Motor rotor assembly, motor and compressor

Abstract

This utility model provides a motor rotor assembly, a motor, and a compressor, belonging to the field of compressor technology. The motor rotor assembly includes a first rotor body and a second rotor body, with the second rotor body fixed to the middle of the first rotor body. The second rotor body has opposing first and second end faces, and multiple swirling holes are provided on the second rotor body. Each swirling hole includes a first straight segment, a swirling segment, and a second straight segment that are interconnected. The first and second straight segments respectively penetrate the first and second end faces; the axis of the swirling segment is arc-shaped. This rotor can optimize the airflow through the motor rotor assembly via the swirling holes, thereby improving the vortex state within the flow holes of the motor rotor assembly and effectively reducing the aerodynamic vortex noise of the motor rotor assembly in the compressor and the overall noise of the compressor.

Description

Technical Field

[0001] This utility model relates to the field of compressor technology, and in particular to a motor rotor assembly, a motor and a compressor. Background Technology

[0002] As a high-efficiency and compact fluid machinery, the rolling rotor compressor is widely used in household air conditioning, commercial refrigeration equipment, and other fields. Its operating performance and noise level directly affect the user experience and market competitiveness of the entire machine. During the operation of the rolling rotor compressor, the high-pressure gas compressed in the compressor cylinder during exhaust needs to flow upward from the lower chamber of the motor through the flow channel of the motor rotor assembly to the upper chamber of the motor to achieve gas discharge and circulation. However, since the motor rotor is always rotating at high speed, the airflow flowing through its flow hole must not only move upward axially, but also rotate synchronously with the rotor. This makes the airflow motion state in the flow hole extremely complex, easily forming turbulence and alternating eddies.

[0003] Existing motor rotor flow holes are typically designed as vertical straight-through holes with a straight axis. In this design, when airflow rotates with the rotor and flows upwards along the straight-through hole, the direction of airflow movement within the hole is difficult to match with the direction of the centrifugal force generated by the rotor's rotation. This easily leads to mutual impact and disturbance between airflows, resulting in the formation of numerous superimposed vortices within the hole. These vortices generate significant vortex aerodynamic noise, which is broadband noise with a wide frequency range and dispersed energy distribution. This contributes significantly to the overall noise of the compressor, and in severe cases, may even exceed relevant noise standards, affecting the product's market acceptance.

[0004] Therefore, existing rolling rotor compressors need to be improved to overcome the shortcomings of the existing technology. Utility Model Content

[0005] To overcome the problems existing in the related technologies, one of the objectives of this utility model is to provide a motor rotor assembly that can optimize the airflow through the motor rotor assembly by means of swirling holes, thereby improving the vortex state in the flow holes of the motor rotor assembly and effectively reducing the aerodynamic vortex noise of the motor rotor assembly in the compressor and the overall noise of the compressor.

[0006] An electric motor rotor assembly includes a first rotor body and a second rotor body. The second rotor body is fixed to the middle of the first rotor body. The second rotor body has a first end face and a second end face that are opposite to each other. A plurality of swirling holes are provided on the second rotor body. Each swirling hole includes a first straight segment, a swirling segment and a second straight segment that are interconnected. The first straight segment and the second straight segment pass through the first end face and the second end face, respectively. The axis of the swirling segment is arranged in an arc shape.

[0007] Specifically, the second rotor body is fixed to the middle of the first rotor body by an interference fit. The two are coaxially arranged and rotate together with the compressor crankshaft (the rotation direction is counterclockwise, consistent with the rotation direction of the swirling orifice). During assembly, the second rotor body is fixed to the compressor crankshaft through the central mounting hole, and the first rotor body, as the outer structure, rotates in tandem with the second rotor body to ensure that the swirling orifice is always in a stable airflow channel.

[0008] The arc-shaped design of the swirl section aligns with the rotor's rotation direction, allowing the airflow to smoothly rise along the arc-shaped channel as the rotor rotates. This avoids the vortex superposition phenomenon caused by the superposition of rotational and axial motion in traditional straight-through holes. Combined with the rectifying effect of the first and second straight sections, this significantly improves the vortex state within the flow hole, reducing its noise power.

[0009] In a preferred embodiment of this invention, a fixing hole is provided in the middle of the second rotor body, and the fixing hole is used to connect with the crankshaft.

[0010] The second rotor rotates on the crankshaft in a first direction, and the bending direction of the swirl section is set along the first direction.

[0011] The first direction refers to the rotation direction of the compressor. That is, when the rotor is installed in the compressor motor, the bending direction of the swirling section is consistent with the rotation direction of the compressor crankshaft.

[0012] When the compressor is working, the airflow entering the swirl orifice has two motion states at the same time: one is the axial flow from the lower chamber of the motor to the upper chamber, and the other is the circular motion that follows the rotation of the rotor (crankshaft).

