further integrated with the support plate, enabling the compressor to maintain stable operation under high load conditions while meeting the demand for large displacement. This significantly improves the rigidity of the crankshaft support, reduces crankshaft deflection, and extends the service life of the bearings.

[0008] In conjunction with the first aspect, in an optional embodiment of the present application, the support plate includes a magnetic isolation zone, and the projections of the inner circles of the stators of two adjacent motors are both located within the magnetic isolation zone, which can isolate magnetic circuit interference between the two adjacent motors.

[0009] In conjunction with the first aspect, in an optional embodiment of the present application, the support plate includes a first annular region centered on the shaft hole, the magnetic shielding region is located within the first annular region, and the inner diameter of the stators of two adjacent motors is smaller than the outer diameter of the first annular region.

[0010] In conjunction with the first aspect, in an optional embodiment of the present application, at least the first annular region is made of a non-magnetic material; or, at least the first annular region is provided with a magnetic shielding layer.

[0011] In conjunction with the first aspect, in an optional embodiment of the present application, the support plate further includes a second annular region centered on the shaft hole; The first annular region is located within the second annular region, and at least one through hole is formed in the circumferential direction of the second annular region.

[0012] In conjunction with the first aspect, in an optional embodiment of the present application, at least one heat dissipation area is further provided in the circumferential direction of the second annular region, and the heat dissipation area is provided with at least one heat dissipation through hole.

[0013] In conjunction with the first aspect, in an optional embodiment of the present application, the outer edge of the support plate is provided with at least one groove, and the groove cooperates with the inner wall of the housing to form a first oil passage; The stators of two adjacent motors each include a first outer wall and a second outer wall. The first outer wall is in contact with the inner wall of the housing. A gap is provided between the second outer wall and the inner wall of the housing to form a second oil passage. The first oil passage and the second oil passage are connected.

[0014] In conjunction with the first aspect, in an optional embodiment of the present application, there is a phase difference angle between the magnets of the rotors of two adjacent motors, the magnitude of which is related to a set harmonic order, the total number of magnetic poles of the two adjacent motors, and the number of stator slots.

[0015] In conjunction with the first aspect, in an optional embodiment of the present application, the larger the total number of magnetic poles, the larger the phase difference angle; And / or, the larger the number of stator slots, the smaller the phase difference angle; And / or, the larger the set harmonic order, the larger the phase difference angle.

[0016] In conjunction with the first aspect, in an optional embodiment of this application, the plurality of motors are motors of the same type; the phase difference angle satisfies the following formula: Δθ = 90° × P / Z × n; In the formula: Δθ is the phase difference angle, P is the total number of magnetic poles, Z is the number of stator slots, and n is the set harmonic order.

[0017] In conjunction with the first aspect, in an optional embodiment of the present application, the compressor further includes an end cover, a first connecting line, and a second connecting line. The end cover is disposed at one end of the housing and has a first terminal. The two ends of the first connecting line are electrically connected to two adjacent motors, and one end of the second connecting line is electrically connected to the motor closest to the end cover among the plurality of motors, and the other end is electrically connected to the first terminal. Alternatively, the compressor assembly may further include an end cover, a first connecting wire, and a second connecting wire. The end cover is located at one end of the housing and has a first terminal block. The outer wall of the housing has a second terminal block. The plurality of motors includes two motors. One end of the first connecting wire is electrically connected to one of the two motors, and the other end is electrically connected to the first terminal block. One end of the second connecting wire is electrically connected to the other of the two motors, and the other end is electrically connected to the second terminal block.

[0018] According to a second aspect of the embodiments of this application, a rotary compressor is provided, the rotary compressor including a liquid storage tank and a compressor assembly proposed in the first aspect of the embodiments of this application, the compressor assembly further including a pump body assembly, the pump body assembly being disposed inside the housing and connected to the crankshaft, the liquid storage tank being disposed outside the housing, and the outlet of the liquid storage tank communicating with the suction port of the pump body assembly.

