Rotor with non-concentric inner diameter and outer diameter and compressor

Abstract

The utility model relates to the technical field of compressors, and discloses a rotor with non-concentric inner diameter and outer diameter and a compressor, the rotor is of a cylinder structure, a first through hole for installing a crankshaft is formed in the rotor in the axial direction of the rotor, the first through hole is a round through hole, and the second through hole is a round through hole. The circle center of the first through hole and the circle center of the rotor are in a non-concentric relationship; the utility model has the following technical effects: when the rotor runs at a high speed, the borne moment balance is realized, the deformation of the crankshaft is greatly reduced, the friction phenomenon between the rotor and the stator is avoided, the abrasion between the crankshaft and the upper support is reduced, and the performance of the compressor and the reliability of high-speed running are improved.

Description

Technical Field

[0001] The utility model belongs to the technical field of compressors, and in particular relates to a rotor with non-concentric inner and outer diameters and a compressor. Background Art

[0002] Usually, a rotary compressor is composed of a pump assembly, a motor assembly, a housing assembly, refrigeration oil, a filter bottle and other components; wherein, the motor assembly is composed of a stator and a rotor, and the rotor inner diameter, the rotor outer diameter and the stator inner diameter are concentrically designed, and there is a gap distance of 0.3 to 0.6 mm between the rotor outer diameter and the stator inner diameter.

[0003] When the compressor is running, the rotor drives the pump to rotate through the crankshaft. Due to the eccentric structure of the pump, it is usually necessary to set upper and lower counterweights on the upper and lower end surfaces of the rotor to achieve balanced operation.

[0004] When the compressor is running at high speed, the centrifugal force of the upper counterweight and the lower counterweight exerts a large bending moment on the crankshaft, causing the crankshaft to bend and deform, thereby causing the rotor to bend and deflect toward the upper counterweight. The stator exerts a magnetic pull on the rotor, the magnitude of which is inversely proportional to the gap between the inner diameter of the stator and the outer diameter of the rotor, thereby causing the direction of the magnetic pull to be consistent with the direction of the centrifugal force of the upper counterweight, thereby causing a greater bending deformation of the crankshaft, increasing the wear of the crankshaft and the upper support, and in severe cases, sintering of the crankshaft and the upper support. The bending deformation of the crankshaft causes the rotor and stator to scrape the bore, that is, the stator and rotor directly rub against each other, generating a large amount of iron filings that directly damage the compressor. In addition, with the development trend of miniaturization and high-speed development of compressors, the rigidity of the crankshaft decreases and the centrifugal force of the upper counterweight increases, resulting in a greater test of the reliability of the compressor. Utility Model Content

[0005] In order to address the deficiencies of the prior art, the utility model provides a rotor and a compressor with non-concentric inner and outer diameters, which achieves balanced torque when the rotor runs at high speed, greatly reduces the deformation of the crankshaft, avoids friction between the rotor and the stator, reduces the wear of the crankshaft and the upper support, and improves the performance of the compressor and the reliability of high-speed operation.

[0006] The technical purpose to be achieved by the utility model is achieved through the following technical solutions:

[0007] The utility model provides a rotor with non-concentric inner and outer diameters. The rotor is a cylindrical structure. A first through hole for crankshaft installation is opened along the axial direction of the rotor. The first through hole is a circular through hole. The center of the first through hole is non-concentric with the center of the rotor. Through a simple eccentric structure, when the rotor is running at high speed, the centrifugal force of the upper counterweight block and the magnetic pulling force of the stator are always kept in opposite directions, so that the torque is balanced, the deformation of the crankshaft is greatly reduced, the friction between the stator and the rotor is avoided, and the wear of the crankshaft and the upper support is reduced.

[0008] In some implementations, on the same horizontal plane, the distance between the center of the first through hole and the center of the rotor is 0.05-0.5 mm, which meets the configuration requirements of products of various sizes.

