Rotor assembly for compressor and compressor

Abstract

The utility model relates to the technical field of compressors, and discloses a rotor assembly for a compressor. The rotor assembly for the compressor comprises a rotor iron core, a groove is formed in one side of the end face in the axial direction, and the groove is eccentrically arranged relative to the axis of the rotor iron core, so that a built-in counterweight balance part is formed in a solid body on the other side of the end face. The rotor assembly is not provided with an end ring part, the groove is directly formed in the end face of the rotor iron core instead of being formed in an end ring, the mass and space occupied by the end ring can be reduced, high rotating speed and miniaturization of the compressor can be achieved, and the service life of the compressor can be prolonged while a refrigerant and oil drops are prevented from colliding with a balance block. The high-rotating-speed operation effect of the compressor can be improved. And meanwhile, the oil spitting rate can be reduced, and the energy efficiency of the compressor is improved. The utility model further discloses the compressor.

Description

Technical Field

[0001] The present application relates to the technical field of compressors, and in particular to a rotor assembly for a compressor and a compressor. Background Art

[0002] At present, with the upgrade of compressors, miniaturization and high speed have become the development direction of compressors. Increasing the maximum operating frequency of the compressor can achieve a smaller displacement and a higher cooling capacity. The double-cylinder rotor is equipped with an upper balance block between the upper baffle and the oil cap plane. When the compressor speed is increased, the refrigerant and oil droplets on the upper part of the motor are stirred by the balance block and collide at high speed, which will lead to the problem of increased oil discharge rate.

[0003] The related technology opens a groove on the rotor end ring of the compressor, balances the weight through the uneven weight of the groove on one side of the rotor end and the solid part on the other side, and adds a groove cover to reduce the drag coefficient, reduce wind loss in the compressor, mechanical loss during collision with oil droplets, improve the energy efficiency of the compressor, and reduce the oil discharge of the compressor.

[0004] In the process of implementing the embodiments of the present disclosure, it is found that there are at least the following problems in the related art:

[0005] In the related art, a groove portion is opened on one side of the end ring of the rotor to make the weight of that end of the rotor unbalanced, and the balancing effect of the balance block is achieved by the weight of the solid portion on the other side of the end ring. However, the additional setting of the end ring will still increase the mass of the rotor assembly, which will affect the high-speed operation of the compressor to a certain extent.

[0006] It should be noted that the information disclosed in the above background technology section is only used to enhance the understanding of the background of the present application, and therefore may include information that does not constitute the prior art known to ordinary technicians in the field. Utility Model Content

[0007] In order to provide a basic understanding of some aspects of the disclosed embodiments, a brief summary is given below. The summary is not an extensive review, nor is it intended to identify key / critical components or delineate the scope of protection of these embodiments, but rather serves as a prelude to the detailed description that follows.

[0008] The disclosed embodiments provide a rotor assembly for a compressor and a compressor, so as to improve the high-speed operation effect of the compressor while preventing the collision between the refrigerant and the oil droplets and the balancing block.

[0009] According to the first aspect of an embodiment of the utility model, a rotor assembly for a compressor is provided, comprising: a rotor core, a groove being provided on one side of an axial end face, the groove being eccentrically arranged relative to the axis of the rotor core so that a solid body on the other side of the end face forms a built-in counterweight balancing portion.

[0010] Optionally, the axial end face of the rotor core includes a first end face and a second end face arranged opposite to the first end face along the axial direction of the rotor core; wherein a first groove is provided on the first end face, and / or a second groove is provided on the second end face; when the first groove is provided on the first end face and the second groove is provided on the second end face, the second groove and the first groove are located on opposite sides of the plane passing through the axis of the rotor core.

[0011] Optionally, the first groove is symmetrically arranged along the first radius; the second groove is symmetrically arranged along the second radius; wherein the first radius is the radius of the first end face, and the second radius is the radius of the second end face; when the first radius is projected axially to the second end face, it forms a diameter with the second radius.

[0012] Optionally, the first end face is away from the main bearing of the compressor, the second end face is close to the main bearing of the compressor, the rotor core is axially provided with a central axis hole, and the second end face is also provided with a clearance groove opened around the central axis hole for making way for the main bearing; wherein the second groove is arranged on the outside of the clearance groove along the radial direction of the second end face.

[0013] Optionally, the rotor assembly for the compressor further includes: an oil deflector cap, which is covered on the first end surface of the rotor core and has a gap with the first end surface, and the gap is radially symmetrical along the oil deflector cap.

[0014] Optionally, the rotor assembly for the compressor also includes: a plurality of magnet sheets extending along the axial direction of the rotor core and arranged in sequence along the circumferential direction of the rotor core; a first baffle plate, covering the first end surface and abutting against the end surface of each magnet sheet located at the first end surface; a second baffle plate, covering the second end surface and abutting against the end surface of each magnet sheet located at the second end surface; wherein at least one of the first baffle plate, the second baffle plate and the oil deflector cap is provided with a positioning indicator corresponding to the groove, for assisting in identifying the groove angle.

[0015] Optionally, the difference between the outer diameter of the first baffle plate and the outer diameter of the oil deflector cap is greater than or equal to 2 mm.

[0016] According to a second aspect of an embodiment of the utility model, a compressor is provided, comprising a rotor assembly for a compressor as described in any one of the above items.

[0017] Optionally, the rotor core is provided with a refrigerant circulation channel extending axially therethrough, and the compressor also includes: a pump body assembly, provided with a pump body exhaust port extending toward the rotor core, the pump body exhaust port being communicated with the refrigerant circulation channel, and the cross-sectional area of ​​the refrigerant circulation channel is larger than the cross-sectional area of ​​the pump body exhaust port.

[0018] Optionally, the pump body assembly includes: a main bearing, in which the end face of the rotor core along the axial direction includes a second end face, and the second end face is provided with a clearance groove opened around the central axis hole, and the main bearing is arranged on the second end face side of the rotor core and corresponds to the second end face; the main bearing includes a main bearing neck extending toward the second end face of the rotor core, and the cross-sectional area of ​​the clearance groove is larger than the outer diameter of the main bearing neck, so that the end of the main bearing neck extending toward the second end face of the rotor core can extend into the clearance groove.