[0019] Additional aspects and advantages of the invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

[0020] Figure 1 This is a cross-sectional view of a conventional rotary compressor.

[0021] Figure 2 This is a longitudinal sectional view of a compressor assembly according to an embodiment of this application.

[0022] Figure 3 The compressor assembly according to the embodiments of this application is in Figure 2 Sectional view along the AA direction.

[0023] Figure 4 This is a schematic diagram of the support plate structure according to an embodiment of this application.

[0024] Figure 5 yes Figure 3 Sectional view along the BB direction.

[0025] Figure 6 This is a schematic diagram of the phase difference angle of two adjacent motors according to an embodiment of this application (the rotors of both motors are in a top-down view).

[0026] Figure 7 This is a longitudinal sectional view of a compressor assembly according to another embodiment of this application.

[0027] Figure 8 This is a schematic diagram of a support plate structure according to another embodiment of this application.

[0028] Figure 9 This is a longitudinal cross-sectional view of a rotary compressor according to an embodiment of this application.

[0029] Figure 10 This is a comparison diagram of the vibration amplitude of a rotary compressor according to an embodiment of this application and a rotary compressor of the prior art.

[0030] The attached figures are labeled as follows: 100. Compressor assembly; 200. Liquid receiver; 300. Pump body assembly; 1. Housing; 2. End cap; 31. First terminal; 32. Second terminal; 4. Motor; 41. Stator; 411. Second outer wall; 412. Inner circle of stator; 42. Rotor; 421. Outer circle of rotor; 43. Balance block; 401. First magnet; 402. Second magnet; 403. First magnet slot; 404. Second magnet slot; 5. Crankshaft; 6. Support plate; 61. Shaft hole; 62. Groove; 63. First annular area; 65. Second annular area; 651. Through hole for wires; 652. Heat dissipation area; 6521. Heat dissipation through hole; 7. First oil passage; 8. First connecting wire; 9. Second connecting wire; 10. Second oil passage. Detailed Implementation

[0031] Embodiments of the present invention are described in detail below, examples of which are illustrated in the accompanying 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 with reference to the accompanying drawings are exemplary and intended to explain the present invention, and should not be construed as limiting the present invention.

[0032] Throughout the specification and claims, the following terms will have at least the meaning explicitly associated herein, unless the context otherwise requires. The meanings defined below are not intended to limit the terms, but are merely illustrative examples. In the description of this invention, the phrase "in one embodiment" does not necessarily refer to the same embodiment, although it may refer to the same embodiment. Similarly, the phrase "in some embodiments," as used herein, does not necessarily refer to the same embodiment when used multiple times, although it may refer to the same embodiment. As used herein, the term "or" is an inclusive "or" operator and is equivalent to the term "and / or," unless the context clearly specifies otherwise. The term "based on" is not exclusive and allows for reliance on additional factors not described, unless the context clearly specifies otherwise. The word "exemplary" herein means "serving as an example, instance, or illustration." Any embodiment described herein as "exemplary" is not necessarily to be construed as superior to or better than other embodiments. The scope of this invention is limited only by the scope of the appended claims, and any examples set forth in this specification are not intended to be limiting, but merely illustrate some of the many possible embodiments of the claimed invention. The various embodiments provided in this invention should not be construed as limiting the scope of protection of this invention.

[0033] In the description of this invention, it should be understood that the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," and "counterclockwise," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this invention.

[0034] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this invention, "a plurality of" means two or more, unless otherwise explicitly specified.

[0035] In this invention, unless otherwise explicitly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0036] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can include direct contact between the first and second features, or contact between the first and second features through another feature between them. Furthermore, "above," "over," and "on top" of the second feature includes the first feature directly above or diagonally above the second feature, or simply indicates that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature includes the first feature directly below or diagonally below the second feature, or simply indicates that the first feature is at a lower horizontal level than the second feature.

