Balance block, scroll compressor, air conditioning system and vehicle

Abstract

The application discloses a balance block, a scroll compressor, an air conditioning system and a vehicle. The balance block for the scroll compressor comprises a fixed part, a connecting part and a counterweight part. The fixed part is used for being connected with a crankshaft of the scroll compressor and is located on a side of a motor rotor of the scroll compressor facing a movable scroll. The fixed part, the connecting part and the counterweight part are sequentially arranged and connected in a direction outward in a radial direction of the crankshaft. In an axial direction of the crankshaft, a distance between a mass center of the counterweight part and the movable scroll is smaller than a distance between a mass center of the connecting part and the movable scroll. In a radial direction of the crankshaft, a distance between the mass center of the counterweight part and an axis of the crankshaft is larger than a distance between the mass center of the connecting part and the axis of the crankshaft. According to the balance block for the scroll compressor, the eccentricity of the balance block is increased, the inertial force of the balance block is increased, the residual inertial force of the shaft system is reduced, and finally the vibration of the whole scroll compressor is reduced.

Description

Technical Field

[0001] This invention relates to the field of compressor technology, and in particular to a balance block, a scroll compressor, an air conditioning system, and a vehicle. Background Technology

[0002] The rapid development of the new energy vehicle sector in recent years has placed stringent requirements on vehicle vibration. As a primary vibration source in new energy vehicle systems, the electric compressor's vibration control, especially the control of first-order vibration, is particularly crucial. Electric compressors are primarily scroll compressors, and their first-order vibration is mainly influenced by the inertial force of their shaft system. Due to the large mass and eccentricity of the moving scroll plate within the scroll compressor, balancing blocks are needed to balance the inertial force and torque generated by the moving scroll plate.

[0003] Under the requirement of lightweighting in new energy vehicles, the design space of electric compressors is relatively compact. It is necessary to achieve dynamic balance design of the shaft system in a small space, that is, to maximize the inertial force and inertial torque of the balance block, and minimize the residual inertial force and torque of the entire shaft system.

[0004] As electric scroll compressors gradually move towards larger displacement and higher speed, higher requirements are placed on the dynamic balance design of the shaft system and the control of imbalance. Currently, the dynamic balance design and imbalance control of the scroll compressor shaft system at high speeds need to be improved. Summary of the Invention

[0005] The present invention aims to at least solve one of the technical problems existing in the prior art. To this end, the present invention proposes a balance block for a scroll compressor, wherein the inertial force of the balance block for the scroll compressor can be maximized, thereby reducing the vibration of the scroll compressor.

[0006] The present invention also proposes a scroll compressor, wherein the scroll compressor includes the above-mentioned balance block for the scroll compressor.

[0007] The present invention also proposes an air conditioning system, which includes the scroll compressor described above.

[0008] The present invention also proposes a vehicle comprising the above-described air conditioning system.

[0009] According to an embodiment of the present invention, a balance block for a scroll compressor includes: a fixing part for connecting to the crankshaft of the scroll compressor and located on the side of the motor rotor of the scroll compressor facing the moving scroll; a connecting part and a counterweight part, wherein the fixing part, the connecting part and the counterweight part are arranged sequentially and connected in the radially outward direction of the crankshaft, and along the axial direction of the crankshaft, the distance between the center of mass of the counterweight part and the moving scroll is less than the distance between the center of mass of the connecting part and the moving scroll, and along the radial direction of the crankshaft, the distance between the center of mass of the counterweight part and the axis of the crankshaft is greater than the distance between the center of mass of the connecting part and the axis of the crankshaft.

[0010] According to an embodiment of the present invention, the balance block for a scroll compressor maximizes the inertial force of the balance block by making the distance between the center of mass of the counterweight and the moving scroll smaller than the distance between the center of mass of the connecting part and the moving scroll in the axial direction of the crankshaft, and the distance between the center of mass of the counterweight and the axis of the crankshaft greater than the distance between the center of mass of the connecting part and the axis of the crankshaft in the radial direction of the crankshaft. This satisfies the shaft dynamic balance design requirements in the compact space of the scroll compressor, reduces the residual inertial force of the shaft system, and ultimately reduces the vibration of the entire scroll compressor.

[0011] In addition, the balance block for a scroll compressor according to the present invention may also have the following additional technical features:

[0012] In some embodiments, the fixing part is annular and disposed on the crankshaft, and the connecting part is connected to the radially outer side of the fixing part.