[0019] Optionally, the compressor also includes: a cylinder; a crankshaft, axially inserted into the rotor core, and provided with an eccentric portion, the eccentric portion being located in the cylinder; wherein the eccentric portion is provided with a through hole, and / or the height of the eccentric portion is greater than 1 / 3 of the height of the cylinder and less than 3 / 4 of the height of the cylinder.

[0020] Optionally, the compressor further comprises: a roller, which is sleeved on the outside of the eccentric portion, and the roller is a hollow structure.

[0021] Optionally, the compressor comprises a high speed compressor having a maximum operating frequency greater than or equal to 140 Hz.

[0022] The rotor assembly for a compressor and the compressor provided by the embodiments of the present disclosure can achieve the following technical effects:

[0023] The rotor assembly is not provided with end ring parts, and the groove is directly provided on the end face of the rotor core, rather than on the end ring, which can reduce the mass and space occupied by the end ring, is conducive to realizing the high speed and miniaturization of the compressor, and can improve the high speed operation effect of the compressor while avoiding the collision between the refrigerant and oil droplets and the balance block. The groove is eccentrically provided on one side of the end face of the rotor core along the axial direction, and the weight of the groove part is removed, so that the entity on the other side of the end face forms a built-in counterweight balance part, which is equivalent to the role of the balance block. The balance block is built into the rotor core, which can avoid the collision between the balance block and the refrigerant and oil droplets, reduce the stirring effect and thus reduce the oil discharge rate. At the same time, the balance block is built into the rotor, which reduces the mechanical loss when the balance block collides with the oil droplets, reduces the windage loss of the balance block, and also reduces the flow loss when the refrigerant flows, which can improve the energy efficiency of the compressor. The setting of the built-in counterweight balance part reduces the use of separate balance block parts and can also reduce costs.

[0024] The above general description and the following description are exemplary and explanatory only and are not intended to limit the present application. BRIEF DESCRIPTION OF THE DRAWINGS

[0025] One or more embodiments are exemplarily described by corresponding drawings, which do not limit the embodiments. Elements with the same reference numerals in the drawings are shown as similar elements, and the drawings do not constitute a scale limitation, and wherein:

[0026] Figure 1 is a structural schematic diagram of a rotor assembly for a compressor provided by an embodiment of the present disclosure;

[0027] Figure 2 is a schematic structural diagram of another rotor assembly for a compressor provided by an embodiment of the present disclosure;

[0028] Figure 3 is a structural schematic diagram of another rotor assembly for a compressor provided by an embodiment of the present disclosure;

[0029] Figure 4 is a structural schematic diagram of another rotor assembly for a compressor provided by an embodiment of the present disclosure;

[0030] Figure 5 is a structural schematic diagram of another rotor assembly for a compressor provided by an embodiment of the present disclosure;

[0031] Figure 6 is a structural schematic diagram of a compressor provided by an embodiment of the present disclosure;

[0032] Figure 7 is a schematic structural diagram of a main bearing provided by an embodiment of the present disclosure;

[0033] Figure 8 is a schematic structural diagram of another main bearing provided by an embodiment of the present disclosure;

[0034] Fig. 9 is a schematic structural diagram of a secondary bearing provided by an embodiment of the present disclosure;

[0035] Fig.10 is a structural schematic diagram of an eccentric portion provided by an embodiment of the present disclosure;

[0036] Fig.11 is a schematic structural diagram of another eccentric portion provided by an embodiment of the present disclosure;

[0037] Fig.12 It is a schematic cross-sectional structure diagram of a rotor assembly for a compressor provided in an embodiment of the present disclosure.

[0038] Reference numerals:

[0039] 10: rotor core; 11: groove; 111: first groove; 112: second groove; 12: built-in counterweight balance part; 13: first end surface; 14: second end surface; 141: clearance groove; 142: reinforcement protrusion; 15: central axis hole; 16: refrigerant circulation channel;

[0040] 20: oil retaining cap; 21: oil retaining cap notch;

[0041] 30: magnet sheet; 31: first baffle; 311: first baffle notch; 32: second baffle;

[0042] 40: main bearing; 41: main bearing neck; 42: third end surface; 43: main bearing exhaust port;

[0043] 50: cylinder; 51: first cylinder; 52: second cylinder;

[0044] 60: crankshaft; 61: eccentric portion; 611: first eccentric portion; 612: second eccentric portion; 62: through hole; 621: first through hole; 622: second through hole;

[0045] 70: roller; 71: first roller; 72: second roller;

[0046] 80: pump body assembly; 801: pump body exhaust port; 81: auxiliary bearing; 811: auxiliary bearing exhaust port. DETAILED DESCRIPTION

[0047] In order to be able to understand the features and technical contents of the embodiments of the present disclosure in more detail, the implementation of the embodiments of the present disclosure is described in detail below in conjunction with the accompanying drawings. The attached drawings are for reference only and are not used to limit the embodiments of the present disclosure. In the following technical description, for the convenience of explanation, a full understanding of the disclosed embodiments is provided through multiple details. However, one or more embodiments can still be implemented without these details. In other cases, to simplify the drawings, well-known structures and devices can be simplified for display.

[0048] The terms "first", "second", etc. in the specification and claims of the disclosed embodiments and the above-mentioned drawings are used to distinguish similar objects, and are not necessarily used to describe a specific order or sequence. It should be understood that the terms used in this way can be interchanged where appropriate for the disclosed embodiments described herein. In addition, the terms "including" and "having" and any variations thereof are intended to cover non-exclusive inclusions.