[0037] Figure 1 This is a cross-sectional view of an existing rotary compressor structure. The compressor motor is located on the upper part of the housing. The motor rotor assembly is fitted onto the long shaft of the crankshaft. The motor stator assembly is connected to the terminals on the upper cover via lead-out components. Three-phase AC power is supplied, and the stator windings generate a rotating magnetic field. The rotor magnets provide a constant magnetic field, and the rotor and rotor magnetic fields work synchronously to generate torque, driving the crankshaft to rotate and compress the refrigerant in the pump's compression chamber. To meet the high load demands of large-displacement rotary compressors, the motor must have sufficient power output, necessitating an increase in motor height. However, excessive motor height can lead to heat accumulation under high loads, causing excessive temperature rise, decreased motor efficiency, and impacting overall energy efficiency. Furthermore, excessively high motor height increases vibration and noise during operation due to increased inertial torque, reducing user experience and increasing the risk of mechanical wear.

[0038] In summary, existing large-displacement rotary compressors face significant challenges in terms of structural strength, bearing reliability, motor performance, and manufacturing cost. To address these issues, there is an urgent need for a structural design for large-displacement rotary compressors that can balance high reliability, low noise, and efficient operation to meet the market's pressing demand for high-performance compressors.

[0039] This embodiment provides a compressor assembly 100, such as Figures 2-8 As shown, the compressor assembly 100 includes a housing 1, a crankshaft 5, a motor assembly, and a support plate 6; wherein: The housing 1 is a sealed container used to house the internal components of the compressor. A cavity is formed inside the housing 1, within which the crankshaft 5, motor assembly, and support plate 6 are housed. In a specific example, the cavity is cylindrical, and the crankshaft 5 is positioned along the height of the cylindrical cavity.

[0040] The motor assembly includes multiple motors 4. These multiple motors 4 can be of the same type or different types. The stack height, winding parameters, or number of magnets of the multiple motors 4 can be the same or different to adapt to the load requirements under different working conditions. No specific limitations are made here.

[0041] Multiple motors 4 are spaced apart on the crankshaft 5 along the axial direction of the crankshaft 5. The stators 41 of the multiple motors 4 are all fixedly connected to the housing 1, and the rotors 42 of the multiple motors 4 are all fixedly connected to the crankshaft 5.

[0042] In a specific example, refer to Figure 2 The compressor assembly 100 includes two motors 4. Each motor 4 includes a rotor 42 and a stator 41 sleeved on the outside of the rotor 42. The stators 41 of both motors 4 are fixed to the inner wall of the housing 1. The rotors 42 of the two motors 4 are sequentially sleeved on the crankshaft 5 along the crankshaft 5, and the inner hole of the rotor 42 is fixed to the crankshaft 5 by an interference fit to ensure the stability of power transmission. Each motor 4 is provided with a balance block 43 to further ensure the stability of power transmission.

[0043] The compressor assembly 100 also includes a pump body assembly 300 for performing the compression process of the refrigerant gas. The pump body assembly 300 is located on the crankshaft 5, see reference 5. Figure 2 As shown, the motor assembly is located at the upper part of the housing 1, the pump body assembly 300 is located at the lower part of the housing 1, the stator 41 of the multiple motors 4 is provided with stator windings, and the rotor 42 of the multiple motors 4 is provided with rotor magnets. The arrangement of the stator windings on the stator 41 and the arrangement of the rotor magnets on the rotor 42 are known to those skilled in the art and will not be described in detail here.

[0044] When the stator winding is energized, a rotating magnetic field is generated. The rotor magnet provides a constant magnetic field, which generates torque under the synchronous action of the rotating magnetic field of the stator 41. This drives the rotor 42 to rotate synchronously. The rotation of the rotor 42 drives the crankshaft 5 to rotate, thereby driving the pump body assembly 300 to compress gas.

[0045] A support plate 6 is fixed between two adjacent motors 4. The support plate 6 has a shaft hole 61, through which the crankshaft 5 passes, and is clearance-fitted with the shaft hole 61 to avoid interference with the rotation of the crankshaft 5. In one example, the shape of the support plate 6 is adapted to the cross-sectional shape of the housing 1, and the outer edge of the support plate 6 is fixed to the inner wall of the housing 1 to improve the assembly reliability between the support plate 6 and the housing 1. In this embodiment, the bearing support structure formed by the support plate 6 effectively reduces the deflection of the crankshaft 5 and enhances the support rigidity.