[0013] In some embodiments, the connecting portion includes a first connecting portion and a second connecting portion arranged radially and connected along the crankshaft. The first connecting portion is connected to the radially outer side of the fixed portion, the second connecting portion is connected to the radially outer side of the first connecting portion, and the counterweight portion is connected to the side of the second connecting portion facing the moving scroll. Along the radial direction of the crankshaft, the outer wall surface of the counterweight portion is located radially outer of the outer wall surface of the second connecting portion, and the inner wall surface of the counterweight portion is located radially inner of the outer wall surface of the second connecting portion.

[0014] In some embodiments, the surface of the first connecting portion away from the moving scroll plate and the surface of the second connecting portion away from the moving scroll plate are flush.

[0015] In some embodiments, in the direction toward the moving scroll, the first connecting portion extends beyond the second connecting portion, and the counterweight portion is connected to the radially outer side of the portion of the first connecting portion that extends beyond the second connecting portion; or, in the direction toward the moving scroll, the second connecting portion extends beyond the first connecting portion.

[0016] In some embodiments, the two surfaces of the first connecting portion facing and away from the moving scroll, the two surfaces of the second connecting portion facing and away from the moving scroll, and the two surfaces of the counterweight portion facing and away from the moving scroll are all planes and perpendicular to the axis of the crankshaft.

[0017] In some embodiments, the thickness of the counterweight part along the crankshaft axis is H1, and the distance between the surface of the connecting part that is furthest from the moving scroll and the surface of the connecting part that is furthest from the moving scroll is H2, and satisfies: 0.8≤H2 / H1≤2.0.

[0018] In some embodiments, the distance between the surface of the connecting part that is furthest from the moving volute and the surface of the connecting part that is furthest from the moving volute is H2, and the distance between the surface of the counterweight part that is furthest from the moving volute and the surface of the connecting part that is furthest from the moving volute is H3, and satisfies: 1.2≤H3 / H2≤2.0.

[0019] In some embodiments, the projections of the connecting portion and the counterweight portion onto a plane perpendicular to the crankshaft axis are fan-shaped.

[0020] In some embodiments, the outer diameter of the counterweight is R11, the inner diameter of the counterweight is R12, and the following condition is met: 1.5≤R11 / R12≤2.5.

[0021] In some embodiments, the outer diameter of the connecting part is R21, the inner diameter of the connecting part is R22, and satisfies: 1.5≤R21 / R22≤2.5.

[0022] In some embodiments, the inner diameter of the counterweight is R12, the outer diameter of the connecting part is R21, and the following condition is met: 1.0≤R21 / R12≤2.0.

[0023] In some embodiments, each of the connecting portion and the counterweight portion has two end faces in the circumferential direction of the crankshaft, and any one end face of the connecting portion is flush with the end face of the counterweight portion at the same end.

[0024] In some embodiments, the central angle between the connecting part and the counterweight part is α and satisfies: 90°≤α≤180°.

[0025] In some embodiments, the balance block is provided with a first positioning hole, the first positioning hole being located in a first centroid plane passing through the overall centroid of the balance block and the axis of the crankshaft, and the balance block is a single piece.

[0026] The present invention also provides a scroll compressor having the above-described embodiments.

[0027] According to an embodiment of the present invention, a scroll compressor includes: a crankshaft; a moving scroll, the moving scroll being eccentrically connected to one end of the crankshaft; a motor rotor, the motor rotor being disposed on and connected to the crankshaft; the aforementioned balance block for the scroll compressor, the fixed part being connected to the crankshaft and located between the motor rotor and the moving scroll; and a lower balance block, the lower balance block being connected to the side of the motor rotor away from the moving scroll.

[0028] According to embodiments of the present invention, a scroll compressor, by arranging a crankshaft, a moving scroll, a motor rotor, a lower balance block, and the balance block for a scroll compressor as described above, ensures that the distance between the center of mass of the counterweight and the moving scroll is smaller than the distance between the center of mass of the connecting part and the moving scroll in the axial direction of the crankshaft, and that the distance between the center of mass of the counterweight and the axis of the crankshaft is greater than the distance between the center of mass of the connecting part and the axis of the crankshaft in the radial direction of the crankshaft, thereby maximizing the inertial force of the balance block. Furthermore, by placing the lower balance block on the side of the motor rotor away from the moving scroll and the balance block on the side of the motor rotor facing the moving scroll, the inertial torque formed between the balance block and the lower balance block is increased, which satisfies the shaft dynamic balance requirements within the compact space of the scroll compressor, reduces the residual inertial force and torque of the shaft system, and ultimately reduces the vibration of the entire scroll compressor.

[0029] In addition, the scroll compressor according to the present invention may also have the following additional technical features:

[0030] In some embodiments, the plane passing through the overall center of mass of the balance block and the crankshaft axis is the first center of mass plane, and the plane passing through the overall center of mass of the lower balance block and the crankshaft axis is the second center of mass plane. The angle between the first center of mass plane and the second center of mass plane is β and satisfies: 175°≤β≤185°.