[0049] In the embodiments of the present disclosure, the terms "upper", "lower", "inside", "middle", "outside", "front", "back" and the like indicate directions or positional relationships based on the directions or positional relationships shown in the accompanying drawings. These terms are mainly intended to better describe the embodiments of the present disclosure and their embodiments, and are not intended to limit the indicated devices, elements or components to have a specific direction, or to be constructed and operated in a specific direction. Moreover, in addition to being used to indicate directions or positional relationships, some of the above terms may also be used to indicate other meanings. For example, the term "upper" may also be used to indicate a certain dependency or connection relationship in certain circumstances. For those of ordinary skill in the art, the specific meanings of these terms in the embodiments of the present disclosure can be understood according to specific circumstances.

[0050] In addition, the terms "disposed", "connected", and "fixed" should be understood in a broad sense. For example, "connected" can be a fixed connection, a detachable connection, or an integral structure; it can be a mechanical connection, or an electrical connection; it can be a direct connection, or an indirect connection through an intermediate medium, or it can be an internal connection between two devices, elements, or components. For those of ordinary skill in the art, the specific meanings of the above terms in the embodiments of the present disclosure can be understood according to specific circumstances.

[0051] Unless otherwise stated, the term "plurality" means two or more.

[0052] In the embodiment of the present disclosure, the character " / " indicates that the preceding and following objects are in an "or" relationship. For example, A / B indicates: A or B.

[0053] The term "and / or" is a description of the association relationship between objects, indicating that three relationships can exist. For example, A and / or B means: A or B, or, A and B.

[0054] It should be noted that, in the absence of conflict, the embodiments and features in the embodiments of the present disclosure may be combined with each other.

[0055] At present, the compressor is usually placed vertically, and the rotor assembly mainly includes the rotor core, upper baffle, lower baffle, upper balance block, lower balance block, oil cap and other main components. The upper baffle and lower baffle are respectively arranged on the upper and lower sides of the rotor core, the upper balance block is arranged between the upper baffle and the oil cap plane, and the lower balance block is arranged below the lower baffle. When the refrigerant gas discharged from the pump body reaches the bottom of the rotor assembly, the lower balance block protrudes on one side, so that an uneven flow field is formed at the bottom of the rotor during high-speed rotation. Part of the refrigerant gas is impacted and dispersed by the lower balance block before entering the refrigerant flow hole of the rotor core to form a turbulent flow field, which increases mechanical losses and causes airflow losses during the collision between the lower balance block and the refrigerant gas. When most of the gas reaches the space between the upper baffle plate and the oil deflector cap plane above the rotor assembly through the flow holes of the rotor assembly, it cannot continue to be discharged axially upward due to the action of the oil deflector cap, and can only be thrown out from the gap to the inner wall of the compressor casing under the centrifugal force of the high-speed rotation of the rotor. However, due to the existence of the upper balance block, the space between the upper baffle plate and the oil deflector cap plane is not radially symmetrical, so the refrigerant gas is not thrown out uniformly during the throwing process, and a part of the refrigerant gas collides with the end face of the upper balance block at high speed, increasing mechanical losses and causing airflow losses. At the same time, the gas flow field formed above the rotor assembly is non-uniform and stable, resulting in poor oil discharge effect and high oil discharge rate.

[0056] The related technology opens a groove on one side of the rotor end ring to make the weight of the rotor end unbalanced, and realizes the balancing effect of the balance block through the weight of the solid part on the other side of the end ring, changing the balance block from being external to being built inside the end ring. However, the additional setting of the end ring still increases the mass of the rotor assembly, which will affect the high-speed operation of the compressor to a certain extent.

[0057] The design of the present application eliminates the balancing block and the end ring parts, and directly provides a groove in the rotor core to form a built-in counterweight balancing part to replace the external balancing block of the conventional solution.

[0058] Combination Figure 1-2 As shown, the embodiment of the present disclosure provides a rotor assembly for a compressor, including a rotor core 10. A groove 11 is provided on one side of the end surface of the rotor core 10 along the axial direction, and the groove 11 is eccentrically arranged relative to the axis of the rotor core 10 so that a built-in counterweight balancing portion 12 is formed on the entity on the other side of the end surface.

[0059] The rotor core generally refers to the main body of the rotor assembly composed of silicon steel laminations, and is a common term in the compressor industry. The present application uses the term rotor core to refer to the main body of the rotor assembly, and does not limit the material.

[0060] The rotor assembly for the compressor provided by the embodiment of the present disclosure is not provided with an end ring part. The groove 11 is directly provided on the end surface of the rotor core 10, rather than providing the groove 11 on the end ring. This can reduce the mass and space occupied by the end ring, is conducive to achieving high speed and miniaturization of the compressor, and can improve the high-speed operation effect of the compressor while avoiding collision between the refrigerant and oil droplets and the balance block.

[0061] A groove 11 is eccentrically arranged on one side of the end face of the rotor core 10 along the axial direction, and the weight of the groove 11 is removed, so that the entity on the other side of the end face forms a built-in counterweight balancing part 12, which is equivalent to the role of a balance block. The balance block is built into the rotor core 10 to avoid the collision of the balance block with the refrigerant and oil droplets, reduce the stirring effect and thus reduce the oil discharge rate. At the same time, the balance block is built into the rotor to reduce the mechanical loss when the balance block collides with the oil droplets, reduce the windage loss of the balance block, and also reduce the local resistance loss and flow loss when the refrigerant flows, which can improve the energy efficiency of the compressor. The provision of the built-in counterweight balancing part 12 reduces the use of separate balance block parts, and can also reduce costs, saving material costs and assembly costs.

[0062] The compressor provided in the present application includes compressors of types such as a twin-cylinder rotor compressor.

[0063] Optionally, combined Figure 1-2 and Fig.12As shown, the axial end face of the rotor core 10 includes a first end face 13 and a second end face 14 which is arranged opposite to the first end face 13 along the axial direction of the rotor core; wherein, a first groove 111 is provided on the first end face 13, and / or, a second groove 112 is provided on the second end face 14; when the first groove 111 is provided on the first end face 13 and the second groove 112 is provided on the second end face 14, the second groove 112 and the first groove 111 are located on opposite sides of a plane passing through the axis of the rotor core 10.