[0013] When the curvature of the swirl section is aligned with the direction of crankshaft rotation, the arc-shaped channel of the swirl orifice and the circular motion trajectory of the airflow form a "forward match". The airflow can flow smoothly along the arc-shaped path without having to overcome the reverse resistance of the channel, thus avoiding the violent impact between the airflow and the orifice wall in traditional straight orifices or reverse curved channels.

[0014] This adaptability significantly reduces turbulence and eddy current superposition in the swirl section, making the airflow motion more stable and reducing eddy noise at its source. When the curvature of the swirl section is consistent with the crankshaft rotation direction, the airflow direction in the channel is coordinated with the rotor rotation direction, reducing friction and impact losses on the orifice wall.

[0015] Compared to straight-through or reverse-bent channels, this design reduces the flow resistance of the airflow along the swirling section, avoiding sudden changes in airflow velocity and energy loss caused by excessive resistance.

[0016] In a preferred embodiment of this invention, the area A1 of the cross-section of the first straight line segment is less than or equal to the area A2 of the cross-section of the second straight line segment.

[0017] And A1:A2 = 1:1 - 1:2.4.

[0018] The segmented design of the swirl section (smaller at both ends and larger in the middle) and the enlarged outlet area (1.5 times the inlet area) make the velocity gradient of the airflow within the channel gentler, reducing the impact friction between the airflow and the orifice wall. At the same time, the matching of the swirl direction with the rotor rotation direction further reduces airflow disturbance, effectively reducing flow resistance compared to traditional straight-through orifices, and improving the compressor's exhaust efficiency.

[0019] In a preferred embodiment of this invention, the total area of ​​the swirling holes at any position on the second rotor body along the axial direction of the second rotor body is S1, and the cross-sectional area of ​​the second rotor body is S2; wherein S1 / S2 = 2.5%-17%.

[0020] When the compressor is working, high-pressure gas needs to flow into the upper chamber efficiently from the lower chamber of the motor through the swirling hole. If the flow area is too small, the airflow velocity will be too high, which will cause turbulence to intensify and noise to increase; if the area is too large, it may damage the integrity of the rotor structure, and the airflow velocity in the hole is too low, which can easily form local vortices.

[0021] Limiting the S1 / S2 ratio to 2.5%-17% ensures that the airflow passes through the swirl orifice at a reasonable velocity.

[0022] When the ratio is within this range, the axial velocity of the airflow in the swirl hole is more coordinated with the circumferential velocity, avoiding severe friction between the airflow and the hole wall due to excessively high velocity, or vortex accumulation due to excessively low velocity.

[0023] Combined with the arc-shaped design of the swirl section, this area ratio allows the airflow to flow more smoothly within the swirl hole, reducing turbulence intensity and lowering vortex aerodynamic noise at the source.

[0024] In a preferred embodiment of this invention, the first straight segment forms an airflow inlet on the first end face, and the second straight segment forms an airflow outlet on the second end face.

[0025] The angle α between the central axes of the airflow inlet and the airflow outlet is 25°-55°.

[0026] When the compressor is working, the airflow entering the swirling orifice simultaneously exhibits axial flow (from the lower chamber to the upper chamber) and circular motion (as the rotor rotates), forming an "oblique compound motion trajectory".

[0027] When the included angle α is between 25° and 55°, the overall channel direction of the vortex orifice matches the combined motion trajectory of the airflow more closely.

[0028] If α is too small (e.g., less than 25°), the swirling hole is close to the straight hole, which cannot effectively guide the circular motion component of the airflow, and easily leads to the formation of violent vortex superposition in the airflow within the channel (such as the problem of "significant vortex superposition effect in the straight hole" in the background technology).

[0029] If α is too large (e.g., greater than 55°), excessive channel curvature will force a greater change in airflow direction, which in turn will cause impact friction between the airflow and the orifice wall, generating new turbulent noise. An angle of 25°-55° allows the airflow to transition smoothly along the swirl section, reducing vortex generation and lowering vortex aerodynamic noise at its source. Furthermore, the airflow turning process from inlet to outlet is smoother, avoiding the "straight-through orifice vortex resistance" caused by an excessively small angle or the "excessive bending impact resistance" caused by an excessively large angle. This angle range reduces frictional losses between the airflow and the orifice wall, reducing flow resistance by 15%-25% compared to traditional straight-through orifices, thus improving compressor exhaust efficiency.

[0030] In a preferred embodiment of this invention, the length of the first straight segment is L1, the length of the second straight segment is L2, and the total length of the vortex orifice is L3; wherein L1 = 1 / 7L3 - 1 / 8L3 and L2 = 1 / 7L3 - 1 / 8L3.

[0031] The first straight section (L1 = 1 / 7L3 - 1 / 8L3) is located at the airflow inlet. Its length is designed to effectively rectify the airflow entering the vortex orifice. The airflow in the lower cavity of the motor may be turbulent before entering the vortex orifice (e.g., turbulence caused by exhaust pressure pulsations). A shorter straight section can quickly guide the airflow into the vortex section and avoid the formation of vortices prematurely within the straight section due to excessive length (a drawback of traditional straight-through orifices), ensuring a more stable initial state of the airflow entering the vortex section. The second straight section (L2 = 1 / 7L3 - 1 / 8L3) is located at the airflow outlet. Its length is designed to stabilize the airflow exiting the vortex section.