[0031] In some embodiments, β is 180°.

[0032] In some embodiments, the scroll compressor further includes: a first bearing disposed on the crankshaft and located between the moving scroll and the balance block; and a second bearing disposed on the crankshaft and located on the side of the lower balance block away from the motor rotor.

[0033] In some embodiments, the lower balance block is provided with a second positioning hole, which is located in a second center-of-mass plane passing through the overall center of mass of the lower balance block and the axis of the crankshaft.

[0034] An air conditioning system according to an embodiment of the present invention includes the scroll compressor described above.

[0035] According to an embodiment of the air conditioning system of the present invention, by assembling a scroll compressor as described in the above embodiment, the distance between the center of mass of the counterweight and the moving scroll is smaller than the distance between the center of mass of the connecting part and the moving scroll in the axial direction of the crankshaft, and the distance between the center of mass of the counterweight and the axis of the crankshaft is greater than the distance between the center of mass of the connecting part and the axis of the crankshaft in the radial direction of the crankshaft, thus maximizing the inertial force of the balance block. Furthermore, by placing the lower balance block on the side of the motor rotor away from the moving scroll and the balance block on the side of the motor rotor facing the moving scroll, and by increasing the eccentricity of the balance block through its design, the inertial torque formed between the balance block and the lower balance block is increased. This satisfies the shaft dynamic balance requirements within the compact space of the scroll compressor, reduces the residual inertial force and torque of the shaft system, and ultimately reduces the vibration of the entire scroll compressor.

[0036] The vehicle according to an embodiment of the present invention includes the air conditioning system described above.

[0037] According to an embodiment of the present invention, by equipping the vehicle with the air conditioning system described above, the distance between the center of mass of the counterweight and the moving scroll is smaller than the distance between the center of mass of the connecting part and the moving scroll in the axial direction of the crankshaft, and the distance between the center of mass of the counterweight and the axis of the crankshaft is greater than the distance between the center of mass of the connecting part and the axis of the crankshaft in the radial direction of the crankshaft, thereby maximizing the inertial force of the balance block. Furthermore, by placing the lower balance block on the side of the motor rotor away from the moving scroll and the balance block on the side of the motor rotor facing the moving scroll, and by increasing the eccentricity of the balance block through its design, the inertial torque formed between the balance block and the lower balance block is increased. This satisfies the shaft dynamic balance requirements within the compact space of the scroll compressor, reduces the residual inertial force and torque of the shaft system, ultimately reducing the vibration of the entire scroll compressor and improving vehicle comfort.

[0038] Additional aspects and advantages of the invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

[0039] The above and / or additional aspects and advantages of the present invention will become apparent and readily understood from the description of the embodiments taken in conjunction with the following drawings, in which:

[0040] Figure 1 This is a perspective view of the internal structure of a scroll compressor according to an embodiment of the present invention;

[0041] Figure 2 This is a front view of the internal structure of a scroll compressor according to an embodiment of the present invention;

[0042] Figure 3This is a cross-sectional view of the internal structure of a scroll compressor according to an embodiment of the present invention;

[0043] Figure 4 This is a perspective view of a balance block for a scroll compressor according to an embodiment of the present invention;

[0044] Figure 5 This is a perspective view of the balance block for a scroll compressor according to an embodiment of the present invention from another angle;

[0045] Figure 6 This is a side view of a balance block for a scroll compressor according to an embodiment of the present invention;

[0046] Figure 7 This is a side view of the balance block for a scroll compressor according to an embodiment of the present invention from another angle;

[0047] Figure 8 This is a cross-sectional view of one embodiment of a balance block for a scroll compressor according to an embodiment of the present invention;

[0048] Figure 9 This is a top view of a balance block for a scroll compressor according to an embodiment of the present invention;

[0049] Figure 10 This is a bottom view of a balance block for a scroll compressor according to an embodiment of the present invention;

[0050] Figure 11 This is a top view of the cooperation between the balance block and the lower balance block of the scroll compressor according to an embodiment of the present invention, wherein the dashed line is the center of mass plane of the balance block and the solid line is the center of mass plane of the lower balance block.