[0064] It can be understood that the groove 11 can be provided on one end surface of the rotor core 10, that is, the first groove 111 is provided on the first end surface 13, or the second groove 112 is provided on the second end surface 14. The groove 11 can also be provided on both end surfaces of the rotor core 10, that is, the first groove 111 is provided on the first end surface 13 and the second groove 112 is provided on the second end surface 14. The embodiment of the present disclosure takes the case where the groove 11 is provided on both end surfaces of the rotor core 10 as an example.

[0065] The first groove 111 and the second groove 112 are respectively arranged on the first end face 13 and the second end face 14 of the rotor core 10 in the axial direction. The grooves 11 are arranged on both end faces, which can replace the upper balancing block and the lower balancing block in the conventional solution, so that both ends of the rotor core 10 in the axial direction can avoid the stirring and collision with the refrigerant and the refrigeration oil droplets, reducing energy loss and oil droplet atomization. The second groove 112 and the first groove 111 are located on opposite sides of the plane passing through the axis of the rotor core 10, so that the rotor core 10 can have a built-in counterweight balancing part 12 on opposite sides of the plane passing through the axis, and both sides can play the role of a balancing block, so that the two end faces of the rotor core 10 tend to be balanced, and the vibration of the rotor core 10 during rotation is reduced.

[0066] Optionally, the first groove 111 is symmetrically arranged along a first radius; the second groove 112 is symmetrically arranged along a second radius; wherein the first radius is the radius of the first end face 13, and the second radius is the radius of the second end face 14; when the first radius is projected axially to the second end face 14, it forms a diameter with the second radius.

[0067] The first radius is the radius of the first end face 13, and the first groove 111 is symmetrically arranged along the first radius, so as to facilitate the positioning of the center of gravity of the first built-in counterweight balancing part corresponding to the first groove 111. The second radius is the radius of the second end face 14, and the second groove 112 is symmetrically arranged along the second radius, so as to facilitate the positioning of the center of gravity of the second built-in counterweight balancing part corresponding to the second groove 112. When the first radius is projected axially to the second end face 14, it forms a diameter with the second radius, so that the center of the first groove and the center of the second groove are symmetrical along the plane passing through the axis of the rotor core 10, so that the center of gravity of the first built-in counterweight balancing part and the center of gravity of the second built-in counterweight balancing part are symmetrical along the plane passing through the axis of the rotor core 10, which can enhance the balance of the rotor core 10 and avoid vibration of the rotor core 10 when rotating.

[0068] Optionally, the second groove 112 has the same volume as the first groove 111 .

[0069] The volume of the second groove 112 is the same as that of the first groove 111, so that the mass of the first built-in counterweight balancing part and the second built-in counterweight balancing part can be the same, so that the rotor core 10 is balanced on opposite sides of the plane passing through the axis, which can balance the rotational force, reduce vibration, and improve the stability and efficiency of the compressor.

[0070] Optionally, combined Figure 2 and Figure 6 As shown, the first end face 13 is away from the main bearing 40 of the compressor, the second end face 14 is close to the main bearing 40 of the compressor, the rotor core 10 is axially provided with a central shaft hole 15, and the second end face 14 is also provided with a make way groove 141 opened around the central shaft hole 15, which is used to make way for the main bearing 40; wherein the second groove 112 is arranged on the outer side of the make way groove 141 along the radial direction of the second end face 14.

[0071] The second end surface 14 of the rotor core 10 is provided with a clearance groove 141 for the main bearing 40 to make way, so that interference between the rotor core 10 and the main bearing 40 can be avoided during the operation of the compressor, and friction loss can be avoided. The clearance groove 141 is opened around the central axis hole 15, and the second groove 112 is eccentrically arranged relative to the axis of the rotor core 10. On the basis of the clearance groove 141, the second groove 112 is further expanded radially outward, so that the second groove 112 is arranged outside the clearance groove 141 along the radial direction of the second end surface 14.

[0072] Optionally, a cross-sectional area of ​​the second groove 112 is smaller than a cross-sectional area of ​​the first groove 111 .

[0073] The first groove 111 and the second groove 112 need to be hollowed out to the same mass, so the hollowed-out groove 11 has the same volume. Since the second end face 14 is also provided with a recess 141, and the first end face 13 and the second end face 14 have the same area, the cross-sectional area of ​​the second groove 112 is smaller than the cross-sectional area of ​​the first groove 111. In order to achieve the same volume of the groove 11, the depth of the second groove 112 is correspondingly greater than the depth of the first groove 111. In this way, the first groove 111 and the second groove 112 can achieve the same volume while minimizing the impact on the function of the rotor core 10 itself.

[0074] It is understandable that the cross-sectional area of ​​the second groove 112 may also be greater than or equal to the cross-sectional area of ​​the first groove 111. It is sufficient to ensure that the volumes of the first groove 111 and the second groove 112 are the same.

[0075] Optionally, the first groove 111 and the second groove 112 are both fan-shaped. When the sinking height is the same, the center angle of the first groove 111 is less than 180°, and the center angle of the second groove 112 is equal to 180°. In order to ensure a smaller iron loss degree of the rotor core 10, it is necessary to control the cross-sectional area of ​​the groove 11 to be as small as possible to avoid affecting the original function of the rotor core 10. It is understandable that the depth of the groove 11 can also be increased while the cross-sectional area of ​​the groove 11 is reduced to achieve the purpose of hollowing out the same mass. The contour angle and depth of the first groove 111 and the second groove 112 can be adjusted according to actual needs.

[0076] Optionally, combined Figure 3-4 As shown, the rotor assembly for the compressor further includes an oil deflector cap 20 , which is disposed on the first end surface 13 of the rotor core 10 and has a gap between the oil deflector cap 20 and the first end surface 13 , and the gap is radially symmetrical along the oil deflector cap 20 .