[0032] After being buffered by the swirl section, the airflow needs to enter the upper cavity of the motor smoothly. A shorter straight section can reduce secondary disturbances in the airflow at the outlet and avoid additional noise caused by outlet turbulence.

[0033] In a preferred embodiment of this invention, the total length of the swirl section is L4; where L4 = 2 / 3L3 - 3 / 4L3.

[0034] As the core structure for improving vortex flow, the swirl section, with a length L4 that accounts for 2 / 3 to 3 / 4 of the total length L3, ensures its dominant guiding role in airflow motion.

[0035] The movement of airflow within the swirl section is crucial for reducing vortex noise. The arc-shaped swirl section needs sufficient length to allow for a smooth transition from a combined axial and circular motion, gradually eliminating vortex superposition. If L4 is too short (less than 2 / 3 of L3), the swirl section cannot adequately guide the airflow, weakening the vortex reduction effect; if L4 is too long (greater than 3 / 4 of L3), the straight section length is compressed, resulting in insufficient rectification and potentially exacerbating inlet / outlet turbulence. This proportional design allows the swirl section to fully utilize the buffering effect of the arc-shaped channel while also forming a complete airflow optimization chain of "inlet rectification → swirl buffering → outlet stabilization" through the auxiliary rectification of the straight section.

[0036] In a preferred embodiment of this invention, the angle between the profile of the swirl section and the vertical plane increases from both ends toward the middle, and the angle at both ends is smaller than the angle at the middle.

[0037] The swirl section, serving as a transitional structure connecting the first straight section (inlet) and the second straight section (outlet), features a profile angle that is "small at both ends and large in the middle," which can accommodate the complex transition of airflow from axial motion to circular motion.

[0038] The lower end of the swirl section (near the inlet) has a smaller included angle, which is closer to the axial direction of the first straight section. This can guide the airflow to smoothly transition from straight motion to an arc shape, avoiding local airflow separation and vortex generation caused by abrupt changes in angle.

[0039] The middle section has the largest included angle, which fully adapts to the circular motion component of the airflow as the rotor rotates, so that the direction of airflow in the channel is highly coordinated with the rotor rotation trajectory.

[0040] The angle at the upper end of the swirl section (near the outlet) decreases, gradually transitioning to the same axial direction as the second straight section, ensuring that the airflow smoothly transitions from arc motion to straight outflow, reducing turbulence at the outlet.

[0041] In the preferred embodiment of this utility model, the first rotor body is formed by lamination and stacking, and the second rotor body is formed by integral molding.

[0042] The first rotor body (laminated laminations), as the outer structure of the motor rotor, mainly undertakes the electromagnetic conversion function (working with the stator to achieve rotational driving force). The lamination lamination process is made by stacking multiple layers of silicon steel sheets, which has the following advantages: the high magnetic permeability and low iron loss characteristics of silicon steel sheets can reduce electromagnetic losses and improve motor efficiency; the lamination structure can effectively suppress eddy current effects (because the insulating coating between silicon steel sheets blocks the eddy current loop), reducing electromagnetic noise and heat generation during motor operation.

[0043] The second rotor body (one-piece molding), as the core carrier of the swirling orifice, must ensure the precision and structural strength of the arc-shaped channel of the swirling section. The advantages of one-piece molding (such as casting, powder metallurgy, etc.) are: it can accurately realize the complex structure of the swirling orifice (such as the continuous molding of the straight section at the inlet end, the arc-shaped transition section in the middle, and the straight section at the outlet end), ensuring the dimensional accuracy of the airflow channel and avoiding airflow disturbance or increased resistance due to splicing errors; the overall structure has no splicing seams, can withstand the centrifugal force and airflow impact during high-speed rotation, and reduce vibration and noise caused by structural loosening.

[0044] The second objective of this utility model is to provide an electric motor, including a stator and the motor rotor assembly as described above.

[0045] The aforementioned motor rotor assembly and stator work together to form a motor. The stator is fixed inside the compressor housing. The rotor assembly rotates under the influence of the stator's magnetic field, and the swirling holes become the airflow channel between the lower and upper chambers of the motor.

[0046] The third objective of this utility model is to provide a compressor, including a motor, wherein the motor is provided with a motor rotor assembly as described above.

[0047] This motor is used in a rolling rotor compressor. The high-pressure gas discharged from the cylinder enters the swirling hole from the lower chamber of the motor. After rectification in the first straight section, buffer transition in the swirling section, and stable outflow in the second straight section, it enters the upper chamber of the motor to complete the exhaust cycle.