[0009] The utility model also provides a compressor, comprising a stator, an upper counterweight and a rotor as described in any one of the above items; the stator is a cylindrical structure, the stator is provided with a second through hole along its axial direction, the second through hole is a circular through hole, the rotor is located in the second through hole, and the center of the second through hole is concentric with the center of the first through hole;

[0010] The rotor has an upper end face and a lower end face, and the upper end face is symmetrically divided into a first area and a second area based on a diameter M. The upper counterweight is connected to the first area, and a gap between an outer edge of the first area and the second through hole is larger than a gap between an outer edge of the second area and the second through hole, so that the centrifugal force of the upper counterweight and the stator magnetic pull are always in opposite directions, thereby reducing the bending deformation of the crankshaft.

[0011] In some implementations, let the diameter of the upper end surface perpendicular to the diameter M be N, let the end point of the diameter N located on the outer edge of the first region be a, and let the end point of the diameter N located on the outer edge of the second region be b;

[0012] The gap between the end point a and the second through hole is larger than the gap between any point on the outer edge of the upper end surface and the second through hole;

[0013] The gap between the end point b and the second through hole is smaller than the gap between any point on the outer edge of the upper end surface and the second through hole, so that the moment is balanced.

[0014] In some implementations, a lower counterweight is also included;

[0015] The lower counterweight is connected to a position on the lower end surface corresponding to the second area.

[0016] In some implementations, an upper end plate is further included, wherein the upper end plate is located between the rotor and the upper counterweight;

[0017] The upper end plate is provided with a plurality of third through holes for exposing the magnets, through which it is easy to observe whether the magnets are missing, thereby ensuring proper assembly and product quality.

[0018] In some implementations, a positioning groove for positioning and installation is provided at the edge of the upper end plate to facilitate assembly and positioning of the upper end plate.

[0019] In some implementations, the rotor, the upper end plate and the upper counterweight are fixedly connected by a first locking member, thereby improving the connection stability between the rotor, the upper end plate and the upper counterweight, thereby improving the use stability of the product.

[0020] In some implementations, the circumferential outer surface of the stator is provided with a plurality of first grooves for positioning and installation and a plurality of first drainage channels for the passage of the refrigerant along its axial direction;

[0021] The plurality of first grooves are evenly or unevenly distributed, and the plurality of first drainage channels are evenly or unevenly distributed, so as to achieve the positioning and installation of the stator and the drainage of the refrigerant.

[0022] In some implementations, a first protrusion is formed at the bottom of one of the first grooves, and the first protrusion has the function of preventing fooling and facilitating assembly.

[0023] In summary, the utility model has at least the following benefits:

[0024] 1. The utility model provides a rotor with non-concentric inner and outer diameters. Through a simple eccentric structure, when the rotor is running at high speed, the centrifugal force of the upper counterweight and the magnetic pulling force of the stator always keep in opposite directions, thereby achieving torque balance, greatly reducing the deformation of the crankshaft, avoiding friction between the stator and the rotor, and reducing the wear of the crankshaft and the upper support.

[0025] 2. The utility model provides a compressor which, after applying a rotor with non-concentric inner and outer diameters, can improve the performance and high-speed operation reliability of the compressor in the development trend of miniaturization and high-speed operation of the compressor. BRIEF DESCRIPTION OF THE DRAWINGS

[0026] Figure 1 This is a schematic diagram of the rotor of Example 1 of the utility model;

[0027] Figure 2 and Figure 3 This is a schematic diagram of a compressor according to Embodiment 2 of the present utility model;

[0028] Figure 4 This is a schematic diagram of a stator according to Embodiment 2 of the present utility model;

[0029] Figure 5 and Figure 6 This is a schematic diagram of a rotor according to Embodiment 2 of the present utility model;

[0030] Figure 7 This is a schematic diagram of a stator according to Embodiment 3 of the present utility model;

[0031] 100, rotor; 110, upper end surface; 111, first region; 112, second region; 120, lower end surface;

[0032] 200, a first through hole;

