Motor rotor assembly and compressor

Abstract

The invention provides a motor rotor assembly and a compressor, the motor rotor assembly comprises a motor rotor and a first balance block, the motor rotor is provided with a first end face close to one side of a compressor pump body assembly, the first balance block is assembled on the first end face, and the first balance block comprises a first balance block main body; the first balance block body is provided with a first windward end and a first leeward end, the first windward end is provided with a first suspended flow guide body extending in the circumferential direction of the motor rotor, and a first suspended overflowing space is formed between the side, close to the first end face, of the first suspended flow guide body and the first end face. The side face, close to one side of the first end face, of the first suspended flow guide body is a first side face, and the axial distance between the first side face of the first suspended flow guide body and the first end face is smaller and smaller in the circumferential direction from the first windward end to the first leeward end. The impact of the refrigerant on the pump body assembly is reduced, and then the energy consumption and the operation noise of the compressor are reduced.

Description

Technical Field

[0001] The present invention belongs to the technical field of compressor design, and particularly relates to an electric motor rotor assembly and a compressor. Background Art

[0002] As Figure 1 shown, the windward end and the leeward end (also called the windward surface and the leeward surface) of the balance weight in the prior art are mostly flat structures. When the compressor operates, the balance weight rotates with the rotor, which will generate a large wind resistance. At the same time, it will disrupt the internal air flow of the compressor, increase the oil discharge rate of the compressor, and generate additional noise. In order to reduce the wind resistance of the rotating balance weight during the operation of the electric motor rotor, in the related art, the windward end and the leeward end of the balance weight are designed as drainage inclined surfaces, as Figure 2 shown. However, this structure of the balance weight will have a strong axial pumping effect on the refrigerant inside the compressor during the high-speed operation of the electric motor rotor assembly. Especially for the main balance weight close to the pump body assembly of the compressor, its downward (towards the pump body assembly) pumping effect causes the refrigerant to impact the muffler arranged on one side of the pump body assembly close to the main balance weight, increasing the gas flow consumption, and even directly hitting the refrigerant discharged from the muffler, resulting in the disorder of the internal flow field of the compressor, and the compressor having high energy consumption and noise. Summary of the Invention

[0003] Therefore, the present invention provides an electric motor rotor assembly and a compressor, which can overcome the technical problem that the balance weight on the electric motor rotor in the related art forms a pumping effect towards the pump body assembly side on the refrigerant inside the compressor during the operation of the compressor, causing the refrigerant to impact the muffler arranged on one side of the pump body assembly close to the main balance weight, increasing the gas flow consumption, and even directly hitting the refrigerant discharged from the muffler, resulting in the disorder of the internal flow field of the compressor, and the compressor having high energy consumption and noise.

[0004] To solve the above problems, the present invention provides an electric motor rotor assembly, including an electric motor rotor and a first balance weight. The first balance weight is assembled on the first end face of the electric motor rotor. The first balance weight includes a first balance weight body, and the first balance weight body has a first windward end and a first leeward end. The first windward end is provided with a first suspended fluid guide extending along the circumferential direction of the electric motor rotor. A first suspended flow-through space is formed between the side of the first suspended fluid guide close to the first end face and the first end face. The side surface of the first suspended fluid guide close to the first end face is a first side surface. Along the circumferential direction from the first windward end to the first leeward end, the axial distance between the first side surface of the first suspended fluid guide and the first end face becomes smaller and smaller.

[0005] In some embodiments, the first leeward end of the first balancing block body also has the first suspended body guide; or, the first leeward end of the first balancing block body has a pressure difference balancing body, the bottom side surface of the pressure difference balancing body is in contact with the first end surface, and along the circumferential direction from the first windward end to the first leeward end, the axial distance between the top side surface of the pressure difference balancing body and the first end surface becomes smaller and smaller.

[0006] In some embodiments, the first suspended body guide and the pressure difference balance body are integrally formed with the first balance block body; and / or the first side surface of the first suspended body guide and / or the second side surface of the pressure difference balance body are inclined surfaces.

[0007] In some embodiments, a cross-section of the first suspended body guide becomes smaller along a circumferential direction away from the first balancing weight body; and / or a second side surface of the first suspended body guide is parallel to the first end surface.