[0077] The first end face 13 is covered with an oil retaining cap 20, which can stop the oil and prevent the freezing oil droplets from being directly discharged axially from the first end face 13 of the rotor core 10, so that the freezing oil droplets are thrown out from the gap to the inner wall surface of the compressor housing under the centrifugal force of the high-speed rotation of the rotor core 10. Under the guidance of the oil retaining cap 20, the freezing oil droplets are refluxed, which can reduce the loss of oil and improve the oil return effect. Since the rotor core 10 cancels the external balancing block, the obstruction to the gap between the oil retaining cap 20 and the first end face 13 is reduced, and the high-speed collision between the refrigerant gas and the balancing block can be avoided. The gap is arranged radially symmetrically along the oil retaining cap 20, so that the flow resistance can be reduced when the refrigerant gas and oil flow out from the side, the refrigerant gas can be thrown out evenly, the mechanical loss is reduced, and the gas flow field can be uniform and stable.

[0078] Optionally, combined Figure 3 As shown, the oil deflector cap 20 is symmetrically arranged along the radial direction. The oil deflector cap 20 is symmetrically arranged along the radial direction, which can also ensure the symmetrical arrangement of the gap.

[0079] Specifically, the oil retaining cap 20 is provided with a plurality of positioning posts extending toward the rotor core 10, and the plurality of positioning posts are arranged circumferentially and symmetrically along the oil retaining cap 20; the rotor core 10 is correspondingly provided with a plurality of positioning holes along the circumferential direction, and the rivets penetrate the positioning posts and cooperate with the positioning holes, so that the oil retaining cap 20 can be fixed to the first end face 13 of the rotor core 10. The obstruction of the external balancing block is eliminated between the oil retaining cap 20 and the rotor core 10, and the plurality of positioning posts are arranged circumferentially and symmetrically along the oil retaining cap 20, so that the gap between the oil retaining cap and the first end face 13 of the rotor core can be divided into a plurality of symmetrical gaps.

[0080] Optionally, combined Figure 1-5 As shown, the rotor assembly for the compressor also includes a plurality of magnet sheets 30, a first baffle plate 31 and a second baffle plate 32. The plurality of magnet sheets 30 extend along the axial direction of the rotor core 10 and are arranged in sequence along the circumferential direction of the rotor core 10; the first baffle plate 31 is covered on the first end face 13, and abuts against the end face of each magnet sheet 30 located at the first end face 13; the second baffle plate 32 is covered on the second end face 14, and abuts against the end face of each magnet sheet 30 located at the second end face 14; wherein, at least one of the first baffle plate 31, the second baffle plate 32 and the oil deflector cap 20 is provided with a positioning indicator corresponding to the groove 11, for assisting in identifying the angle of the groove 11.

[0081] The rotor assembly provided in the embodiments of the present disclosure is mainly aimed at the rotor assembly of the variable frequency motor, and the variable frequency rotor assembly mainly includes a rotor core 10, a magnet sheet 30, a first baffle 31, a second baffle 32 and a rivet. The magnet sheet 30 is arranged in the rotor core 10 to realize the variable speed operation of the rotor core 10. The rotor core 10 is provided with a plurality of V-shaped magnetic steel grooves, and the plurality of magnetic steel grooves are evenly distributed in a circle around the center of the rotor core 10. The magnet sheet 30 is inserted into the V-shaped magnetic steel groove. The V-shaped magnetic steel groove is V-shaped or similar to a V-shaped setting. The rivet can fix the oil deflector cap 20, the first baffle 31, the second baffle 32 and the rotor core 10.

[0082] The first baffle 31 is covered on the first end face 13 and abuts against the end face of each magnet piece 30 located at the first end face 13. The second baffle 32 is covered on the second end face 14 and abuts against the end face of each magnet piece 30 located at the second end face 14. In this way, the first baffle 31 and the second baffle 32 can prevent the magnet piece 30 from moving axially along the rotor core 10.

[0083] In order to be able to identify the angle of the groove 11 of the rotor core 10 during the assembly process, a positioning indicator corresponding to the groove 11 is provided on at least one of the first baffle 31, the second baffle 32, and the oil deflector cap 20. During assembly, the positioning indicator is aligned with the angle of the groove 11, which can better identify the angle of the groove 11.

[0084] Optionally, combined Figure 5 As shown, the positioning indicator is a notch structure, which is opened at the outer diameter position of at least one of the first baffle plate 31 , the second baffle plate 32 , and the oil deflector cap 20 , and the position of the notch structure is aligned with the center of the groove 11 .

[0085] The notch structure is opened at the outer diameter position, the production process and structure are simple, and it is easy to identify.

[0086] The notch structure can be opened at one or more of the outer diameters of the first baffle plate 31 , the second baffle plate 3 , and the oil deflector cap 20 to form a first baffle plate notch 311 , a second baffle plate notch, and an oil deflector cap notch 21 .

[0087] This application takes the example of providing a notch structure corresponding to the groove 11 on the first baffle plate 31, the second baffle plate 32, and the oil deflector cap 20. The notch structure is aligned with the center of the groove 11, which can identify the angle of the groove 11 more accurately and quickly.

[0088] Optionally, the second groove 112 is provided with a reinforcement portion, and the reinforcement portion is arranged corresponding to the adjacent magnet piece 30 .

[0089] Since the rotor core 10 is provided with multiple V-shaped magnetic steel grooves for placing magnet sheets 30, the corners of the V-shaped magnetic steel grooves are relatively fragile. When opening the second groove 112, it is necessary to set reinforcement parts at the corners of the V-shaped magnetic steel grooves between adjacent magnet sheets 30 to improve the overall strength of the rotor core 10.

[0090] Optionally, combined Figure 2 As shown, the reinforcement portion is a reinforcement protrusion 142 protruding toward the central shaft hole 15.

[0091] When the second groove 112 is formed, a part of the solid body is retained at the corner of the magnetic steel groove to form a reinforcing protrusion 142, which can achieve the reinforcement effect, and the operation is simple, and no additional reinforcement parts are required. It can be understood that the reinforcement part can also be other reinforcement structures that can reinforce the corners of the V-shaped magnetic steel groove.

[0092] Optionally, the difference between the outer diameter of the first baffle plate 31 and the outer diameter of the oil deflector cap 20 is greater than or equal to 2 mm.