[0033] 300, stator; 310, first groove; 320, first drainage channel; 330, first protrusion;

[0034] 400, upper counterweight;

[0035] 500, second through hole;

[0036] 600, lower counterweight;

[0037] 700, upper end plate; 710, third through hole; 720, positioning groove. DETAILED DESCRIPTION

[0038] In order to make the purpose, technical solution and advantages of the implementation of the utility model clearer, the technical solution in the implementation of the utility model will be clearly and completely described below in conjunction with the drawings in the implementation of the utility model. The described implementation is a part of the implementation of the utility model, not all of the implementations.

[0039] Therefore, the following detailed description of the embodiments of the present invention provided in the accompanying drawings is not intended to limit the scope of the claimed invention, but merely represents selected embodiments of the present invention. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in the field without creative work are within the scope of protection of the present invention.

[0040] Embodiment 1:

[0041] See also Figure 1 , a rotor with non-concentric inner and outer diameters, the rotor 100 is a cylindrical structure, formed by stacking a plurality of silicon steel sheets, a through hole is opened in the middle of the plurality of silicon steel sheets, corresponding to the first through hole 200 opened in the axial direction of the rotor 100 for crankshaft installation, the crankshaft is located in the first through hole 200, and is combined with the rotor 100 by a shrink sleeve, when the compressor is running, the pump is driven to rotate by the rotor 100 through the crankshaft.

[0042] The first through hole 200 is a circular through hole, and the center of the first through hole 200 is non-concentric with the center of the rotor 100, see Figure 1 The center of the first through hole 200 is Q1, and the center of the rotor 100 is Q2.

[0043] The rotor 100 is a cylindrical structure, and the first through hole 200 is opened in the axial direction of the rotor 100. Therefore, it can be understood that the rotor with the first through hole 200 as a whole presents a hollow cylindrical structure, having an inner circle and an outer circle, the inner circle is formed by the circumferential outer edge of the first through hole 200, and the outer circle is formed by the circumferential outer edge of the rotor, that is, it can be obtained that the center of the inner circle and the center of the outer circle are non-concentric.

[0044] It can be seen from the background technology that when the direction of the magnetic pull is consistent with the direction of the centrifugal force of the upper counterweight, it will cause greater bending deformation of the crankshaft, cause sintering of the crankshaft and the upper support, and even damage the compressor. Therefore, the rotor with non-concentric inner and outer diameters provided in this embodiment has a simple eccentric structure, so that when the rotor runs at high speed, the centrifugal force of the upper counterweight block and the magnetic pull of the stator always keep in opposite directions, thereby achieving torque balance, greatly reducing the deformation of the crankshaft, avoiding friction between the stator and the rotor, and reducing the wear of the crankshaft and the upper support.

[0045] In some embodiments, on the same horizontal plane, the distance between the center of the first through hole 200 and the center of the rotor 100 is 0.05-0.5 mm, which meets the configuration requirements of products of various sizes.

[0046] For example, when the distance between the center of the first through hole 200 and the center of the rotor is set to 0.2 mm, combined with the conventional motor assembly structure, it can be understood that the motor assembly is composed of a stator 300 and a rotor, and the inner circle of the rotor, the outer circle of the rotor and the inner circle of the stator are concentrically designed, and the stator 300 is sleeved on the outside of the rotor, and there is a gap distance of 0.3 to 0.6 mm between the outside of the rotor and the stator. For ease of understanding, it is set here that there is a gap distance of 0.3 mm between the outside of the rotor and the stator. When the rotor and the stator in this embodiment are assembled, in order to keep the center of the first through hole 200 and the center of the stator The centers are concentric, that is, the inner circle of the rotor and the inner circle of the stator are kept concentrically designed. At this time, the gap distance between the outside of the rotor and the stator has a maximum gap of 0.5mm and a minimum gap of 0.1mm. Specifically, the maximum gap of 0.5mm is obtained by adding the distance between the center of the first through hole 200 and the center of the rotor 100 of 0.2mm plus the gap distance between the outside of the rotor and the stator of 0.3mm, and the minimum gap of 0.1mm is obtained by subtracting the distance between the center of the first through hole 200 and the center of the rotor 100 of 0.2mm from the gap distance between the outside of the rotor 100 and the stator of 0.3mm.