[0048] The beneficial effects of this utility model are as follows:

[0049] This utility model provides a motor rotor assembly, which includes a first rotor body and a second rotor body. The second rotor body is fixed to the middle of the first rotor body and has opposing first and second end faces. Multiple swirling holes are provided on the second rotor body. Each swirling hole includes a first straight segment, a swirling segment, and a second straight segment that are interconnected. The first and second straight segments penetrate the first and second end faces, respectively. The axis of the swirling segment is arc-shaped. The arc-shaped axis of the swirling segment of this rotor is consistent with the rotor's rotation direction. When airflow enters the swirling segment from the first straight segment, it rotates synchronously with the rotor along the arc trajectory, reducing the impact of airflow on the hole wall and turbulent disturbance within the airflow, significantly improving vortex superposition. Compared to traditional through-hole rotors, the vortex intensity within the swirling holes is significantly reduced, and the broadband vortex noise power level is also effectively reduced. The parallel design of the first and second straight segments can rectify the airflow, and the smooth transition structure of the swirling segment avoids local resistance loss caused by right-angle turns, improving exhaust efficiency.

[0050] This application also provides a motor and a compressor including the aforementioned rotor, which can reduce eddies during exhaust by means of the aforementioned rotor, thereby reducing the exhaust noise of the compressor and helping to improve the user experience. Attached Figure Description

[0051] Figure 1 This is a perspective view of the motor rotor assembly provided in the embodiments of this application;

[0052] Figure 2 This is a perspective view of the second rotor body provided in the embodiments of this application;

[0053] Figure 3 This is a cross-sectional view of the second rotor body provided in an embodiment of this application;

[0054] Figure 4 This is a schematic diagram showing the angle α between the central axes of the airflow inlet and outlet provided in the embodiments of this application;

[0055] Figure 5 The image shows the noise power level distribution of the rotor assembly in the counterclockwise rotation direction provided in the embodiments of this application.

[0056] Figure 6 This is a diagram showing the clockwise rotation direction of the rotor assembly and its noise power level distribution in an embodiment of this application.

[0057] Figure label:

[0058] 1. First rotor body; 2. Second rotor body; 22. Second end face; 201. Airflow inlet; 202. Airflow outlet; 3. Swirl hole; 31. First straight section; 32. Swirl section; 33. Second straight section. Detailed Implementation

[0059] Preferred embodiments of the present invention will now be described in more detail with reference to the accompanying drawings. While preferred embodiments of the present invention are shown in the drawings, it should be understood that the present invention may be implemented in various forms and should not be limited to the embodiments set forth herein. Rather, these embodiments are provided so that the present invention will be thorough and complete, and will fully convey the scope of the present invention to those skilled in the art.

[0060] The flow holes in existing motor rotor assemblies are typically designed as vertical straight-through holes with a straight axis. In this design, when airflow rotates with the rotor and flows upwards along the straight-through hole, the direction of airflow movement within the hole is difficult to match with the direction of the centrifugal force generated by the rotor rotation. This easily leads to mutual impact and disturbance between airflows, resulting in the formation of numerous superimposed vortices within the hole. These vortices generate significant vortex aerodynamic noise, which is broadband noise with a wide frequency range and dispersed energy distribution. This contributes significantly to the overall noise of the compressor, and in severe cases, may even exceed relevant noise standards, affecting the product's market acceptance.

[0061] Based on this, this application provides a motor rotor assembly.

[0062] Example 1

[0063] like Figures 1-6 As shown, this embodiment provides a motor rotor assembly, including a first rotor body 1 and a second rotor body 2. The second rotor body 2 is fixed in the middle of the first rotor body 1. The second rotor body 2 has a first end face and a second end face 22 facing each other. The second rotor body 2 is provided with a plurality of swirling holes 3. The swirling holes 3 include a first straight segment 31, a swirling segment 32 and a second straight segment 33 that are interconnected. The first straight segment 31 and the second straight segment 33 respectively penetrate the first end face and the second end face 22. The axis of the swirling segment 32 is arranged in an arc shape.

[0064] Specifically, the second rotor 2 is fixed to the middle of the first rotor 1 by an interference fit. The two are coaxially arranged and rotate together with the compressor crankshaft (the rotation direction is counterclockwise, consistent with the rotation direction of the swirling orifice 3). During assembly, the second rotor 2 is fixed to the compressor crankshaft through the central mounting hole. The first rotor 1, as the outer structure, rotates in tandem with the second rotor 2 to ensure that the swirling orifice 3 is always in a stable airflow channel.

[0065] The arc-shaped design of the swirl section 32 is consistent with the rotor's rotation direction, allowing the airflow to smoothly rise along the arc-shaped channel while rotating with the rotor. This avoids the vortex superposition phenomenon caused by the superposition of rotation and axial motion in traditional straight-through holes. Combined with the rectifying effect of the first and second straight sections 33, the vortex state within the flow hole is significantly improved, reducing its noise power.

[0066] Example 2

[0067] This embodiment is an improvement on embodiment 1.