[0008] In some embodiments, the first end face is the end face of the motor rotor close to the compressor pump body assembly, the motor rotor assembly also includes a second balancing block, the motor rotor has a second end face close to the compressor exhaust pipe, the second balancing block is assembled on the second end face, the second balancing block includes a second balancing block body, the second balancing block body has a second windward end and a second leeward end, the second windward end has a second suspended flow guide extending along the circumference of the motor rotor, a second suspended flow space is formed between the side of the second suspended flow guide close to the second end face and the second end face, the side of the second suspended flow guide close to the second end face is a third side face, and along the circumference from the second windward end to the second leeward end, the axial spacing between the third side face of the second suspended flow guide and the second end face becomes smaller and smaller.

[0009] In some embodiments, the axial thickness of the first balancing weight body is greater than the axial thickness of the second balancing weight body, and the maximum axial spacing between the first side surface and the first end surface of the first suspended body guide is greater than the maximum axial spacing between the third side surface and the second end surface of the second suspended body guide.

[0010] In some embodiments, the first end face is the end face of the motor rotor close to the compressor pump body assembly, the motor rotor assembly also includes a second balancing block, the motor rotor has a second end face close to the compressor exhaust pipe, the second balancing block is assembled on the second end face, the second balancing block includes a second balancing block body, the second balancing block body has a second windward end and a second leeward end, the second windward end has an airflow guide body extending along the circumference of the motor rotor, the side of the airflow guide body close to the second end face is in contact with the second end face, the side face of the airflow guide body facing away from the second end face is a drainage top face, and along the circumference from the second windward end to the second leeward end, the axial spacing between the drainage top face of the airflow guide body and the second end face becomes larger and larger.

[0011] In some embodiments, a retaining ring is provided on the end face of the first balancing block away from the motor rotor, and the radial width of the retaining ring is equal to the radial width of the first balancing block; and / or, a retaining ring is provided on the end face of the second balancing block away from the motor rotor, and the radial width of the retaining ring is equal to the radial width of the second balancing block.

[0012] In some embodiments, the first side surface of the first suspended body guide and / or the second suspended body guide respectively includes a radially inner guide surface and a radially outer guide surface, wherein the intersection of the radially inner guide surface and the radially outer guide surface forms a diverter surface; and / or, a positioning surface is formed at one end of the first suspended body guide away from the first balancing block body and / or one end of the second suspended body guide away from the second balancing block body, and the positioning surface is on a radial surface coplanar with the rotation axis of the motor rotor.

[0013] The present invention also provides a compressor, comprising the above-mentioned motor rotor assembly.

[0014] The motor rotor assembly and compressor provided by the present invention have the following beneficial effects:

[0015] A first suspended flow space is formed between the first side surface of the first suspended flow guide on the first windward end of the first balancing block body and the first end surface of the motor rotor close to the compressor pump body assembly. This can reduce the windward area of ​​the balancing block during rotation, thereby significantly reducing the refrigerant airflow resistance. At the same time, the suspended setting can effectively reduce the pumping effect along the axial direction of the motor rotor during the rotation of the balancing block, thereby reducing the impact of the refrigerant on the pump body assembly, reducing the refrigerant flow consumption, reducing the turbulence of the flow field inside the compressor, and thus reducing the energy consumption and operating noise of the compressor;

[0016] By designing the axial thickness of the first balancing block close to the compressor pump body assembly to be greater than the axial thickness of the second balancing block far from the compressor pump body assembly, the axial force borne on the first side surface of the first suspended flow guide body of the first balancing block toward the pump body assembly can be greater than the axial force borne on the first side surface of the second suspended flow guide body of the second balancing block away from the pump body assembly, that is, the axial resultant force formed by the two balancing blocks is directed toward the pump body assembly. During the high-speed rotation of the pump body assembly, the aforementioned axial resultant force can be applied to the motor rotor, thereby enabling the crankshaft thrust surface of the motor rotor to be reliably supported on the lower flange thrust surface of the pump body assembly, without the need to form the axial thrust by axially stacking the motor rotor and the stator as in the prior art, or to reduce the motor The design value of the axial stacking height of the rotor and the stator can improve the motor efficiency (the greater the difference in axial stacking height between the stator and the rotor, the greater the sacrifice in motor efficiency). More importantly, the aforementioned axial resultant force can increase with the increase in the rotation speed of the motor rotor, which can effectively avoid the excessive friction between the crankshaft and the thrust surface of the lower flange and the excessive power consumption caused by the excessive axial resultant force when the pump body assembly (that is, the motor rotor) rotates at a low speed (that is, reducing the additional power consumption when the compressor is running at a low frequency). It can also effectively avoid the axial resultant force being a relatively low fixed value when the pump body assembly rotates at a high speed, causing the crankshaft (that is, the motor rotor) to have irregular axial up and down jumping, thereby eliminating the abnormal noise (that is, thrust noise) caused by the contact between the crankshaft and the lower flange during the high-speed operation of the compressor;