[0093] The outer diameter of the first baffle plate 31 is set to be larger than the outer diameter of the oil deflector cap 20, so that the height difference between the stator core and the rotor core 10 can be easily measured. The difference between the outer diameter of the first baffle plate 31 and the outer diameter of the oil deflector cap 20 is greater than or equal to 2 mm, so that the oil deflector cap 20 can stop and guide the moving direction of the gas refrigerant and oil droplets while also facilitating measurement.

[0094] It can be understood that the difference between the outer diameter of the first baffle plate 31 and the outer diameter of the oil deflector cap 20 can be 2 mm, 2.5 mm, 3 mm, 3.5 mm and 4 mm.

[0095] Combination Figure 6 As shown, an embodiment of the present disclosure provides a compressor, including a rotor assembly for a compressor as described in the above disclosed embodiment.

[0096] The compressor provided in the embodiment of the present disclosure includes a rotor assembly for a compressor as provided in any of the above disclosed embodiments, and thus has all the beneficial effects of the rotor assembly for a compressor provided in any of the above disclosed embodiments, which will not be repeated here.

[0097] Optionally, combined Figure 1-2 , Figure 6 and Figure 8-9 As shown, the rotor core 10 is provided with a refrigerant circulation channel 16 extending axially therethrough, and the compressor also includes a pump body assembly 80, and the pump body assembly 80 is provided with a pump body exhaust port 801 extending toward the rotor core 10, and the pump body exhaust port 801 is communicated with the refrigerant circulation channel 16, and the cross-sectional area of ​​the refrigerant circulation channel 16 is larger than the cross-sectional area of ​​the pump body exhaust port 801.

[0098] The rotor core 10 is provided with a refrigerant flow channel 16 for the refrigerant to flow, and the pump body exhaust port 801 is connected to the refrigerant flow channel 16, so that the refrigerant gas can flow out of the pump body assembly 80, flow through the refrigerant flow channel 16, and then flow out of the internal space through the exhaust pipe. The cross-sectional area of ​​the refrigerant flow channel 16 is larger than the cross-sectional area of ​​the pump body exhaust port 801, so that when the refrigerant gas flows from the pump body assembly 80 to the rotor core 10, it can flow from the pump body exhaust port 801 with a small space and high pressure into the refrigerant flow channel 16 with a large space and low pressure, which can improve the smoothness of the refrigerant flow.

[0099] Optionally, combined Figure 8-9 As shown, the pump body assembly 80 includes a main bearing 40 and a secondary bearing 81, and the pump body exhaust port 801 includes a main bearing exhaust port 43 and a secondary bearing exhaust port 811. The main bearing exhaust port 43 is opened at the main bearing 40 and extends toward the rotor core 10, and the secondary bearing exhaust port 811 is opened at the secondary bearing 81 and extends toward the rotor core 10.

[0100] Since the gas from the main bearing exhaust port 43 and the auxiliary bearing exhaust port 811 will enter the upper muffler of the compressor and then be discharged to the outside of the pump body assembly 80 from the upper muffler exhaust port, the area of ​​the pump body exhaust port 801 in the embodiment of the present disclosure is based on the exhaust port area of ​​the upper muffler.

[0101] The cross-sectional area of ​​the refrigerant circulation channel 16 is larger than the cross-sectional area of ​​the pump body exhaust port 801 , that is, the cross-sectional area of ​​the refrigerant circulation channel 16 is larger than the cross-sectional area of ​​the main bearing exhaust port 43 and also larger than the cross-sectional area of ​​the auxiliary bearing exhaust port 811 .

[0102] Optionally, the cross-sectional areas of the main bearing exhaust port 43 and the auxiliary bearing exhaust port 811 are equal.

[0103] Optionally, combined Figure 6-7 As shown, the pump body assembly 80 includes a main bearing 40, and the main bearing 40 includes a second end face 14 on the axial end face of the rotor core 10, and the second end face 14 is provided with a clearance groove 141 opened around the central axis hole 15. The main bearing 40 is arranged on the second end face 14 side of the rotor core 10 and is arranged corresponding to the second end face 14. The main bearing 40 includes a main bearing neck 41 extending toward the second end face 14 of the rotor core 10, and the cross-sectional area of ​​the clearance groove 141 is larger than the outer diameter of the main bearing neck 41, and one end of the main bearing neck 41 extending toward the second end face 14 of the rotor core 10 can extend into the clearance groove 141.

[0104] One end of the main bearing neck 41 extending toward the second end face 14 has a third end face 42 . The second end face 14 is lower than the third end face 42 , so that the third end face 42 can extend into the clearance groove 141 .

[0105] One end of the main bearing neck 41 extending toward the second end face 14 of the rotor core 10 extends into the clearance groove 141. The second end face 14 is set lower than the third end face 42, which can reduce the space between the main bearing 40 and the rotor core 10, thereby increasing the pressure in the space and improving the flow effect of the refrigerant gas. At the same time, the reduction in the space between the main bearing 40 and the rotor core 10 also helps to achieve the miniaturization of the compressor. The main bearing neck 41 extends toward the second end face 14 and is set corresponding to the second end face 14. The cross-sectional area of ​​the clearance groove 141 is larger than the outer diameter of the main bearing neck 41, and the third end face 42 is located in the clearance groove 141, so that there is a gap between the clearance groove 141 and the main bearing 40 for the normal operation of both, which can avoid interference between the main bearing neck 41 and the rotor core 10, so that the compressor can operate normally.

[0106] Optionally, combined Figure 6 As shown, the compressor also includes a cylinder 50 and a crankshaft 60; the crankshaft 60 is axially inserted into the rotor core 10, and is provided with an eccentric portion 61, and the eccentric portion 61 is located in the cylinder 50; wherein the eccentric portion 61 is provided with a through hole 611, and / or the height of the eccentric portion 61 is greater than 1 / 3 of the height of the cylinder 50 and less than 3 / 4 of the height of the cylinder 50.