[0068] like Figures 1-6 As shown, in this embodiment, a fixing hole is provided in the middle of the second rotor body 2, and the fixing hole is used to connect with the crankshaft;

[0069] The second rotor body 2 rotates on the crankshaft in a first direction, and the bending direction of the swirl section 32 is set along the first direction.

[0070] The first direction refers to the rotation direction of the compressor. That is, when the rotor is installed in the compressor motor, the bending direction of the swirl section 32 is consistent with the rotation direction of the compressor crankshaft.

[0071] When the compressor is working, the airflow entering the swirling hole 3 has two motion states at the same time: one is the axial flow from the lower chamber of the motor to the upper chamber, and the other is the circular motion that rotates with the rotor (crankshaft).

[0072] When the bending direction of the swirl section 32 is consistent with the rotation direction of the crankshaft, the arc-shaped channel of the swirl hole 3 forms a "forward match" with the circular motion trajectory of the airflow. The airflow can flow smoothly along the arc-shaped path without having to overcome the reverse resistance of the channel, thus avoiding the violent impact between the airflow and the hole wall in traditional straight holes or reverse curved channels.

[0073] This adaptability significantly reduces turbulence and eddy current superposition within the swirl section 32, resulting in a more stable airflow and reducing eddy noise at its source. When the curvature of the swirl section 32 aligns with the crankshaft rotation direction, the airflow direction within the channel coordinates with the rotor rotation direction, reducing friction and impact losses on the borehole walls.

[0074] Compared to straight holes or reverse curved channels, this design reduces the flow resistance of the airflow along the swirl section 32, avoiding sudden changes in airflow velocity and energy loss due to excessive resistance.

[0075] Example 3

[0076] This embodiment is an improvement on embodiment 2.

[0077] like Figures 1-6 As shown, in this embodiment, the area A1 of the cross-section of the first straight line segment 31 is less than or equal to the area A2 of the cross-section of the second straight line segment 33.

[0078] And A1:A2 = 1:1 - 1:2.4. Preferably, A1:A2 = 1:1.5.

[0079] The 32° angled segmented design of the swirl section (smaller at both ends and larger in the middle) and the enlarged outlet area (1.5 times the inlet area) make the airflow velocity gradient within the channel gentler, reducing the impact friction between the airflow and the orifice wall. Simultaneously, the matching of the swirl direction with the rotor's rotation direction further reduces airflow disturbance, effectively lowering flow resistance compared to traditional straight-through orifices and improving the compressor's exhaust efficiency.

[0080] The A1:A2 ratio range of 1:1 to 1:2.4 can be flexibly adjusted according to the compressor's displacement, speed, and other operating conditions. For high-displacement compressors, a ratio close to 1:2.4 can be selected to improve flow efficiency; for small-displacement compressors, a ratio of 1:1 can be selected to balance structural strength. This flexibility makes the design applicable to various models of rolling rotor compressors, giving it significant industrialization value.

[0081] Example 4

[0082] This embodiment is an improvement on embodiment 3.

[0083] like Figures 1-6 As shown, in this embodiment, along the axial direction of the second rotor body 2, the total area of ​​the swirling holes 3 at any position of the second rotor body 2 is S1, and the cross-sectional area of ​​the second rotor body 2 is S2; wherein S1 / S2 = 2.5%-17%. Preferably, S1 / S2 = 10%.

[0084] In this embodiment, the ratio of the cross-sectional area A1 of the first straight segment 31 of a single swirling orifice 3 to the cross-sectional area A2 of the second straight segment 33 is maintained at A1:A2 = 1:1.5. The swirling segment 32 still adopts the angle segmentation design of "small at both ends and large in the middle" (such as 15°, 30°, 15°). The bending direction of the swirling segment 32 is consistent with the rotation direction of the second rotor body 2. The angle α between the central axis of the airflow inlet 201 and the outlet is 40°.

[0085] When the compressor is working, high-pressure gas needs to flow into the upper chamber efficiently from the lower chamber of the motor through the swirling hole 3. If the flow area is too small, the airflow velocity will be too high, which will cause turbulence to intensify and noise to increase; if the area is too large, it may damage the integrity of the rotor structure, and the airflow velocity in the hole is too low, which can easily form local vortices.

[0086] Limiting S1 / S2 to 2.5%-17% ensures that the airflow passes through the swirl orifice 3 at a reasonable speed.

[0087] When the ratio is within this range, the axial velocity of the airflow in the swirl hole 3 is more coordinated with the circumferential velocity, avoiding severe friction between the airflow and the hole wall due to excessively high velocity, or vortex accumulation due to excessively low velocity.

[0088] Combined with the arc-shaped design of the swirl section 32, this area ratio allows the airflow to flow more smoothly within the swirl hole 3, reducing turbulence intensity and lowering vortex aerodynamic noise at the source.

[0089] Example 5

[0090] This embodiment is an improvement on embodiment 1.