[0017] When the motor rotor rotates, the axial forces borne by the first balancing block and the second balancing block are both directed toward one side of the pump body assembly, that is, the two form an axial resultant force. During the high-speed rotation of the pump body assembly, the aforementioned axial resultant force can be applied to the motor rotor, so that the crankshaft thrust surface of the motor rotor can be reliably supported on the lower flange thrust surface of the pump body assembly. There is no need to form an axial thrust force by axially stacking the motor rotor and the stator as in the prior art, or to reduce the design value of the axial stacking of the motor rotor and the stator, thereby improving the motor efficiency (the greater the difference in the axial stacking height of the stator and the rotor, the greater the sacrifice in motor efficiency). More importantly, the aforementioned axial resultant force can increase with the increase of the rotation speed of the motor rotor, so that it can effectively avoid the excessive friction between the crankshaft and the thrust surface of the lower flange caused by the excessive axial resultant force when the pump body assembly (that is, the motor rotor) rotates at a low speed, resulting in excessive power consumption (that is, reducing the extra power consumption when the compressor is running at a low frequency), and can also effectively avoid the axial resultant force being a relatively low constant value when the pump body assembly rotates at a high speed, resulting in irregular axial up and down jumping of the crankshaft (that is, the motor rotor), thereby eliminating the abnormal noise (that is, thrust noise) caused by the contact between the crankshaft and the lower flange during the high-speed operation of the compressor. It should be noted that since the windward end of the second balance block on the second end face of the motor rotor in this technical solution is not provided with the aforementioned suspended guide body, it objectively lacks the effect of reducing the exhaust oil discharge rate. Based on this, in a preferred embodiment, a retaining ring is provided on the end face of the second balance block away from the motor rotor, and the radial width of the retaining ring is equal to the radial width of the second balance block, which can reduce the axial pumping effect of the balance block guide surface (that is, the inclined surface) on the refrigerant and reduce its adverse effects;

[0018] Due to the existence of the suspended flow space, the positioning surface is objectively a protruding structure set in the air, and a smaller cross-sectional area can be used to achieve circumferential positioning of the motor rotor through the balancing block during the magnetization process or assembly process. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] In order to more clearly illustrate the implementation methods of the present invention or the technical solutions in the prior art, the following briefly introduces the drawings required for the implementation methods or the description of the prior art. The drawings described below are only exemplary, and for ordinary technicians in this field, other implementation drawings can be derived from the provided drawings without creative work.

[0020] Figure 1 It is a three-dimensional structural schematic diagram of a balancing block for a motor rotor in the related art;

[0021] Figure 2It is a schematic diagram of the state in which the balance block with flow guiding and wind resistance reduction in the motor rotor of a compressor in the related art generates a pumping effect on the refrigerant toward the compressor exhaust pipe side during rotation;

[0022] Figure 3 It is a three-dimensional structural schematic diagram of the motor rotor assembly in the first embodiment of the present invention;

[0023] Figure 4 Is Figure 3 A three-dimensional structural schematic diagram from another perspective;

[0024] Figure 5 It is a three-dimensional structural schematic diagram of the motor rotor assembly in the second embodiment of the present invention;

[0025] Figure 6 Is Figure 5 A three-dimensional structural schematic diagram from another perspective;

[0026] Figure 7 It is a three-dimensional structural schematic diagram of the motor rotor assembly in the third embodiment of the present invention;

[0027] Figure 8 Is Figure 7 A three-dimensional structural schematic diagram from another perspective;

[0028] Figure 9 It is a schematic diagram of the state after the motor rotor assembly in the fourth embodiment of the present invention is applied to a compressor. In the figure, F1 and F2 respectively show schematic diagrams of the axial forces formed by the first balance block and the second balance block during rotation;

[0029] Figure 10 It is a three-dimensional structural schematic diagram of the motor rotor assembly in the fifth embodiment of the present invention;

[0030] Figure 11 Is Figure 10 A three-dimensional structural schematic diagram of the first balance block or the second balance block in;

[0031] Reference numerals are:

[0032] 1. Motor rotor; 2. First balance block; 21. First balance block main body; 22. First suspended fluid guide; 221. Radial inner flow guiding surface; 222. Radial outer flow guiding surface; 223. Flow dividing surface; 224. Positioning surface; 23. Pressure difference balance body; 3. Second balance block; 31. Second balance block main body; 32. Second suspended fluid guide; 33. Air flow guiding body; 4. Retaining ring; 5. Compressor pump body assembly; 100. First suspended flow-through space; 200. Second suspended flow-through space. Detailed implementation manners