[0046] The structural design proposed in this embodiment, which involves multiple motors 4 working together to drive the crankshaft 5 and combining it with the support plate 6, not only meets the large displacement requirements of the rotary compressor, but also enables the compressor to maintain stable operation under high load conditions, significantly improving the support rigidity of the crankshaft 5, reducing the crankshaft 5 deflection, and extending the service life of the bearings.

[0047] In a preferred embodiment, the support plate 6 includes a magnetic isolation zone, and the projections of the inner circles 412 of the stators of two adjacent motors 4 are both located within the magnetic isolation zone. The magnetic isolation zone can effectively isolate the magnetic circuit interference between the two adjacent motors 4, optimize the magnetic flux distribution, and improve the efficiency of the motors 4.

[0048] It should be noted that the magnetic isolation zone is not a necessary structure. In practical applications, magnetic interference between two adjacent motors 4 can also be avoided by adjusting the distance between them and the magnetic field strength.

[0049] In one example, the support plate 6 includes a first annular region 63 centered on the shaft hole 61. This first annular region 63 forms a magnetic shielding area, and the inner diameter 412 of the stators of two adjacent motors 4 is smaller than the outer diameter of the first annular region 63. (Combined with...) Figure 3 and Figure 4 The outer circle 421 of the rotor of motor 4 has a diameter of Dz, the inner circle 412 of the stator of motor 4 has a diameter of Dd, the diameter of the shaft hole 61 has a diameter of Dq, the first annular region 63 surrounds the outer circumference of the shaft hole 61, and the inner circle of the first annular region 63 has a diameter of D1. The outer circle of the first annular region 63, the inner circle 412 of the stator of motor 4, the outer circle 421 of the rotor of motor 4 and the shaft hole 61 are concentric, and D1 > Dd, so as to ensure magnetic circuit isolation while meeting the winding arrangement requirements.

[0050] This embodiment offers several methods for setting the magnetic shielding zone: In one example, at least the first annular region 63 is made of a non-magnetic material. Preferably, the support plate 6 is entirely made of a non-magnetic material.

[0051] In one example, at least the first annular region 63 is provided with a magnetic shielding layer, which can be a non-magnetic coating or a non-magnetic material layer. For example, a non-magnetic material coating is applied to the first annular region 63, or a non-magnetic material is adhered to the first annular region 63. Preferably, a non-magnetic material layer is provided on both sides of the support plate 6 opposite to the two adjacent motors 4. Non-magnetic materials include, for example, stainless steel, ceramics, rubber, and plastics.

[0052] It should be noted that the first annular region 63 can be located on both opposite sides of the support plate 6, that is, the support plate 6 has a first annular region 63 on the side opposite to the two adjacent motors 4, and the first annular regions 63 on both opposite sides of the support plate 6 form magnetic isolation regions. Alternatively, the first annular region 63 can be located only on one side of the support plate 6, that is, the support plate 6 has a first annular region 63 on the side opposite to one of the two adjacent motors 4, and this first annular region 63 forms a magnetic isolation region. Setting a magnetic isolation region on one side of the support plate 6 can also achieve the effect of isolating the magnetic circuits of the two adjacent motors 4.

[0053] In one alternative implementation, refer to Figure 4 , Figure 5 and Figure 8 The support plate 6 also includes a second annular region 65 centered on the shaft hole 61. The first annular region 63 is located within the second annular region 65, meaning that the second annular region 65 and the first annular region 63 are concentric. At least one through hole 651 is opened in the circumferential direction of the second annular region 65. The through hole 651 is used for the wiring between two adjacent motors 4, ensuring the neatness of the internal wiring of the compressor and improving circuit safety.

[0054] In a preferred embodiment, refer to Figure 4 There are multiple through holes 651, which are spaced apart along the circumferential direction of the second annular area 65 to improve the convenience of wiring.