[0047] In this embodiment, the distance between the center of the first through hole and the center of the rotor is set to between 0.05 and 0.5 mm. The distance between the center of the first through hole and the center of the rotor can be selected accordingly in combination with different assembly size requirements of the stator and the rotor. While adapting to the assembly requirements, it can also ensure that the eccentric structure design can balance the torque.

[0048] Embodiment 2:

[0049] This embodiment provides a compressor based on the above embodiment. Figure 2-Figure 6 .

[0050] See also Figure 2-Figure 4 , a compressor includes a stator 300 , an upper counterweight 400 and a rotor 100 .

[0051] The stator 300 is a cylindrical structure, and a second through hole 500 is opened in the axial direction of the stator 300. The second through hole 500 is a circular through hole. The rotor 100 is located in the second through hole 500, and the center of the second through hole 500 is concentric with the center of the first through hole 200. Figure 2 , the center of the second through hole 500 is Q3, and the center of the first through hole 200 is Q1.

[0052] See also Figure 1 , Figure 5 and Figure 6 The rotor has an upper end face 110 and a lower end face 120. The upper end face 110 is symmetrically divided into a first area 111 and a second area 112 based on a diameter M. The upper counterweight 400 is connected to the first area 111, and the gap between the outer edge of the first area 111 and the second through hole 500 is larger than the gap between the outer edge of the second area 112 and the second through hole 500, so that the centrifugal force of the upper counterweight 400 and the magnetic pull of the stator 300 always keep opposite directions, thereby reducing the bending deformation of the crankshaft.

[0053] Since the center of the first through hole 200 is not concentric with the center of the rotor, and when the rotor is installed in the second through hole 500, the center of the first through hole 200 is kept concentric with the center of the second through hole 500, there must be a small gap and a large gap between the outside of the rotor and the second through hole 500.

[0054] See also Figure 6, a diameter M is defined on the upper end surface 110, and the upper end surface 110 is symmetrically divided into a first area 111 and a second area 112, and the gap between the outer edge of the first area 111 and the second through hole 500 is larger than the gap between the outer edge of the second area 112 and the second through hole 500, which is equivalent to that the center of the rotor is offset toward the second area 112 relative to the center of the second through hole 500, and therefore, the gap between the outer edge of the second area 112 and the second through hole 500 is relatively small.

[0055] The upper counterweight is connected to the side of the rotor upper end surface 110 where the gap from the second through hole 500 is larger, so that when the rotor is running at high speed, the centrifugal force of the upper counterweight and the magnetic pulling force of the stator 300 always remain in opposite directions, achieving torque balance, greatly reducing the deformation of the crankshaft, avoiding friction between the stator 300 and the rotor, and reducing the wear of the crankshaft and the upper support.

[0056] See also Figure 2 and Figure 6 In some embodiments, let the diameter on the upper end surface 110 perpendicular to the diameter M be N, let the endpoint of the diameter N located on the outer edge of the first area 111 be a, and let the endpoint of the diameter N located on the outer edge of the second area 112 be b.

[0057] Among them, the gap between endpoint a and the second through hole 500 is larger than the gap between any point on the outer edge of the upper end surface 110 and the second through hole 500, which is equivalent to endpoint a being located at the midpoint of the outer edge of the first area 111; the gap between endpoint b and the second through hole 500 is smaller than the gap between any point on the outer edge of the upper end surface 110 and the second through hole 500, which is equivalent to endpoint b being located at the midpoint of the outer edge of the second area 112. Based on this limited relationship, the positional relationship between the upper counterweight block and the diameter N can be presented as follows: the diameter N is located on the axis of symmetry of the upper counterweight block, thereby ensuring a better torque balance effect.