[0033] Next, the technical solutions in the embodiments of the present invention will be clearly and completely described in conjunction with the accompanying drawings in the embodiments of the present invention. Obviously, the described embodiments are only a part of the embodiments of the present invention, rather than all the embodiments. The following description of at least one exemplary embodiment is actually illustrative only and in no way limits the present invention and its application or use. All other embodiments obtained by those of ordinary skill in the art based on the embodiments of the present invention without creative efforts shall fall within the scope of protection of the present invention.

[0034] In the description of the present invention, it should be understood that the orientation or positional relationship indicated by orientation words such as "front, rear, upper, lower, left, right", "lateral, vertical, perpendicular, horizontal" and "top, bottom", etc. is usually based on the orientation or positional relationship shown in the accompanying drawings. It is only for the convenience of describing the present invention and simplifying the description. Without contrary description, these orientation words do not indicate and imply that the device or element referred to must have a specific orientation or be constructed and operated in a specific orientation. Therefore, it should not be construed as limiting the scope of protection of the present invention; the orientation words "inside, outside" refer to the inside and outside relative to the contour of each component itself.

[0035] For the convenience of description, spatial relative terms such as "above...", "over...", "on the upper surface of...", "above" can be used here to describe the spatial positional relationship between a device or feature shown in the figure and other devices or features. It should be understood that the spatial relative terms are intended to include different orientations in use or operation in addition to the orientation described in the figure for the device. For example, if the device in the figure is inverted, the device described as "above other devices or structures" or "over other devices or structures" will then be positioned "below other devices or structures" or "under other devices or structures". Thus, the exemplary term "above..." can include both the orientations of "above..." and "below...". The device can also be positioned in other different ways (rotated 90° or in other orientations), and corresponding explanations are made for the spatial relative descriptions used here.

[0036] In addition, it should be noted that the use of words such as "first", "second" to limit components is only for the convenience of distinguishing the corresponding components. Without otherwise stating, these words have no special meaning. Therefore, it should not be construed as limiting the scope of protection of the present invention.

[0037] See Figures 3 to 11As shown, according to an embodiment of the present invention, a motor rotor assembly is provided, including a motor rotor 1 and a first balance weight 2. The motor rotor 1 has a first end face (not labeled in the figure) on the side close to the compressor pump body assembly 5. The first balance weight 2 is assembled on the first end face. The first balance weight 2 includes a first balance weight main body 21. The first balance weight main body 21 has a first windward end (not labeled in the figure) and a first leeward end (not labeled in the figure). A first suspended fluid guide 22 extending along the circumferential direction of the motor rotor 1 is provided on the first windward end. A first suspended flow-through space 100 is formed between the side of the first suspended fluid guide 22 close to the first end face and the first end face (specifically refer to Figure 4 as shown). The side of the first suspended fluid guide 22 close to the first end face is the first side face (not labeled in the figure). Along the circumferential direction from the first windward end to the first leeward end, for example, in the counterclockwise direction from the azimuthal perspective of looking up as shown in Figure 6 , the axial distance between the first side face of the first suspended fluid guide 22 and the first end face becomes smaller and smaller, that is, the first side face is generally an inclined slope structure.

[0038] In this technical solution, the first suspended flow-through space 100 formed between the first side face of the first suspended fluid guide 22 on the first windward end of the first balance weight main body 21 and the first end face of the motor rotor 1 close to the compressor pump body assembly 5 can reduce the windward area of the balance weight during rotation, and thus can significantly reduce the resistance of the refrigerant airflow. At the same time, due to the suspended setting, it can effectively reduce the pumping action along the axial direction of the motor rotor during the rotation of the balance weight, thereby reducing the impact of the refrigerant on the pump body assembly, reducing the consumption of refrigerant flow, reducing the disorder degree of the internal flow field of the compressor, and further reducing the energy consumption and operating noise of the compressor.