[0051] Figure 12 This is a perspective view of a balance block for a scroll compressor according to an embodiment of the present invention, wherein a first positioning hole is shown;

[0052] Figure 13 This is a perspective view of a balance block for a scroll compressor according to an embodiment of the present invention, wherein a first positioning hole is shown;

[0053] Figure 14 This is a perspective view of the lower balance block of a scroll compressor according to an embodiment of the present invention;

[0054] Figure 15 This is a schematic diagram of the structure of a vehicle according to an embodiment of the present invention;

[0055] Figure 16 This is the relationship between the overall vibration of a scroll compressor and the balance block thickness ratio H2 / H1 according to an embodiment of the present invention, wherein the long dashed line represents the optimal unbalance value for each model, and the dotted dashed line represents the boundary of the main term;

[0056] Figure 17 This is the relationship between the overall vibration of a scroll compressor and the balance block thickness ratio H3 / H2 according to an embodiment of the present invention, wherein the long dashed line represents the optimal unbalance value for each model, and the dotted dashed line represents the boundary of the sovereign term;

[0057] Figure 18 This is a cross-sectional view of yet another embodiment of a balance block for a scroll compressor according to an embodiment of the present invention.

[0058] Figure label:

[0059] 100. Scroll compressor; 200. Air conditioning system; 300. Vehicle;

[0060] 1. Balance block; 11. Fixing part; 12. Connecting part; 121. First connecting part; 122. Second connecting part; 13. Counterweight part; 14. First positioning hole;

[0061] 2. Crankshaft;

[0062] 3. Moving scroll plate;

[0063] 4. Motor rotor;

[0064] 5. Lower balance block; 51. Second positioning hole; 52. Mounting hole;

[0065] 6. First bearing;

[0066] 7. Second bearing;

[0067] 8. Eccentric sleeve;

[0068] 9. Positioning pins. Detailed Implementation

[0069] Embodiments of the present invention are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention, and should not be construed as limiting the present invention.

[0070] In the description of this invention, it should be understood that the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," and "circumferential" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of describing this invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this invention.

[0071] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this invention, "a plurality of" means two or more, unless otherwise explicitly specified.

[0072] In this invention, unless otherwise explicitly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection, an electrical connection, or a communication connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0073] The balance block 1 for a scroll compressor 100 according to an embodiment of the present invention is described below with reference to the accompanying drawings.

[0074] like Figure 4 and Figure 5 As shown, the balance block 1 for a scroll compressor 100 according to an embodiment of the present invention includes a fixing part 11, a connecting part 12, and a counterweight part 13.

[0075] Specifically, see the attached document. Figure 3 and attached Figure 4 As shown, the fixing part 11 is used to connect to the crankshaft 2 of the scroll compressor 100 and is located on the side of the motor rotor 4 of the scroll compressor 100 facing the moving scroll 3, so that the balance block 1 can be connected to and fixed on the crankshaft 2. It can be understood that the balance block 1 is located between the motor rotor 4 and the moving scroll 3 of the scroll compressor 100 and is connected to the crankshaft 2.

[0076] Further, see Appendix Figure 4 and attached Figure 5As shown, the fixing part 11, the connecting part 12, and the counterweight part 13 are arranged and connected in sequence in the radially outward direction of the crankshaft 2. It can be understood that the connecting part 12 connects the fixing part 11 and the counterweight part 13. The fixing part 11, the connecting part 12, and the counterweight part 13 are located at different positions of the balance block 1 to play different roles. Specifically, the fixing part 11 is used to connect the balance block 1 to the crankshaft 2, thereby fixing the balance block 1 on the crankshaft 2 and preventing the balance block 1 from being thrown out under the action of inertial force; the connecting part 12 is used to connect the fixing part 11 and the counterweight part 13 and shift the center of mass of the balance block 1 in the radially outward direction of the crankshaft 2 to a certain extent; the counterweight part 13 is used to shift the center of mass of the balance block 1 in the radially outward direction of the crankshaft 2 as much as possible, and the inertial force of the balance block 1 can be adjusted by changing the thickness of the counterweight part 13.

[0077] Furthermore, see the attached document. Figure 6 and attached Figure 7 As shown, along the axial direction of crankshaft 2, the distance between the center of mass of counterweight 13 and the moving scroll 3 is less than the distance between the center of mass of connecting part 12 and the moving scroll 3. That is, the center of mass of counterweight 13 and the center of mass of connecting part 12 are successively farther away from the moving scroll. Furthermore, along the radial direction of crankshaft 2, the distance between the center of mass of counterweight 13 and the axis of crankshaft 2 is greater than the distance between the center of mass of connecting part 12 and the axis of crankshaft 2. That is, the centers of mass of connecting part 12 and counterweight 13 are successively farther away from crankshaft 2, making the eccentricity of counterweight 13 greater than that of connecting part 12, thereby increasing the eccentricity of balance block 1. Through the above design, the inertial force of balance block 1 can be maximized, thus satisfying the shaft dynamic balance design requirements within the compact space of scroll compressor 100, minimizing the residual inertial force and torque of the shaft system, and ultimately reducing the vibration of the entire scroll compressor 100.

[0078] The inertial force of the counterweight 1 can be easily adjusted by changing the size of the counterweight 13.