[0091] like Figures 1-6As shown, in this embodiment, the first straight segment 31 forms an airflow inlet 201 on the first end face, and the second straight segment 33 forms an airflow outlet 202 on the second end face 22;

[0092] The angle α between the central axes of the airflow inlet 201 and the airflow outlet 202 is 25°-55°. Preferably, α = 40°.

[0093] When the compressor is working, the airflow entering the swirling hole 3 simultaneously exhibits axial flow (from the lower chamber to the upper chamber) and circular motion (as the rotor rotates), forming an "oblique compound motion trajectory".

[0094] When the included angle α is between 25° and 55°, the overall channel direction of the swirl orifice 3 is more compatible with the combined motion trajectory of the airflow:

[0095] If α is too small (e.g., less than 25°), the swirling hole 3 is close to the straight hole, which cannot effectively guide the circular motion component of the airflow, and easily leads to the formation of violent vortex superposition in the airflow in the channel (such as the problem of "significant vortex superposition effect in the straight hole" in the background technology).

[0096] If α is too large (e.g., greater than 55°), excessive channel curvature will force a greater change in airflow direction, which in turn will cause impact friction between the airflow and the orifice wall, generating new turbulent noise. An angle of 25°-55° allows the airflow to smoothly transition along the swirl section 32, reducing vortex generation and lowering vortex aerodynamic noise at its source. Furthermore, the airflow turning process from inlet to outlet is smoother, avoiding the "straight-through orifice vortex resistance" caused by an excessively small angle or the "excessive bending impact resistance" caused by an excessively large angle. This angle range reduces frictional losses between the airflow and the orifice wall, reducing flow resistance by 15%-25% compared to traditional straight-through orifices, thus improving compressor exhaust efficiency.

[0097] Furthermore, in this embodiment, the length of the first straight segment 31 is L1, the length of the second straight segment 33 is L2, and the total length of the vortex orifice 3 is L3; wherein L1 = 1 / 7L3 - 1 / 8L3 and L2 = 1 / 7L3 - 1 / 8L3.

[0098] The first straight section 31 (L1 = 1 / 7L3 - 1 / 8L3) is located at the airflow inlet 201. Its length is designed to effectively rectify the airflow entering the vortex orifice 3: the airflow in the lower cavity of the motor may be turbulent before entering the vortex orifice 3 (such as turbulence caused by exhaust pressure pulsation). The shorter straight section can quickly guide the airflow into the vortex section 32 and avoid the formation of vortices in the straight section prematurely due to excessive length (a drawback of traditional straight-through orifices), ensuring a more stable initial state of the airflow entering the vortex section 32. The second straight section 33 (L2 = 1 / 7L3 - 1 / 8L3) is located at the airflow outlet 202. Its length is designed to stably drain the airflow out of the vortex section 32.

[0099] After passing through the swirl section 32 for buffering, the airflow needs to enter the upper cavity of the motor smoothly. A shorter straight section can reduce secondary disturbances in the airflow at the outlet and avoid additional noise caused by outlet turbulence.

[0100] Furthermore, in this embodiment, the total length of the swirl section 32 is L4; where L4 = 2 / 3L3 - 3 / 4L3.

[0101] The swirl section 32, as the core structure for improving vortex flow, has a length L4 that accounts for 2 / 3 to 3 / 4 of the total length L3, ensuring its dominant guiding role in airflow motion.

[0102] The movement of airflow within the swirl section 32 is crucial for reducing vortex noise. The arc-shaped swirl section 32 needs to be long enough to allow the airflow to smoothly transition from a combined axial and circumferential motion, gradually eliminating vortex superposition. If L4 is too short (less than 2 / 3 of L3), the swirl section 32 cannot adequately guide the airflow, weakening the vortex improvement effect; if L4 is too long (greater than 3 / 4 of L3), the straight section length is compressed, resulting in insufficient rectification and potentially exacerbating inlet / outlet turbulence. This proportional design allows the swirl section 32 to fully utilize the buffering effect of the arc-shaped channel while also forming a complete airflow optimization chain of "inlet rectification → swirl buffering → outlet stabilization" through the auxiliary rectification of the straight section.

[0103] Example 6

[0104] This embodiment is an improvement on embodiment 5.

[0105] like Figures 1-6 As shown, in this embodiment, the angle between the profile of the swirl section 32 and the vertical plane increases from both ends to the middle, and the angle at both ends is smaller than the angle at the middle.

[0106] The angle between the swirl section 32-shaped line and the vertical plane increases from both ends toward the middle (e.g., 15°, 30°, 15°). The second rotor body 2 is connected to the crankshaft through the middle fixing hole. The first rotor body 1 is fixed in the middle of the second rotor body 2 by interference fit. The whole rotates synchronously with the crankshaft.

[0107] The swirl section 32 serves as a transitional structure connecting the first straight section 31 (inlet) and the second straight section 33 (outlet). Its profile angle, which is "small at both ends and large in the middle," is designed to accommodate the complex transition of airflow from axial motion to circular motion.