[0039] Refer to Figure 4 as shown. In the first embodiment of the present invention, the first suspended fluid guide 22 is also provided on the first leeward end of the first balance weight main body 21. In this way, the versatility of the first balance weight 2 can be improved, and the phenomenon that the setting purpose cannot be achieved due to the reverse assembly direction of the balance weight can be effectively avoided;

[0040] Or, refer to Figure 6As shown, in the second embodiment of the present invention, a pressure difference balancing body 23 is provided on the first leeward end of the first balancing block main body 21, and the bottom side surface of the pressure difference balancing body 23 is in contact with the first end surface, and along the circumferential direction from the first windward end to the first leeward end, the axial spacing between the top side surface of the pressure difference balancing body 23 and the first end surface becomes smaller and smaller, and the top side surface of the pressure difference balancing body 23 and the bottom side surface of the pressure difference balancing body 23 are the side surfaces on the opposite sides of the pressure difference balancing body 23, respectively. At this time, it can be understood that the inclination direction of the top side surface of the aforementioned pressure difference balancing body 23 is roughly opposite to the inclination direction of the first suspended flow guide 22, and are respectively located on the opposite sides of the circumferential extension direction of the first balancing block main body 21.

[0041] In this technical solution, by arranging the aforementioned pressure difference balance body 23 on the first leeward end of the first balance block body 21, the generation of turbulent structure at the leeward end is reduced, which can effectively reduce the pressure difference resistance of the refrigerant between the first windward end and the first leeward end, and further help to reduce the turbulence degree of the refrigerant airflow in the compressor.

[0042] In some embodiments, the first suspended body guide 22 and the pressure difference balance body 23 are integrally formed with the first balance block body 21 , and the aforementioned integral forming is specifically achieved by, for example, casting, powder metallurgy, machining, milling after injection molding, etc.

[0043] In this technical solution, the first balancing block body 21 and the first suspended body guide 22 and / or the pressure difference balancing body 23 are formed into an organic whole by integral molding, which can simplify the manufacturing process of the balancing block and the assembly process.

[0044] In a specific embodiment, the first side surface of the first suspended body guide 22 and / or the second side surface of the pressure difference balance body 23 are inclined surfaces. The aforementioned inclined surfaces can be planes or curved surfaces (specifically arc surfaces), preferably planes, so as to simplify the manufacturing process and facilitate the precise control and selection of the balancing quality.

[0045] In some embodiments, the cross-section of the first suspended flow guide 22 in the circumferential direction away from the first balancing block body 21 becomes smaller and smaller, so as to minimize the windward area of ​​the first suspended flow guide 22 and enhance the flow guidance effect on the refrigerant airflow during the rotation of the balancing block.

[0046] The second side surface of the first suspended body guide 22 (ie, the side surface opposite to the first end surface) is parallel to the first end surface, which can simplify the structural design of the first balancing weight 2.

[0047] In some embodiments, the motor rotor assembly further includes a second balancing mass 3, and the motor rotor 1 has a portion close to the compressor exhaust pipe (seeFigure 2 The second end face of the motor rotor 1 is shown in the figure, the second balancing block 3 is assembled on the second end face, the second balancing block 3 includes a second balancing block body 31, the second balancing block body 31 has a second windward end (not marked in the figure) and a second leeward end (not marked in the figure), the second windward end has a second suspended flow guide 32 extending along the circumferential direction of the motor rotor 1, a second suspended flow-through space 200 is formed between the side of the second suspended flow guide 32 close to the second end face and the second end face, the side of the second suspended flow guide 32 close to the second end face is a first side face, and along the circumferential direction from the second windward end to the second leeward end, that is, with Figure 5 In the counterclockwise direction from the top-down perspective, the axial distance between the first side surface and the second end surface of the second suspended body guide 32 becomes smaller and smaller.

[0048] In this technical solution, a second suspended flow space 200 is formed between the second suspended flow guide 32 on the windward end of the second balancing block body 31 and the second end face close to the motor rotor, which can reduce the windward area of ​​the balancing block during rotation, thereby significantly reducing the refrigerant airflow resistance. At the same time, it effectively reduces the pumping effect of the balancing block along the axial direction of the motor rotor toward the exhaust pipe of the compressor during rotation, effectively preventing the disturbance of the internal flow field of the compressor due to the pumping effect, reducing the operating noise of the compressor, and reducing the oil discharge rate and oil discharge amount of the compressor exhaust refrigerant, ensuring sufficient lubrication of the internal components of the compressor by the lubricating oil.

[0049] Specifically Figures 3 to 4 In the first embodiment shown, the axial thickness of the first balancing block body 21 is greater than the axial thickness of the second balancing block body 31, and the maximum axial spacing between the first side surface and the first end surface of the first suspended body guide 22 is greater than the maximum axial spacing between the third side surface and the second end surface of the second suspended body guide 32.