[0055] In one alternative implementation, refer to Figure 8 The second annular region 65 also has at least one heat dissipation area 652 in the circumferential direction. The heat dissipation area 652 has at least one heat dissipation through-hole 6521 to improve the heat dissipation effect of the stator winding, reduce deformation caused by thermal expansion, enhance the structural stability of the support plate 6 under high load, and improve the operating efficiency and lifespan of the motor 4. Furthermore, the heat dissipation through-hole 6521 can also serve as part of the lubrication channel, further optimizing the distribution and flow path of the lubricating oil and improving the overall operational reliability of the compressor. Preferably, the second annular region 65 has multiple heat dissipation areas 652, which are spaced apart along the circumferential direction of the second annular region 65.

[0056] In a preferred embodiment, continue to refer to Figure 8Multiple heat dissipation holes 6521 form a porous honeycomb structure in the heat dissipation area 652, which further improves heat dissipation performance while ensuring the structural rigidity of the support plate 6, and has the advantages of high bending stiffness and lightweight.

[0057] In one alternative implementation, refer to Figure 3 , Figure 4 and Figure 8 The outer edge of the support plate 6 is provided with at least one groove 62, which mates with the inner wall of the housing 1 to form a first oil passage 7. The stators 41 of the two adjacent motors 4 each include a first outer wall and a second outer wall 411. The first outer wall is in contact with the inner wall of the housing 1, and a gap is formed between the second outer wall 411 and the inner wall of the housing 1 to form a second oil passage 10. The first oil passage 7 communicates with the second oil passage 10. Preferably, multiple grooves 62 are provided on the outer edge of the support plate 6, and these grooves 62 are spaced apart along the circumferential direction of the support plate 6 to form multiple first oil passages 7 between the support plate and the inner wall of the housing 1, thereby improving the uniformity of lubricant distribution within the two adjacent motors 4.

[0058] The first oil passage 7 and the second oil passage 10 are connected in such a way that the projections of the first oil passage 7 and the second oil passage 10 on the support plate 6 at least partially overlap. This allows the first oil passage 7 of two adjacent motors 4 to be connected through the second oil passage 10, thereby enabling the flow of lubricating oil between the two adjacent motors 4. Alternatively, the first oil passage 7 and the second oil passage 10 can be connected through an intermediate pipe, which also allows the flow of lubricating oil between the two adjacent motors 4.

[0059] In a preferred embodiment, the first outer wall and the second outer wall 411 are arranged along the circumferential direction of the stator 41, and both the first outer wall and the second outer wall 411 extend along the height direction of the stator 41. An oil passage is formed between the second outer wall 411 and the housing 1, extending along the height direction of the stator 41. The second outer wall 411 is a concave wall, or the second outer wall 411 is a wall surface formed after cutting the outer edge of the stator 41. The first outer wall is adapted to the inner wall surface of the housing 1, and the first outer wall is in close contact with the inner wall surface of the housing 1. More preferably, the stator 41 and the inner wall surface of the housing 1 are interference-fitted, the first outer wall is in close contact with the inner wall surface of the housing 1, and a gap is provided between the second outer wall 411 and the housing 1 to form a second oil passage 10.

[0060] In one optional embodiment, there is a phase difference angle between the magnets of the rotors 42 of two adjacent motors 4. The magnitude of the phase difference angle is related to a set harmonic order, the total number of magnetic poles of the two adjacent motors 4, and the number of stator slots. Setting the phase difference angle can achieve the effect of eliminating or improving noise and vibration caused by harmonic components of a set order as needed in actual applications.

[0061] In a specific example, refer to Figure 6 In the top view, of the rotors 42 of two adjacent motors 4, the rotor 42 of the upper motor 4 has multiple first magnet slots 403 arranged along the circumferential direction of the rotor 42, and the rotor 42 of the lower motor 4 has multiple second magnet slots 404 arranged along the circumferential direction of the rotor 42. First magnets 401 are housed in the first magnet slots 403, and second magnets 402 are housed in the second magnet slots 404. When there is no phase difference angle between the magnets of the rotors of the two adjacent motors, the positions of the first magnets 401 and the second magnets 402 coincide. When there is a phase difference angle between the magnets of the rotors of the two adjacent motors, the positions of the first magnets 401 and the second magnets 402 are offset by an angle, which is the phase difference angle.