[0108] The lower end of the swirl section 32 (near the inlet) has a smaller included angle, which is closer to the axial direction of the first straight section 31. This can guide the airflow to smoothly transition from straight motion to an arc shape, avoiding local airflow separation and vortex generation caused by sudden angle changes.

[0109] The middle section has the largest included angle, which fully adapts to the circular motion component of the airflow as the rotor rotates, so that the direction of airflow in the channel is highly coordinated with the rotor rotation trajectory.

[0110] The angle at the upper end of the swirl section 32 (near the outlet) decreases, gradually transitioning to the same axial direction as the second straight section 33, ensuring that the airflow smoothly transitions from arc motion to straight outflow, reducing turbulence at the outlet.

[0111] Example 7

[0112] This embodiment is an improvement on embodiment 1.

[0113] like Figures 1-6 As shown, in this embodiment, the first rotor body 1 is formed by lamination, and the second rotor body 2 is formed by integral molding.

[0114] The first rotor body 1 (laminated lamination), as the outer structure of the motor rotor, mainly undertakes the electromagnetic conversion function (working with the stator to achieve rotational driving force). The lamination lamination process is formed by stacking multiple layers of silicon steel sheets, which has the following advantages: the high magnetic permeability and low iron loss characteristics of silicon steel sheets can reduce electromagnetic losses and improve motor efficiency; the lamination structure can effectively suppress eddy current effects (because the insulating coating between silicon steel sheets blocks the eddy current loop), reducing electromagnetic noise and heat generation during motor operation.

[0115] The second rotor body 2 (one-piece molding) serves as the core carrier of the swirling orifice 3, and must ensure the precision and structural strength of the arc-shaped channel of the swirling section 32. The advantages of one-piece molding (such as casting, powder metallurgy, etc.) are: it can accurately realize the complex structure of the swirling orifice 3 (such as the continuous molding of the straight section at the inlet end, the arc-shaped transition section in the middle, and the straight section at the outlet end), ensuring the dimensional accuracy of the airflow channel and avoiding airflow disturbance or increased resistance due to splicing errors; the overall structure has no splicing seams, can withstand the centrifugal force and airflow impact during high-speed rotation, and reduce vibration and noise caused by structural loosening.

[0116] Example 8

[0117] like Figures 1-6 As shown, this embodiment provides an electric motor, including a stator and a motor rotor assembly as described above.

[0118] Specifically, the stator is an annular cylindrical structure, fixed to the inner wall of the compressor housing, and rigidly connected to the housing through an interference fit or locating pins to ensure the stability of the motor during operation. The stator is made of laminated silicon steel sheets, with the lamination direction aligned with the motor axis (i.e., the axis of the second rotor body 2). An insulating coating is provided between the silicon steel sheets to reduce eddy current losses. Multiple stator slots are evenly distributed along the circumference on the stator core, and three-phase windings (such as copper wire windings) are wound in the slots. When the windings are energized, they generate a rotating magnetic field, providing rotational driving force for the rotor assembly.

[0119] The motor rotor assembly is located on the inner ring of the stator and is coaxially arranged with the stator. The second rotor body 2 is rigidly connected to the compressor crankshaft (such as with an interference fit) through a fixing hole in the middle and rotates synchronously with the crankshaft. The first rotor body 1 is fixed to the middle of the second rotor body 2 with an interference fit, and its outer circumferential surface maintains an air gap with the inner circumferential surface of the stator. Under the action of the rotating magnetic field of the stator, it drives the second rotor body 2 and the crankshaft to rotate as a whole.

[0120] The upper and lower ends of the stator respectively mate with the partition or end cover inside the compressor housing, forming a relatively closed "lower motor cavity" (closer to the compressor cylinder side) and "upper motor cavity" (away from the cylinder side). The swirling hole 3 in the rotor assembly penetrates the first end face (facing the lower motor cavity) and the second end face 22 (facing the upper motor cavity) of the second rotor body 2, becoming the only airflow channel between the lower and upper motor cavities. The high-pressure gas discharged from the compressor cylinder enters the swirling hole 3 from the lower motor cavity, is rectified by the first straight section 31, buffered and transitioned by the swirling section 32, and flows out stably by the second straight section 33 before entering the upper motor cavity and finally being discharged from the compressor through the exhaust pipe.

[0121] When three-phase alternating current is applied to the stator windings, a magnetic field rotating at synchronous speed is generated. The first rotor body 1 (silicon steel sheet laminated structure) generates electromagnetic torque under the action of the magnetic field force, driving the second rotor body 2 and the crankshaft to rotate. At this time, the high-pressure gas discharged from the compressor cylinder enters the lower chamber of the motor and flows upward through the swirling hole 3 of the second rotor body 2 under the action of pressure difference. Since the swirling section 32 of the swirling hole 3 bends in the same direction as the rotor rotation direction, and the structure of each section (first straight section 31, swirling section 32, second straight section 33) is optimized, the vortex state of the airflow in the swirling hole 3 is improved, and it flows smoothly into the upper chamber of the motor, achieving efficient exhaust while significantly reducing the impact of vortex aerodynamic noise on the whole machine.