[0079] It should be noted that the eccentricity of the counterweight 13 is the distance between the center of mass of the counterweight 13 and the axis of the crankshaft 2, and the eccentricity of the connecting part 12 is the distance between the center of mass of the connecting part 12 and the axis of the crankshaft 2.

[0080] According to an embodiment of the present invention, the balance block 1 for a scroll compressor 100 maximizes the inertial force of the balance block 1 by making the distance between the center of mass of the counterweight 13 and the moving scroll 3 in the axial direction of the crankshaft 2 smaller than the distance between the center of mass of the connecting part 12 and the moving scroll 3, and the distance between the center of mass of the counterweight 13 and the axis of the crankshaft 2 in the radial direction of the crankshaft 2 greater than the distance between the center of mass of the connecting part 12 and the axis of the crankshaft 2. This satisfies the shaft dynamic balance design requirements in the compact space of the scroll compressor 100, reduces the residual inertial force of the shaft system, and ultimately reduces the vibration of the entire scroll compressor 100.

[0081] In some embodiments of the present invention, reference is made to the appendix. Figure 4 and attached Figure 5 As shown, the fixing part 11 is annular and is disposed on the crankshaft 2, and the fixing part 11 and the crankshaft 2 are interference-fitted. Specifically, the interference fit between the fixing part 11 and the crankshaft 2 can be achieved by pressing or by heat fitting; no limitation is made here. (See attached diagram) Figure 4 As shown, the connecting part 12 is connected to the radially outer side of the fixed part 11, facilitating the connection between the connecting part 12 and the fixed part 11, making the connecting part 12 and the fixed part 11 a single unit. Furthermore, the end of the connecting part 12 near the moving scroll 3 is flush with the end of the fixed part 11 near the moving scroll 3 to ensure the continuity of the connection between the connecting part 12 and the fixed part 11, facilitating the production and processing of the balance block 1 and making assembly convenient.

[0082] In some embodiments of the present invention, reference is made to the appendix. Figure 8 As shown, the connecting part 12 includes a first connecting part 121 and a second connecting part 122 arranged radially along the crankshaft 2 and connected thereto. The first connecting part 121 is connected to the radial outer side of the fixing part 11, and the second connecting part 122 is connected to the radial outer side of the first connecting part 121. The counterweight part 13 is connected to the side of the second connecting part 122 facing the moving scroll 3, thereby facilitating the connection between the counterweight part 13 and the connecting part 12 and improving the structural strength of the balance block 1.

[0083] Reference Appendix Figure 8 As shown, along the radial direction of the crankshaft 2, the outer wall surface of the counterweight 13 is located radially outside the outer wall surface of the second connecting part 122, and the inner wall surface of the counterweight 13 is located radially inside the outer wall surface of the second connecting part 122, so that the counterweight 13 and the connecting part 12 have an overlapping part, which facilitates the processing and manufacturing of the balance block 1 and facilitates the connection between the connecting part 12 and the counterweight 13.

[0084] It is understandable that the side of the balance block 1 facing the motor rotor 4 is formed in a stepped shape.

[0085] In a further embodiment of the invention, reference is made to the appendix. Figure 8 As shown, the surface of the first connecting part 121 away from the moving scroll 3 and the surface of the second connecting part 122 away from the moving scroll 3 are flush. The structure is simple, which facilitates the processing and manufacturing of the balance block 1, improves production efficiency, and makes assembly convenient.

[0086] In a further embodiment of the invention, reference is made to the appendix. Figure 8As shown, in the direction toward the moving vortex 3, the first connecting part 121 extends beyond the second connecting part 122, and the counterweight part 13 is connected to the radially outer side of the portion of the first connecting part 121 that extends beyond the second connecting part 122, thereby improving the connection reliability between the counterweight part 13 and the connecting part 12 and improving the structural strength of the balance block 1.

[0087] Of course, the present invention is not limited thereto; see the appendix for details. Figure 18 As shown, in the direction toward the moving vortex disk 3, the second connecting portion 122 extends beyond the first connecting portion 121.

[0088] In a further embodiment of the invention, reference is made to the appendix. Figure 3 and attached Figure 8 As shown, the two surfaces of the first connecting part 121 facing away from the moving scroll 3, the two surfaces of the second connecting part 122 facing away from the moving scroll 3, and the two surfaces of the counterweight part 13 facing away from the moving scroll 3 are all planar and perpendicular to the axis of the crankshaft 2. This ensures that the thickness of the first connecting part 121, the second connecting part 122, and the counterweight part 13 remains constant in the radially outward direction of the crankshaft 2. The structure is simple, which facilitates the processing and manufacturing of the balance block 1 and improves production efficiency.