[0107] The smaller the groove 11 of the rotor core 10 is, the smaller the impact on the iron loss of the rotor core 10 is. The groove 11 is provided to form a built-in counterweight balancing portion 12 on the axial end face of the rotor core 10, and the main function of the built-in counterweight balancing portion 12 is to balance the eccentric portion 61 of the crankshaft 60. Therefore, an important factor affecting the size of the groove 11 is the mass of the eccentric portion 61. In order to make the groove 11 of the rotor core 10 as small as possible, part of the mass of the eccentric portion 61 of the crankshaft 60 is removed. This can be achieved by providing a through hole 611 in the eccentric portion 61 and removing the mass in the through hole 611. It can also be achieved by reducing the height of the eccentric portion 61, thereby reducing the overall mass of the eccentric portion 61.

[0108] Optionally, combined Figure 10-11 As shown, the through hole 611 of the eccentric part 61 is opened in the axial direction. The through hole 611 is opened in the axial direction, and can guide the flow of the refrigerant while realizing the mass removal of the eccentric part 61. Fig.10 As shown, the through hole 611 may be a plurality of circular holes, such as Fig.11 As shown, the through hole 611 may also be an arc-shaped through hole 611. It is understandable that the through hole 611 may also be opened along other directions.

[0109] For the twin-cylinder rotor compressor, the number of the eccentric parts 61 and the number of the cylinders 50 are respectively two, and the two eccentric parts 61 are respectively located in the two cylinders 50 .

[0110] Optionally, combined Figure 6 and Figure 10-11 As shown, the eccentric portion 61 includes a first eccentric portion 611 and a second eccentric portion 612; the first eccentric portion 611 is arranged close to the main bearing 40, and the second eccentric portion 612 is arranged away from the main bearing 40; wherein, the first eccentric portion 611 is provided with a first through hole 621, and / or, the second eccentric portion 612 is provided with a second through hole 621.

[0111] The first eccentric portion 611 of the twin-cylinder rotor compressor may be provided with a first through hole 621, which can reduce the mass of the first eccentric portion 611, thereby forming a balance with the corresponding built-in counterweight balancing portion 12, and reducing the volume of the corresponding groove 11 accordingly. The second eccentric portion 612 may be provided with a second through hole 621, which can reduce the mass of the second eccentric portion 612, thereby forming a balance with the corresponding built-in counterweight balancing portion 12, and reducing the volume of the corresponding groove 11 accordingly.

[0112] The height of the conventional eccentric portion 61 is usually about 3 / 4 of the height of the cylinder 50. If the mass of the eccentric portion 61 is too small, it will affect the efficiency of the compressor. The embodiment of the present disclosure reduces the height of the eccentric portion 61, so that the height of the eccentric portion 61 is greater than 1 / 3 and less than 3 / 4 of the height of the cylinder 50. On the basis of ensuring the normal operation of the eccentric portion 61, the mass of the eccentric portion 61 can be reduced, so that the groove 11 of the rotor core 10 can be as small as possible, ensuring the normal operation of the rotor core 10.

[0113] Optionally, the cylinder 50 includes a first cylinder 51 and a second cylinder 52, the first eccentric portion 611 is located in the first cylinder 51, and the second eccentric portion 612 is located in the second cylinder 52; wherein, the height of the first eccentric portion 611 is greater than 1 / 3 of the height of the first cylinder 51 and less than 3 / 4 of the height of the first cylinder 51, and / or, the height of the second eccentric portion 612 is greater than 1 / 3 of the height of the second cylinder 52 and less than 3 / 4 of the height of the second cylinder 52.

[0114] In the twin-cylinder rotor compressor, the height of the first eccentric portion 611 is limited to between 1 / 3 and 3 / 4 of the height of the first cylinder 51, which can reduce the mass of the first eccentric portion 611 relative to the conventional solution, so that the groove 11 corresponding to the first eccentric portion 611 can be as small as possible. The height of the second eccentric portion 612 is limited to between 1 / 3 and 3 / 4 of the height of the second cylinder 52, which can reduce the mass of the second eccentric portion 612 relative to the conventional solution, so that the groove 11 corresponding to the second eccentric portion 612 can be as small as possible.

[0115] The original scheme (external balancing block), the disclosed embodiment scheme 1 of the present application (built-in counterweight balancing part in the rotor core), and the disclosed embodiment scheme 2 of the present application (built-in balancing block in the rotor core and through-hole in the eccentric part of the crankshaft) were respectively adopted to carry out simulation tests under the national standard working condition of 60Hz. Among them, the external balancing block in the original scheme and the built-in counterweight balancing part in the disclosed embodiment scheme 1 of the present application can achieve the same amount of balance. In the disclosed embodiment 2 of the present application, since the through-hole is provided in the eccentric part of the crankshaft, the mass of the eccentric part of the crankshaft is reduced, and the mass of the built-in counterweight balancing part that needs to balance it is also reduced accordingly. Therefore, the amount of balance that can be achieved by the built-in counterweight balancing part in the disclosed embodiment 2 of the present application is less than the amount of balance that can be achieved by the built-in counterweight balancing part in the disclosed embodiment 1 of the present application. The specific test data are shown in the following table.

[0116] It can be seen from the test data that compared with the original solution, the disclosed embodiment solution 1 of the present application can effectively reduce the oil discharge rate of the compressor and improve the energy efficiency of the compressor. The disclosed embodiment solution 2 of the present application has a similar oil discharge rate to the disclosed embodiment solution 1, and the energy efficiency of the compressor is improved. When the compressor is running at high frequency, the change trend of the oil discharge rate and energy efficiency is the same as the above trend.

[0117] Test items Original plan Public embodiment scheme 1 Public embodiment 2 Oil discharge rate / % 0.5 0.36 0.35 Energy efficiency 3.91 3.96 3.98

[0118] Optionally, combined Figure 6 As shown, the compressor further includes a roller 70 , which is sleeved on the outside of the eccentric portion 61 , and is a hollow structure.

[0119] The use of hollow rollers 70 can reduce the mass of the rollers 70 and improve the response speed and efficiency of the system. At the same time, the mass of the built-in counterweight balancing part 12 can also be reduced accordingly, thereby reducing the size of the groove 11 of the rotor core 10 and reducing the impact of the groove 11 on the overall structure of the rotor core 10.