[0122] Example 9

[0123] like Figures 1-6 As shown, this embodiment provides a compressor, including a motor, wherein the motor is provided with a motor rotor assembly as described above.

[0124] Specifically, the compressor is a rolling rotor compressor, comprising a housing, a cylinder, a rolling piston, a crankshaft, and the aforementioned motor. The motor is fixed inside the housing. One end of the crankshaft is connected to the motor rotor assembly, and the other end passes through the cylinder and drives the rolling piston to rotate. Gas compression is achieved through the cooperation of the rolling piston and the cylinder. After the compressed high-pressure gas is discharged from the cylinder, it passes sequentially through the lower chamber of the motor, the swirling hole 3 of the rotor, and the upper chamber of the motor, and finally exits from the exhaust port of the housing.

[0125] This compressor can reduce exhaust noise by reducing turbulence during exhaust through the aforementioned rotor, thereby improving the user experience.

[0126] Unless otherwise specifically stated, the relative arrangement, numerical expressions, and values ​​of the components and steps described in these embodiments do not limit the scope of this application. It should also be understood that, for ease of description, the dimensions of the various parts shown in the drawings are not drawn to actual scale. Techniques, methods, and devices known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and devices should be considered part of the specification. In all examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not as limitations. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters in the following drawings denote similar items; therefore, once an item is defined in one drawing, it need not be further discussed in subsequent drawings. In the description of this application, it should be understood that the orientation or positional relationship indicated by directional terms such as "front, back, up, down, left, right", "horizontal, vertical, horizontal" and "top, bottom" is usually based on the orientation or positional relationship shown in the accompanying drawings, and is only for the convenience of describing this application and simplifying the description. Unless otherwise stated, these directional terms 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, and therefore should not be construed as a limitation on the scope of protection of this application; the directional terms "inner" and "outer" refer to the inner and outer contours relative to the outline of each component itself.

[0127] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation beyond the orientation of the device as described in the figures. For example, if the device in the figures were inverted, a device described as "above" or "on top of" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.

[0128] Furthermore, it should be noted that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, these terms have no special meaning and therefore should not be construed as limiting the scope of protection of this application. The above description is only a preferred embodiment of this utility model and is not intended to limit this utility model. For those skilled in the art, this utility model can have various modifications and variations. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this utility model should be included within the scope of protection of this utility model.

Claims

1. A motor rotor assembly, comprising a first rotor body and a second rotor body, the second rotor body being fixed to the middle of the first rotor body, the second rotor body having opposing first end faces and second end faces, and the second rotor body being provided with a plurality of swirling holes, characterized in that: The swirling orifice includes a first straight segment, a swirling segment, and a second straight segment that are interconnected. The first straight segment and the second straight segment pass through the first end face and the second end face, respectively. The axis of the swirling segment is arranged in an arc shape.

2. The motor rotor assembly according to claim 1, characterized in that: The second rotor body has a fixing hole in the middle, which is used to connect to the crankshaft; The second rotor rotates on the crankshaft in a first direction, and the bending direction of the swirl section is set along the first direction.

3. The motor rotor assembly according to claim 1, characterized in that: The area A1 of the cross-section of the first straight line segment is less than or equal to the area A2 of the cross-section of the second straight line segment; And A1:A2 = 1:1 - 1:2.

4.

4. The motor rotor assembly according to claim 3, characterized in that: Along the axial direction of the second rotor body, the total area of ​​the swirling holes at any position of the second rotor body is S1, and the cross-sectional area of ​​the second rotor body is S2; where S1 / S2 = 2.5%-17%.

5. The motor rotor assembly according to any one of claims 1-4, characterized in that: The first straight segment forms an airflow inlet on the first end face, and the second straight segment forms an airflow outlet on the second end face; The angle α between the central axes of the airflow inlet and the airflow outlet is 25°-55°.

6. The motor rotor assembly according to any one of claims 1-4, characterized in that: The length of the first straight segment is L1, the length of the second straight segment is L2, and the total length of the vortex orifice is L3; wherein L1 = 1 / 7L3 - 1 / 8L3 and L2 = 1 / 7L3 - 1 / 8L3.

7. The motor rotor assembly according to claim 6, characterized in that: The total length of the swirl section is L4; where L4 = 2 / 3L3 - 3 / 4L3.

8. The motor rotor assembly according to any one of claims 1-4, characterized in that: The angle between the profile of the swirl section and the vertical plane increases from both ends toward the middle, and the angle at both ends is smaller than the angle at the middle.

9. The motor rotor assembly according to any one of claims 1-4, characterized in that: The first rotor body is formed by lamination and stacking, while the second rotor body is formed by integral molding.

10. An electric motor, characterized in that: It includes a stator and an electric motor rotor assembly as described in any one of claims 1-9.

11. A compressor, comprising a motor, characterized in that: The motor is provided with a motor rotor assembly as described in any one of claims 1-9.

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