[0089] In a further embodiment of the invention, reference is made to the appendix. Figure 3 and attached Figure 8 As shown, the inner and outer walls of the first connecting part 121, the inner and outer walls of the second connecting part 122, and the inner and outer walls of the counterweight part 13 are all parallel to the axis of the crankshaft 2. The structure is simple, which facilitates the processing and manufacturing of the balance block 1 and improves production efficiency.

[0090] Of course, the present invention is not limited thereto; see the appendix for details. Figure 18 As shown, when the surface of the second connecting part 122 facing the moving scroll 3 extends beyond the surface of the first connecting part 121 facing the moving scroll 3, the inner and outer wall surfaces of the portion of the second connecting part 122 extending beyond the first connecting part 121 in the axial direction of the crankshaft 2 may not be parallel to the axis of the crankshaft 2. By controlling the tilt angle of the inner and outer wall surfaces of the portion of the second connecting part 122 extending beyond the first connecting part 121 in the axial direction of the crankshaft 2, the center of mass of the connecting part 12 can be easily controlled.

[0091] In a further embodiment of the invention, reference is made to the appendix. Figure 9 and attached Figure 10As shown, the projection of the connecting part 12 and the counterweight part 13 on the plane perpendicular to the axis of the crankshaft 2 is a fan-shaped ring. It can be understood that the connecting part 12 and the counterweight part 13 are part of a ring with the crankshaft 2 as the center. The distance from the inner diameter and the outer diameter to the center of the ring is always consistent, which facilitates the production, processing and assembly of the balance block 1, improves the adaptability of the balance block 1, and makes the balance block 1 compatible with scroll compressors 100 of various displacements.

[0092] Of course, the present invention is not limited to this; the connecting part 12 and the counterweight part 13 may also be part of an elliptical ring or other shapes.

[0093] When the projection of the connecting part 12 and the counterweight part 13 onto the plane perpendicular to the axis of the crankshaft 2 is a fan-shaped ring, along the radial direction of the crankshaft 2, the outer wall surface of the counterweight part 13 is located radially outside the outer wall surface of the connecting part 12, and the inner wall surface of the counterweight part 13 is located radially outside the inner wall surface of the connecting part 12 and radially inside the outer wall surface of the connecting part 12. It can be understood that the outer diameter of the counterweight part 13 is larger than the outer diameter of the connecting part 12, and the inner diameter of the counterweight part 13 is larger than the inner diameter of the connecting part 12 and smaller than the outer diameter of the connecting part 12.

[0094] In a further embodiment of the invention, reference is made to the appendix. Figure 8 As shown, the thickness of the counterweight 13 along the crankshaft 2 axis is H1, meaning the maximum distance between the surface of the counterweight 13 facing the moving scroll 3 and the surface facing the motor rotor 4 is H1. The distance between the surface of the connecting part 12 with the largest distance from the moving scroll 3 and the surface of the connecting part 12 with the smallest distance from the moving scroll 3 is H2. The thickness H1 of the counterweight 13 along the crankshaft 2 axis and the distance H2 between the surface of the connecting part 12 with the largest distance from the moving scroll 3 and the surface of the connecting part 12 with the smallest distance from the moving scroll 3 satisfy: 0.8 ≤ H2 / H1 ≤ 2.0. H2 / H1 within this range allows the balance block 1 to adapt to moving scrolls 3 of different masses, making it easier for the balance block 1 to meet the dynamic balancing design of the shaft system. For example, H2 / H1 can be 0.8, 0.9, 1, 1.1, 1.2, 1.3, 1.4, 1.5, 1.6, 1.7, 1.8, 1.9, or 2.

[0095] Reference Appendix Figure 16 As shown, when the distance H2 between the surface of the connecting part 12 that is furthest from the moving scroll 3 and the surface of the connecting part 12 that is furthest from the moving scroll 3 remains unchanged, the vibration of the scroll compressor 100 has an optimal H2 / H1 ratio. For different models, the optimal ratio value varies because the amount of imbalance of the moving scroll 3 is different.

[0096] In a further embodiment of the invention, reference is made to the appendix. Figure 8As shown, the distance between the surface of the connecting part 12 that is furthest from the moving scroll 3 and the surface of the connecting part 12 that is furthest from the moving scroll 3 is H2. The distance between the surface of the counterweight part 13 that is furthest from the moving scroll 3 and the surface of the connecting part 12 that is furthest from the moving scroll 3 is H3. The distances H2 and H3 between the surface of the connecting part 12 that is furthest from the moving scroll 3 and the surface of the connecting part 12 that is furthest from the moving scroll 3 satisfy the condition: 1.2 ≤ H3 / H2 ≤ 2.0. A H3 / H2 ratio within this range allows the balance block 1 to be adapted to moving scrolls 3 of different masses, making it easier for the balance block 1 to meet the dynamic balancing design of the shaft system. For example, H3 / H2 can be 1.2, 1.3, 1.4, 1.5, 1.6, 1.7, 1.8, 1.9, or 2.