[0120] Optionally, combined Figure 6 As shown, the roller 70 includes a first roller 71 and a second roller 72, wherein the first roller 71 is sleeved on the outside of the first eccentric portion 611, and the second roller 72 is sleeved on the outside of the second eccentric portion 612; wherein the first roller 71 is a hollow structure and / or the second roller 72 is a hollow structure.

[0121] For the twin-cylinder rotor compressor, a first roller 71 and a second roller 72 are provided. The first roller 71 and the second roller 72 may both be hollow structures, or one of them may be hollow structure, depending on actual needs.

[0122] Specifically, the inside of the roller 70 is completely hollowed out to form a hollow structure. The four surfaces of the hollow roller 70 can be welded, or two or three surfaces of the hollow roller 70 can be integrally formed and then welded to other surfaces. It is understood that the inside of the roller 70 can also be partially hollowed out.

[0123] Optionally, the compressor comprises a high speed compressor having a maximum operating frequency greater than or equal to 140 Hz.

[0124] The disclosed embodiment controls the maximum operating frequency range of the compressor to ≥140 Hz, which can form a high speed environment. The rotor assembly for the compressor involved in the above embodiments is suitable for high speed compressors, which can solve the problem of high oil discharge rate of high speed compressors.

[0125] The above description and the accompanying drawings sufficiently illustrate the embodiments of the present disclosure to enable those skilled in the art to practice them. Other embodiments may include structural and other changes. The embodiments represent only possible variations. Unless explicitly required, individual components and functions are optional, and the order of operations may vary. Portions and features of some embodiments may be included in or replace portions and features of other embodiments. The embodiments of the present disclosure are not limited to the structures described above and shown in the accompanying drawings, and various modifications and changes may be made without departing from the scope thereof. The scope of the present disclosure is limited only by the appended claims.

Claims

1. A rotor assembly for a compressor, characterized in that: include: The rotor core has a groove on one side of the axial end surface, and the groove is eccentrically arranged relative to the axis of the rotor core so that the entity on the other side of the end surface forms a built-in counterweight balancing part.

2. The rotor assembly for a compressor according to claim 1, characterized in that: The end surface of the rotor core along the axial direction includes a first end surface and a second end surface arranged opposite to the first end surface along the axial direction of the rotor core; Wherein, a first groove is provided on the first end surface, and / or a second groove is provided on the second end surface; When the first end surface is provided with the first groove and the second end surface is provided with the second groove, the second groove and the first groove are located on opposite sides of a plane passing through the axis of the rotor core.

3. The rotor assembly for a compressor according to claim 2, characterized in that: The first groove is symmetrically arranged along the first radius; the second groove is symmetrically arranged along the second radius; The first radius is the radius of the first end face, and the second radius is the radius of the second end face; when the first radius is projected onto the second end face along the axial direction, the first radius and the second radius form a diameter.

4. The rotor assembly for a compressor according to claim 2, characterized in that: The first end face is far away from the main bearing of the compressor, the second end face is close to the main bearing of the compressor, the rotor core is provided with a central shaft hole along the axial direction, and the second end face is also provided with a clearance groove opened around the central shaft hole, which is used to make way for the main bearing; Wherein, the second groove is arranged outside the clearance groove along the radial direction of the second end surface.

5. The rotor assembly for a compressor according to any one of claims 2 to 4, characterized in that: Also includes: The oil deflector cap is covered on the first end surface of the rotor core, and there is a gap between the oil deflector cap and the first end surface, and the gap is symmetrical along the radial direction of the oil deflector cap.

6. The rotor assembly for a compressor according to claim 5, characterized in that: Also includes: A plurality of magnet sheets extending along the axial direction of the rotor core and arranged in sequence along the circumferential direction of the rotor core; A first baffle, covering the first end surface and abutting against an end surface of each magnet sheet located at the first end surface; A second baffle, which is covered on the second end surface and abuts against the end surface of each magnet sheet located at the second end surface; At least one of the first baffle plate, the second baffle plate and the oil deflector cap is provided with a positioning indicator corresponding to the groove, which is used to assist in identifying the angle of the groove.

7. The rotor assembly for a compressor according to claim 6, characterized in that: The difference between the outer diameter of the first baffle plate and the outer diameter of the oil deflector cap is greater than or equal to 2 mm.

8. A compressor, characterized in that: The invention comprises a rotor assembly for a compressor according to any one of claims 1 to 7.

9. The compressor according to claim 8, characterized in that The rotor core is provided with a refrigerant flow channel extending axially therethrough, and the compressor further comprises: The pump body assembly is provided with a pump body exhaust port extending toward the rotor core, the pump body exhaust port is communicated with a refrigerant flow channel, and the cross-sectional area of ​​the refrigerant flow channel is larger than the cross-sectional area of ​​the pump body exhaust port.

10. The compressor according to claim 9, characterized in that The pump assembly includes: The main bearing is arranged on the second end face side of the rotor core and corresponds to the second end face when the end face of the rotor core along the axial direction includes a second end face and the second end face is provided with a clearance groove opened around the central axis hole; the main bearing includes a main bearing neck extending toward the second end face of the rotor core, and the cross-sectional area of ​​the clearance groove is larger than the outer diameter of the main bearing neck, so that one end of the main bearing neck extending toward the second end face of the rotor core can extend into the clearance groove.

11. The compressor according to any one of claims 8 to 10, characterized in that Also includes: cylinder; The crankshaft is axially inserted into the rotor core and is provided with an eccentric portion, and the eccentric portion is located in the cylinder; The eccentric portion is provided with a through hole, and / or the height of the eccentric portion is greater than 1 / 3 of the height of the cylinder and less than 3 / 4 of the height of the cylinder.

12. The compressor according to any one of claims 8 to 10, characterized in that Also includes: The roller is sleeved on the outside of the eccentric part and has a hollow structure.

13. The compressor according to any one of claims 8 to 10, characterized in that The compressor includes a high speed compressor having a maximum operating frequency greater than or equal to 140 Hz.

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