[0050] In this technical solution, the axial thickness of the first balancing block 2 close to the compressor pump body assembly is designed to be greater than the axial thickness of the second balancing block 3 away from the compressor pump body assembly. In this way, the axial force borne on the first side surface of the first suspended flow guide 22 of the first balancing block 2 toward the pump body assembly is greater than the axial force borne on the first side surface of the second suspended flow guide 32 of the second balancing block 3 away from the pump body assembly. That is, the axial resultant force formed by the two balancing blocks is toward the pump body assembly. During the high-speed rotation of the pump body assembly, the aforementioned axial resultant force can be applied to the motor rotor 1, so that the crankshaft thrust surface of the motor rotor 1 can be reliably supported on the lower flange thrust surface of the pump body assembly, without the need to form the axial thrust by axially stacking the motor rotor and the stator as in the prior art. Or reduce the design value of the axial stacking height difference between the motor rotor and the stator, thereby improving the motor efficiency (the greater the axial stacking height difference between the stator and the rotor, the greater the sacrifice in motor efficiency), and more importantly, the aforementioned axial resultant force can increase with the increase in the rotation speed of the motor rotor 1, thereby effectively avoiding the excessive friction between the crankshaft and the thrust surface of the lower flange and the excessive power consumption caused by the excessive axial resultant force when the pump body assembly (that is, the motor rotor 1) rotates at a low speed (that is, reducing the additional power consumption when the compressor runs at a low frequency), and can also effectively avoid the axial resultant force being a relatively low value when the pump body assembly rotates at a high speed, causing the crankshaft (that is, the motor rotor 1) to produce irregular axial up and down jumping, thereby eliminating the abnormal noise (that is, thrust noise) caused by the contact between the crankshaft and the lower flange during the high-speed operation of the compressor. It is worth emphasizing that since the windward ends of the first balance block 2 and the second balance block 3 at both axial ends of the motor rotor 1 in this technical solution are provided with the aforementioned suspended body guide, it can also take into account the weakening of the pumping effect of the refrigerant airflow to the pump body assembly and the exhaust pipe in the axial direction, thereby reducing the refrigerant impact noise and oil discharge rate.

[0051] Specifically referring to the embodiment shown in Figure 9, the motor rotor assembly further includes a second balancing block 3, and the motor rotor 1 has a portion close to the compressor exhaust pipe (see Figure 2The motor rotor 1 has a second end face on one side thereof (shown in the figure), the second balancing block 3 is assembled on the second end face, the second balancing block 3 includes a second balancing block main body 31, the second balancing block main body 31 has a second windward end (not shown in the figure) and a second leeward end (not shown in the figure), the second windward end has an airflow guide body 33 extending along the circumferential direction of the motor rotor 1, the airflow guide body 33 is close to the second end face on one side thereof and is in contact with the second end face, the side face of the airflow guide body 33 facing away from the second end face is a drainage top face, along the circumferential direction from the second windward end to the second leeward end, the axial spacing between the drainage top face of the airflow guide body 33 and the second end face becomes larger and larger, the above-mentioned drainage top face can specifically be an inclined plane or an inclined curved surface (for example, it can be an inclined arc surface), in a specific embodiment, the bottom side face (the side opposite to the drainage top face) of the above-mentioned airflow guide body 33 is a plane.

[0052] In this technical solution, the axial forces borne by the first balancing block 2 and the second balancing block 3 when the motor rotor 1 rotates are both directed toward one side of the pump body assembly, that is, the two form an axial resultant force. During the high-speed rotation of the pump body assembly, the aforementioned axial resultant force can be applied to the motor rotor 1, so that the crankshaft thrust surface of the motor rotor 1 can be reliably supported on the lower flange thrust surface of the pump body assembly. There is no need to form an axial thrust force by axially stacking the motor rotor and the stator as in the prior art, or to reduce the design value of the axial stacking of the motor rotor and the stator, thereby improving the motor efficiency (the greater the difference in the axial stacking height of the stator and the rotor, the greater the sacrifice in motor efficiency). Large), and more importantly, the aforementioned axial resultant force can increase with the increase of the rotation speed of the motor rotor 1, which can effectively avoid the excessive friction between the crankshaft and the thrust surface of the lower flange and the excessive power consumption caused by the excessive axial resultant force when the pump body assembly (that is, the motor rotor 1) rotates at a low speed (that is, reducing the additional power consumption of the compressor when it runs at a low frequency), and can also effectively avoid the axial resultant force being a relatively low constant value when the pump body assembly rotates at a high speed, causing the crankshaft (that is, the motor rotor 1) to produce irregular axial up and down jumps, thereby eliminating the abnormal noise (that is, thrust noise) caused by the contact between the crankshaft and the lower flange during the high-speed operation of the compressor. It should be noted that since the windward end of the second balance block 3 on the second end face of the motor rotor 1 in this technical solution is not provided with the aforementioned suspended guide body, it objectively lacks the effect of reducing the exhaust oil discharge rate. Based on this, in a preferred embodiment, a retaining ring 4 is provided on the end face of the second balance block 3 away from the motor rotor 1, and the radial width of the retaining ring 4 is equal to the radial width of the second balance block 3, which can reduce the axial pumping effect of the balance block guide surface (that is, the inclined surface) on the refrigerant and reduce the adverse effects thereof.