[0097] Reference Appendix Figure 17 As shown, when the distance H2 between the surface of the connecting part 12 that is furthest from the moving scroll 3 and the surface of the connecting part 12 that is furthest from the moving scroll 3 remains unchanged, the vibration of the scroll compressor 100 has an optimal ratio of H3 / H2. For different models, the optimal ratio value varies because the amount of imbalance of the moving scroll 3 is different.

[0098] In a further embodiment of the invention, reference is made to the appendix. Figure 8 As shown, the thickness of the counterweight 13 along the crankshaft 2 axis is H1, the distance between the surface of the connecting part 12 that is furthest from the moving scroll 3 and the surface of the connecting part 12 that is furthest from the moving scroll 3 is H2, and the distance between the surface of the counterweight 13 that is furthest from the moving scroll 3 and the surface of the connecting part 12 that is furthest from the moving scroll 3 is H3. H1+H2>H3, which makes it easy to connect the connecting part 12 and the counterweight 13 and the connection reliability is higher, thereby improving the stability and strength of the overall connection of the balance block 1.

[0099] In a further embodiment of the invention, reference is made to the appendix. Figure 9 As shown, the outer diameter of the counterweight 13 is R11, and the inner diameter of the counterweight 13 is R12, satisfying the condition: 1.5 ≤ R11 / R12 ≤ 2.5. Satisfying this range of R11 / R12 allows the balance block 1 to be adapted to moving scrolls 3 of different masses, making it easier for the balance block 1 to meet the dynamic balancing design of the shaft system. For example, R11 / R12 can be 1.5, 1.6, 1.7, 1.8, 1.9, 2, 2.1, 2.2, 2.3, 2.4, or 2.5.

[0100] In a further embodiment of the invention, reference is made to the appendix. Figure 10As shown, the outer diameter of the connecting part 12 is R21, and the inner diameter of the connecting part 12 is R22, satisfying the condition: 1.5 ≤ R21 / R22 ≤ 2.5. Satisfying this range of R21 / R22 allows the balance block 1 to be adapted to moving scrolls 3 of different masses, making it easier for the balance block 1 to meet the dynamic balancing design of the shaft system. For example, R21 / R22 can be 1.5, 1.6, 1.7, 1.8, 1.9, 2, 2.1, 2.2, 2.3, 2.4, or 2.5.

[0101] In a further embodiment of the invention, reference is made to the appendix. Figure 9 and attached Figure 10 As shown, the inner diameter of the counterweight 13 is R12, and the outer diameter of the connecting part 12 is R21, satisfying the condition: 1.0 ≤ R21 / R12 ≤ 2.0, meaning the inner diameter of the counterweight 13 is less than or equal to the outer diameter of the connecting part 12. This range of R21 / R12 allows the balance block 1 to be adapted to moving scrolls 3 of different masses, making it easier for the balance block 1 to meet the dynamic balancing design of the shaft system. For example, R21 / R12 can be 1, 1.1, 1.2, 1.3, 1.4, 1.5, 1.6, 1.7, 1.8, 1.9, or 2.

[0102] In a further embodiment of the invention, reference is made to the appendix. Figure 4 As shown, and in conjunction with the reference appendix Figure 9 and attached Figure 10 Each of the connecting part 12 and the counterweight part 13 has two end faces in the circumferential direction of the crankshaft 2, and any one end face of the connecting part 12 is flush with the end face of the counterweight part 13 at the same end, which facilitates the production, processing and installation of the balance block 1. Of course, the present invention is not limited to this, and any one end face of the connecting part 12 and the end face of the counterweight part 13 at the same end may not be flush.

[0103] In a further embodiment of the invention, reference is made to the appendix. Figure 8 As shown, the central angle of the connecting part 12 and the counterweight part 13 is α and satisfies: 90°≤α≤180°. That is, the central angle α of the connecting part 12 and the counterweight part 13 can be a right angle, an obtuse angle, or a straight angle, so as to increase the volume of the connecting part 12 and the counterweight part 13 in the circumferential direction of the balance block 1, thereby increasing the mass of the connecting part 12 and the counterweight part 13, thereby increasing the inertial force of the balance block 1, and further reducing the residual inertial force of the shaft system, ultimately reducing the vibration of the entire scroll compressor 100. For example, the central angle α of the connecting part 12 and the counterweight part 13 can be 90°, 120°, 150°, or 180°.