[0058] In some embodiments, the compressor further includes a lower counterweight 600 , which is connected to a position on the lower end surface 120 corresponding to the second area 112 .

[0059] The positions of the upper counterweight block and the lower counterweight block are set relative to each other to achieve a balanced operation effect.

[0060] Furthermore, the compressor also includes an upper end plate 700, which is located between the rotor and the upper counterweight. The upper end plate 700 is provided with a plurality of third through holes 710 for exposing magnets. The third through holes 710 are used to easily observe whether the magnets are missing, thereby ensuring proper assembly and product quality.

[0061] Typically, magnets are assembled on the rotor, and an upper end plate 700 is provided to shield the magnets to prevent them from falling. To ensure the shielding effect of the upper end plate 700 and facilitate observation of whether the magnets are missing, a third through hole 710 is opened on the upper end plate 700 at the position corresponding to the magnet. It can be understood that the third through hole 710 can only expose part of the structure of the magnet without affecting the original shielding effect of the upper end plate 700 on the magnet, and the number and position distribution of the third through holes 710 are adjusted accordingly according to the number and position distribution of the magnets.

[0062] Furthermore, a positioning groove 720 for positioning and installation is provided at the edge of the upper end plate 700, so as to facilitate assembly and positioning of the upper end plate.

[0063] The rotor, the upper end plate 700 and the upper counterweight are fixedly connected by a first locking member, thereby improving the connection stability between the rotor, the upper end plate 700 and the upper counterweight, thereby improving the use stability of the product.

[0064] It is understandable that corresponding connection holes are provided on the rotor, the upper end plate 700 and the upper counterweight, so that the first locking member can pass through the connection holes to establish a connection relationship between the rotor, the upper end plate 700 and the upper counterweight.

[0065] Embodiment 3:

[0066] The difference between this embodiment and embodiment 2 is that this embodiment further optimizes the structure of the compressor of the utility model, see Figure 7 .

[0067] The circumferential outer surface of the stator 300 is provided with a plurality of first grooves 310 for positioning and installation and a plurality of first drainage channels 320 for the passage of refrigerant along its axial direction; the plurality of first grooves 310 are evenly or unevenly spaced, and the plurality of first drainage channels 320 are evenly or unevenly spaced, so as to realize the positioning and installation of the stator 300 and the drainage of the refrigerant.

[0068] The number and position distribution of the first grooves 310 and the first drainage channels 320 can be adjusted according to actual needs. For example, the number of the first grooves 310 is three, and the three first grooves 310 are evenly spaced, and the number of the first drainage channels 320 is six, and the six first drainage channels 320 are unevenly spaced.

[0069] In order to further improve the positioning, assembly and fool-proofing of the stator 300 , a first protrusion 330 is formed at the bottom of one of the first grooves 310 . The first protrusion 330 cooperates with the positioning position inside the compressor housing to quickly align and assemble the stator 300 .

[0070] The utility model provides a compressor which, after applying a rotor with non-concentric inner and outer diameters, can improve the performance of the compressor and the reliability of high-speed operation in the development trend of miniaturization and high-speed operation of the compressor.

[0071] In the present invention, unless otherwise clearly specified and limited, the terms "install", "connect", "connect", "fix" and the like should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, it can be the internal connection of two elements or the interaction relationship between two elements. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0072] In the description of the present utility model, it should be noted that the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inside", "outside", etc. indicate the orientation or position relationship based on the orientation or position relationship shown in the accompanying drawings, or the orientation or position relationship in which the utility model product is usually placed when in use, which is only for the convenience of describing the utility model and simplifying the description, and does not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present utility model. In addition, the terms "first", "second", "third", etc. are only used to distinguish the description, and cannot be understood as indicating or implying relative importance.