[0053] In some embodiments, a retaining ring 4 is provided on one end face of the first balance weight 2 away from the motor rotor 1. The radial width of the retaining ring 4 is equal to the radial width of the first balance weight 2, which can further reduce the pumping effect during the operation of the balance weight.

[0054] For specific reference Figure 10 and Figure 11 As shown, in some embodiments, the first side surfaces of the first suspended deflector 22 and / or the second suspended deflector 32 respectively include a radially inner deflector surface 221 and a radially outer deflector surface 222. The intersection position of the radially inner deflector surface 221 and the radially outer deflector surface 222 forms a flow splitting surface 223, so that the refrigerant air flow at the windward end can be split into the radially inner and outer sides, reducing the frontal impact between the balance weight and the air flow, thereby further reducing the windward resistance of the balance weight. The intersection positions of the aforementioned radially inner deflector surface 221, radially outer deflector surface 222 and flow splitting surface 223 are rounded (i.e., smoothly connected) to prevent vortex phenomena at the intersection positions and further reduce the wind resistance of the balance weight. It should be noted that, in some embodiments, the aforementioned flow splitting surface 223 can specifically be an intersection line structure (i.e., the radially inner deflector surface 221 and the radially outer deflector surface 222 intersect to form a line).

[0055] For further reference Figure 11 As shown, a positioning surface 224 is formed at one end of the first suspended deflector 22 away from the first balance weight body 21 and / or at one end of the second suspended deflector 32 away from the second balance weight body 31. The positioning surface 224 is on a radial plane coplanar with the rotation axis of the motor rotor 1. It can be understood that, due to the existence of the suspended flow-through space, the aforementioned positioning surface 224 is objectively a protruding structure arranged in the air, and a relatively small cross-sectional area can be used to achieve the circumferential positioning of the motor rotor through the balance weight during the magnetization process or the assembly process.

[0056] Specifically, during the assembly and magnetization process of the motor rotor (assembly), the balance weight is required for positioning and fixing, and the corresponding positioning tooling cannot accurately position on the inclined surface. In the prior art, the axial thickness of the end face of the balance weight that is in contact with the aforementioned first end face of the motor rotor is usually increased to ensure the accurate alignment of the positioning tooling with the balance weight and avoid the displacement of the tooling and the balance weight. This will undoubtedly result in too large an end face cross-sectional area at the windward end and / or the leeward end of the balance weight, and further lead to too large a wind resistance of the refrigerant air flow. However, since the aforementioned positioning surface in the present application is arranged in the air, even if the set cross-sectional area is small (i.e., not too large), the tooling can accurately perform positioning and alignment.

[0057] According to an embodiment of the present invention, a compressor is further provided, including the above-mentioned motor rotor assembly.

[0058] Those skilled in the art can easily understand that, on the premise of no conflict, the advantageous technical features of the above-mentioned various methods can be freely combined and superimposed.

[0059] The above are only the preferred embodiments of the present invention and are not intended to limit the present invention. Any modifications, equivalent replacements, and improvements made within the spirit and principles of the present invention shall be included within the protection scope of the present invention. The above is only the preferred implementation manner of the present invention. It should be noted that for those of ordinary skill in the art, without departing from the technical principle of the present invention, several improvements and variations can still be made, and these improvements and variations should also be regarded as within the protection scope of the present invention.

Claims

1. A motor rotor assembly, characterized in that, It includes a motor rotor (1) and a first balance weight (2). The first balance weight (2) is assembled on the first end face of the motor rotor (1). The first balance weight (2) includes a first balance weight body (21). The first balance weight body (21) has a first windward end and a first leeward end. A first suspended fluid guide (22) extending along the circumferential direction of the motor rotor (1) is provided on the first windward end. A first suspended flow-through space (100) is formed between the side of the first suspended fluid guide (22) close to the first end face and the first end face. The side face of the first suspended fluid guide (22) close to the first end face is the first side face. Along the circumferential direction from the first windward end to the first leeward end, the axial distance between the first side face of the first suspended fluid guide (22) and the first end face becomes smaller and smaller.