[0062] In one method of determining the phase difference angle, the angle between the first line passing through the first magnet 401 and perpendicular to the crankshaft 5 axis and the second line passing through the second magnet 402 and perpendicular to the crankshaft 5 axis is the phase difference angle.

[0063] Another method for determining the phase difference angle is to determine it based on the angle between the reference lines of the first magnet 401 and the second magnet 402, respectively. In a specific example, continue to refer to... Figure 6 Each first magnet slot 403 includes two first sub-magnet slots, and one end of the two first sub-magnet slots intersects at point a1 to form a first preset angle. Each first sub-magnet slot contains a first magnet 401. Each second magnet slot 404 includes two second sub-magnet slots, and one end of the two second sub-magnet slots intersects at point a2 to form a second preset angle. Each second sub-magnet slot contains a second magnet 402. The first magnet 401 is positioned in the same location as the second magnet 402 in the same location. The first preset angle and the second preset angle are the same. The phase difference angle is the angle between the first reference line passing through point a1 and the second reference line passing through point a2. (Refer to...) Figure 6 The first reference line is the reference line of the first magnet 401, and the second reference line is the reference line of the second magnet 402. Both the first reference line and the second reference line pass through the central axis of the crankshaft 5.

[0064] Of course, the above is just a specific example to illustrate the reference lines of the first magnet 401 and the second magnet 402. The reference lines of the first magnet 401 and the second magnet 402 are not limited to the positions specified above. In practical applications, the positions of the first reference line and the second reference line can be flexibly adjusted, as long as they can indicate the deflection angle between the first magnet 401 and the second magnet 402.

[0065] When motor 4 is running, the electromagnetic force between stator 41 and rotor 42 generates tangential force (i.e., torque pulsation), mainly caused by uneven magnetic field distribution, harmonic components, or changes in magnetic reluctance of the magnets. These forces are transmitted through the mechanical structure, leading to vibration and noise. In this embodiment, by creating a phase difference angle between the rotor magnets of two adjacent motors 4, the electromagnetic force generated between the rotors 42 of the two motors 4 forms a phase difference in space, which optimizes the magnetic circuit distribution, reduces harmonic excitation, and improves the vibration characteristics of the compressor.

[0066] Furthermore, the magnitude of the phase difference angle is related to the set harmonic order, the total number of magnetic poles of the two adjacent motors 4, and the number of stator slots. This allows for setting a reasonable phase difference angle according to different application requirements, enabling the electromagnetic forces of certain harmonic components to cancel each other out, thereby reducing the total excitation force and motor 4 vibration. During high-speed operation, high-frequency harmonic excitation is more significant, and phase angle cancellation technology can effectively reduce high-frequency vibration.

[0067] Reference Figure 10 The test results show that when the stack height of the compressor rotor 42 is ≥100mm, compared with the comparative prototype (i.e., the prior art) that does not use the magnet phase difference design, this embodiment can effectively suppress the fifth electromagnetic force harmonic component generated by the fifth harmonic current of the stator winding of the motor 4 by setting the phase angle difference of the magnets of the rotor 42 of the two adjacent motors 4 to Δθ=12°, so that the average peak value of the compressor body vibration acceleration is reduced by 30%, and the high frequency harmonic excitation reaches 30% to 40% when running at high speed.

[0068] In a preferred embodiment, the larger the total number of magnetic poles, the larger the phase difference angle; and / or, the larger the number of stator slots, the smaller the phase difference angle; and / or, the larger the set harmonic order, the larger the phase difference angle.

[0069] In one example, when two adjacent motors 4 are of the same type, the phase difference angle satisfies the following formula: Δθ=90°× P / Z× n; where: Δθ is the phase difference angle, P is the total number of magnetic poles, Z is the number of stator slots, and n is the set harmonic order.