[0073] In addition, the terms "horizontal", "vertical", "overhanging" and the like do not mean that the components are required to be absolutely horizontal or overhanging, but can be slightly tilted. For example, "horizontal" only means that its direction is more horizontal than "vertical", and does not mean that the structure must be completely horizontal, but can be slightly tilted.

[0074] In the present utility model, unless otherwise clearly specified and limited, the first feature being above or below the second feature may include the first and second features being in direct contact, or may include the first and second features not being in direct contact but being in contact through another feature between them. Moreover, the first feature being above, above, and above the second feature includes the first feature being directly above and obliquely above the second feature, or simply means that the first feature is higher in level than the second feature. The first feature being below, below, and below the second feature includes the first feature being directly below and obliquely below the second feature, or simply means that the first feature is lower in level than the second feature.

[0075] Although the utility model is described in conjunction with the above specific embodiments, it is obvious that those skilled in the art can make many substitutions, modifications and changes based on the above content. Therefore, all such substitutions, improvements and changes are included in the spirit and scope of the appended claims.

Claims

1. A rotor with non-concentric inner and outer diameters, characterized in that: The rotor (100) is a cylindrical structure, and is provided with a first through hole (200) for crankshaft installation along its axial direction, the first through hole (200) is a circular through hole, and the center of the first through hole (200) is non-concentric with the center of the rotor (100).

2. The rotor with non-concentric inner and outer diameters according to claim 1, characterized in that: On the same horizontal plane, the distance between the center of the first through hole (200) and the center of the rotor (100) is 0.05-0.5 mm.

3. A compressor, characterized in that: It comprises a stator (300), an upper counterweight (400), and the rotor (100) according to claim 1 or 2; The stator (300) is a cylindrical structure, and a second through hole (500) is provided on the stator (300) along its axial direction, the second through hole (500) is a circular through hole, the rotor (100) is located in the second through hole (500), and the center of the second through hole (500) is concentric with the center of the first through hole (200); The rotor (100) comprises an upper end surface (110) and a lower end surface (120), wherein the upper end surface (110) is symmetrically divided into a first region (111) and a second region (112) based on a diameter M, the upper counterweight (400) is connected to the first region (111), and a gap between an outer edge of the first region (111) and the second through hole (500) is greater than a gap between an outer edge of the second region (112) and the second through hole (500).

4. The compressor according to claim 3, characterized in that The diameter of the upper end surface (110) perpendicular to the diameter M is N, the end point of the diameter N located on the outer edge of the first region (111) is a, and the end point of the diameter N located on the outer edge of the second region (112) is b; The gap between the end point a and the second through hole (500) is larger than the gap between any point on the outer edge of the upper end surface (110) and the second through hole (500); The gap between the end point b and the second through hole (500) is smaller than the gap between any point on the outer edge of the upper end surface (110) and the second through hole (500).

5. The compressor according to claim 3, characterized in that Also includes a lower counterweight (600); The lower counterweight block (600) is connected to a position on the lower end surface (120) corresponding to the second area (112).

6. The compressor according to claim 3, characterized in that It also includes an upper end plate (700), wherein the upper end plate (700) is located between the rotor (100) and the upper counterweight (400); The upper end plate (700) is provided with a plurality of third through holes (710) for exposing the magnets.

7. The compressor according to claim 6, characterized in that A positioning groove (720) for positioning and installation is provided at the edge of the upper end plate (700).

8. The compressor according to claim 6, characterized in that The rotor, the upper end plate (700) and the upper counterweight (400) are fixedly connected via a first locking member.

9. The compressor according to claim 3, characterized in that The circumferential outer surface of the stator (300) is provided with a plurality of first grooves (310) for positioning and installation and a plurality of first drainage channels (320) for the passage of refrigerant along its axial direction; The plurality of first grooves (310) are evenly or unevenly spaced and distributed, and the plurality of first drainage channels (320) are evenly or unevenly spaced and distributed.

10. The compressor according to claim 9, characterized in that A first protrusion (330) is formed at the bottom of one of the first grooves (310).

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