2. The motor rotor assembly according to claim 1, characterized in that The first suspended fluid guide (22) is also provided on the first leeward end of the first balance weight body (21); or, a differential pressure balance body (23) is provided on the first leeward end of the first balance weight body (21). The bottom side face of the differential pressure balance body (23) is in contact with the first end face, and along the circumferential direction from the first windward end to the first leeward end, the axial distance between the top side face of the differential pressure balance body (23) and the first end face becomes smaller and smaller.

3. The motor rotor assembly according to claim 2, characterized in that, The first suspended fluid guide (22) and the differential pressure balance body (23) are integrally formed with the first balance weight body (21); and / or, the first side face of the first suspended fluid guide (22) and / or the second side face of the differential pressure balance body (23) is an inclined face.

4. The motor rotor assembly according to claim 1, wherein, The cross-section of the first suspended fluid guide (22) becomes smaller and smaller along the circumferential direction away from the first balance weight body (21); and / or, the second side face of the first suspended fluid guide (22) is parallel to the first end face.

5. The motor rotor assembly according to claim 2, characterized in that, The first end face is the end face of the motor rotor (1) close to the compressor pump body assembly (5). It further includes a second balance weight (3). The motor rotor (1) has a second end face close to the compressor exhaust pipe. The second balance weight (3) is assembled on the second end face. The second balance weight (3) includes a second balance weight body (31). The second balance weight body (31) has a second windward end and a second leeward end. A second suspended fluid guide (32) extending along the circumferential direction of the motor rotor (1) is provided on the second windward end. A second suspended flow-through space (200) is formed between the side of the second suspended fluid guide (32) close to the second end face and the second end face. The side face of the second suspended fluid guide (32) close to the second end face is the third side face. Along the circumferential direction from the second windward end to the second leeward end, the axial distance between the third side face of the second suspended fluid guide (32) and the second end face becomes smaller and smaller.

6. The motor rotor assembly according to claim 5, wherein The axial thickness of the first balancing block body (21) is greater than the axial thickness of the second balancing block body (31), and the maximum axial spacing between the first side surface and the first end surface of the first suspended body guide (22) is greater than the maximum axial spacing between the third side surface and the second end surface of the second suspended body guide (32).

7. The motor rotor assembly according to claim 1, characterized in that, The first end face is an end face of the motor rotor (1) close to the compressor pump body assembly (5), and also includes a second balancing block (3). The motor rotor (1) has a second end face close to the compressor exhaust pipe. The second balancing block (3) is assembled on the second end face. The second balancing block (3) includes a second balancing block body (31). The second balancing block body (31) has a second windward end and a second leeward end. The second windward end has an airflow guide (33) extending along the circumference of the motor rotor (1). The side of the airflow guide (33) close to the second end face is in contact with the second end face. The side of the airflow guide (33) facing away from the second end face is a drainage top face. Along the circumference from the second windward end to the second leeward end, the axial distance between the drainage top face of the airflow guide (33) and the second end face increases.

8. The motor rotor assembly according to any one of claims 5 to 7, characterized in that, A retaining ring (4) is provided on the end face of the first balancing block (2) away from the motor rotor (1), and the radial width of the retaining ring (4) is equal to the radial width of the first balancing block (2); and / or a retaining ring (4) is provided on the end face of the second balancing block (3) away from the motor rotor (1), and the radial width of the retaining ring (4) is equal to the radial width of the second balancing block (3).

9. The motor rotor assembly according to claim 5, characterized in that, The first suspended body guide (22) and / or the second suspended body guide (32) respectively have a first side surface comprising a radial inner flow guide surface (221) and a radial outer flow guide surface (222), wherein the intersection of the radial inner flow guide surface (221) and the radial outer flow guide surface (222) forms a flow splitter surface (223); and / or, a positioning surface (224) is formed at one end of the first suspended body guide (22) away from the first balancing block body (21) and / or an end of the second suspended body guide (32) away from the second balancing block body (31), and the positioning surface (224) is located on a radial surface coplanar with the rotation axis of the motor rotor (1).

10. A compressor, characterized in that, A motor rotor assembly comprising any one of claims 1 to 9.

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