[0070] In another example, when the two adjacent motors 4 are of different types, P is the average of the total number of magnetic poles of the two adjacent motors 4, Z is the average of the number of stator slots of the two adjacent motors 4, and n is the set harmonic order. By differentiating the parameters of the two adjacent motors 4 (such as stack height, winding parameters, magnet configuration, etc.), the motor assembly can flexibly adapt to different loads and operating conditions, thereby improving the overall operating efficiency and reliability of the compressor.

[0071] In one alternative implementation, refer to Figure 2 The compressor also includes an end cover 2, a first connecting line 8, and a second connecting line 9. The end cover 2 is located at one end of the housing 1 and has a first terminal 31. The two ends of the first connecting line 8 are electrically connected to two adjacent motors 4, respectively. One end of the second connecting line 9 is electrically connected to the motor 4 closest to the end cover 2 among the multiple motors 4, and the other end is electrically connected to the first terminal 31 to achieve electrical connection with an external circuit. At this time, the two adjacent motors 4 are connected in series to achieve synchronous control of the two adjacent motors 4.

[0072] Or, refer to Figure 7 The compressor assembly 100 also includes an end cover 2, a first connecting wire 8, and a second connecting wire 9. The end cover 2 is located at one end of the housing 1 and has a first terminal 31. The outer wall of the housing 1 also has a second terminal 32. The plurality of motors 4 includes two motors 4. One end of the first connecting wire 8 is electrically connected to one of the two motors 4, and the other end is electrically connected to the first terminal 31 to achieve electrical connection with an external circuit. One end of the second connecting wire 9 is electrically connected to the other of the two motors 4, and the other end is electrically connected to the second terminal 32 to achieve electrical connection with an external circuit. In this configuration, the two motors 4 are connected in parallel to allow for independent control of each motor 4, facilitating different application requirements.

[0073] It should be noted that the electrical connection defined in this embodiment does not mean that this connection method is always in a powered state, but rather that this connection method enables the two connected parts to have the ability to connect in a powered state.

[0074] This embodiment also proposes a rotary compressor, referring to... Figure 9 The rotary compressor includes a liquid storage tank 200 and the compressor assembly 100 mentioned above. The compressor assembly 100 also includes a pump body assembly 300, which is disposed inside the housing 1 and connected to the crankshaft 5. The liquid storage tank 200 is disposed outside the housing 1, and its outlet is connected to the suction port of the pump body assembly 300. The structure of the pump body assembly 300, the connection relationship between the main body assembly and the crankshaft 5, and the specific connection relationship between the pump body assembly 300 and the liquid storage tank 200 in this embodiment are known to those skilled in the art and will not be described in detail here.

[0075] The compressor in this embodiment can achieve a large displacement while maintaining stable operation under high load conditions, significantly improving crankshaft support rigidity, reducing crankshaft deflection, and extending bearing service life.

[0076] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. In addition, those skilled in the art can combine and integrate the different embodiments or examples described in this specification.

[0077] Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention. Those skilled in the art can make changes, modifications, substitutions and variations to the above embodiments within the scope of the present invention.

Claims

1. A compressor assembly, characterized in that, The compressor assembly (100) includes: Shell (1); A crankshaft (5) is disposed within the housing (1); The motor assembly is located inside the housing (1). The motor assembly includes multiple motors (4). The multiple motors (4) are spaced apart on the crankshaft (5) along the axial direction of the crankshaft (5). The stators (41) of the multiple motors (4) are all fixedly connected to the housing (1), and the rotors (42) of the multiple motors (4) are all fixedly connected to the crankshaft (5). A support plate (6) is fixed between two adjacent motors (4). The support plate (6) has a shaft hole (61). The crankshaft (5) passes through the shaft hole (61) and is clearance-fitted with the shaft hole (61).

2. The compressor assembly according to claim 1, characterized in that, The support plate (6) includes a magnetic isolation zone. The projections of the inner circles (412) of the stators of two adjacent motors (4) are both located within the magnetic isolation zone. The magnetic isolation zone can isolate magnetic circuit interference between two adjacent motors (4).

3. The compressor assembly according to claim 2, characterized in that, The support plate (6) includes a first annular region (63) centered on the shaft hole (61). The first annular region (63) forms the magnetic isolation region. The inner circle (412) diameter of the stator of the two adjacent motors (4) is smaller than the outer circle diameter of the first annular region (63).

4. The compressor assembly according to claim 3, characterized in that, At least the first annular region (63) is made of a non-magnetic material; or, at least the first annular region (63) is provided with a magnetic shielding layer.

5. The compressor assembly according to claim 3, characterized in that, The support plate (6) also includes a second annular region (65) centered on the shaft hole (61). The first annular region (63) is located within the second annular region (65), and at least one through hole (651) is opened in the circumferential direction of the second annular region (65).

6. The compressor assembly according to claim 5, characterized in that, The second annular region (65) is further provided with at least one heat dissipation area (652) in the circumferential direction, and the heat dissipation area (652) is provided with at least one heat dissipation through hole (6521).

7. The compressor assembly according to claim 1, characterized in that, The outer edge of the support plate (6) is provided with at least one groove (62), and the groove (62) cooperates with the inner wall of the housing (1) to form a first oil passage (7). The stators (41) of the two adjacent motors (4) each include a first outer wall and a second outer wall (411). The first outer wall is in contact with the inner wall of the housing (1). The second outer wall (411) is separated from the inner wall of the housing (1) to form a second oil passage (10). The first oil passage (7) is connected to the second oil passage (10).

8. The compressor assembly according to claim 1, characterized in that, There is a phase difference angle between the magnets of the rotors (42) of two adjacent motors (4), and the magnitude of the phase difference angle is related to the set harmonic order, the total number of magnetic poles of the two adjacent motors (4), and the number of stator slots.

9. The compressor assembly according to claim 8, characterized in that, The greater the total number of magnetic poles, the greater the phase difference angle; And / or, the larger the number of stator slots, the smaller the phase difference angle; And / or, the larger the set harmonic order, the larger the phase difference angle.

10. The compressor assembly according to claim 9, characterized in that, The plurality of motors (4) are of the same type; the phase difference angle satisfies the following formula: Δθ = 90° × P / Z × n; In the formula: Δθ is the phase difference angle, P is the total number of magnetic poles, Z is the number of stator slots, and n is the set harmonic order.

11. The compressor assembly according to any one of claims 1-10, characterized in that, The compressor also includes an end cover (2), a first connecting line (8), and a second connecting line (9). The end cover (2) is located at one end of the housing (1), and the end cover (2) is provided with a first terminal (31). The two ends of the first connecting line (8) are electrically connected to two adjacent motors (4), and one end of the second connecting line (9) is electrically connected to the motor (4) closest to the end cover (2) among the plurality of motors (4), and the other end is electrically connected to the first terminal (31). Alternatively, the compressor assembly (100) may further include an end cap (2), a first connecting line (8), and a second connecting line (9). The end cap (2) is located at one end of the housing (1), and the end cap (2) is provided with a first terminal (31). The outer wall of the housing (1) is provided with a second terminal (32). The plurality of motors (4) includes two motors (4). One end of the first connecting line (8) is electrically connected to one of the two motors (4), and the other end is electrically connected to the first terminal (31). One end of the second connecting line (9) is electrically connected to the other of the two motors (4), and the other end is electrically connected to the second terminal (32).

12. A rotary compressor, characterized in that, The rotary compressor includes a liquid storage tank (200) and a compressor assembly (100) according to any one of claims 1-11. The compressor assembly (100) further includes a pump body assembly (300). The pump body assembly (300) is disposed inside the housing (1) and connected to the crankshaft (5). The liquid storage tank (200) is disposed outside the housing (1). The outlet of the liquid storage tank (200) is connected to the suction port of the pump body assembly (300).

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