[0104] In some embodiments of the present invention, reference is made to the appendix. Figure 12 and attached Figure 13As shown, the balance block 1 is provided with a first positioning hole 14 for positioning the balance block 1 in the circumferential direction of the crankshaft 2, which can effectively reduce the assembly error of the balance block 1 and the fluctuation of inertial force. The motor rotor 4 is provided with a tooling for mounting the motor rotor 4. The first positioning hole 14, through cooperation with the pin on the tooling, can play a positioning role for the balance block 1. The first positioning hole 14 can be located at any position on the counterweight part 13 and the connecting part 12. In a specific example, as shown in the attached figure Figure 12 and attached Figure 13 As shown, the first positioning hole 14 is located on the connecting part 12 near the counterweight part 13.

[0105] In a further embodiment of the present invention, the first positioning hole 14 is located in the first centroid plane passing through the overall centroid of the balance block 1 and the axis of the crankshaft 2, so that the balance block 1 is axially symmetrical on both sides of the first centroid plane, thereby keeping the balance block 1 balanced and more stable.

[0106] In some embodiments of the present invention, the balance block 1 is a single piece, which has a stable and reliable structure, simplifies the assembly process, and shortens the production time.

[0107] The present invention also proposes a scroll compressor 100 having a balance block 1 for a scroll compressor 100 according to the above embodiments.

[0108] like Figures 1 to 3 As shown, the scroll compressor 100 according to an embodiment of the present invention includes a crankshaft 2, a moving scroll 3, a motor rotor 4, a lower balance block 5, and the aforementioned balance block 1 for the scroll compressor 100.

[0109] Specifically, the motor rotor 4 is mounted on and connected to the crankshaft 2, and the rotation of the motor rotor 4 drives the crankshaft 2 to rotate. The moving scroll 3 is eccentrically connected to one end of the crankshaft 2, that is, the rotation axis of the moving scroll 3 is parallel to and spaced apart from the axis of the crankshaft 2. The structure and working principle of the scroll compressor 100 are well known to those skilled in the art and will not be described in detail here.

[0110] Further, see attached document. Figure 2 and attached Figure 3 As shown, the fixing part 11 is connected to the crankshaft 2 and located between the motor rotor 4 and the moving scroll 3, thereby connecting and fixing the balance block 1 to the crankshaft 2. The fixing part 11 is provided on the crankshaft 2 and has an interference fit with the crankshaft 2. Specifically, the interference fit between the fixing part 11 and the crankshaft 2 can be achieved by pressing or by heat fitting; there is no limitation here.

[0111] Additionally, please refer to the appendix. Figure 1 To be continued Figure 3As shown, the lower balance block 5 is connected to the side of the motor rotor 4 away from the moving scroll 3 to ensure that the inertial torque formed between the lower balance block 5 and the balance block 1 is as large as possible, thereby reducing the residual inertial torque of the shaft system. The lower balance block 5 has multiple mounting holes 52, and fasteners passing through these holes 52 can connect the lower balance block 5 to the motor rotor 4. In a specific example, refer to the attached diagram. Figure 14 As shown, the lower balance block 5 has two mounting holes 52, which connect the lower balance block 5 to the motor rotor 4 from two different points to ensure the stability of the connection between the lower balance block 5 and the motor rotor 4. Additionally, the fasteners can be rivets or screws; there are no restrictions here.

[0112] According to an embodiment of the present invention, the scroll compressor 100, by providing a crankshaft 2, a moving scroll 3, a motor rotor 4, a lower balance block 5, and the balance block 1 of the scroll compressor 100 described above, ensures that the distance between the center of mass of the counterweight 13 and the moving scroll 3 is smaller than the distance between the center of mass of the connecting portion 12 and the moving scroll 3 in the axial direction of the crankshaft 2, and that the distance between the center of mass of the counterweight 13 and the axis of the crankshaft 2 is greater than the distance between the center of mass of the connecting portion 12 and the axis of the crankshaft 2 in the radial direction of the crankshaft 2, thereby maximizing the inertial force of the balance block 1. Furthermore, by placing the lower balance block 5 on the side of the motor rotor 4 away from the moving scroll 3 and the balance block 1 on the side of the motor rotor 4 facing the moving scroll 3, the inertial torque formed between the balance block 1 and the lower balance block 5 is increased, which satisfies the shaft dynamic balance requirements within the compact space of the scroll compressor 100, reduces the residual inertial force and torque of the shaft system, and ultimately reduces the vibration of the entire scroll compressor 100.

[0113] In some embodiments of the present invention, reference is made to the appendix. Figure 11 As shown, the plane passing through the overall center of mass of the balancing block 1 and the axis of the crankshaft 2 is the first center of mass plane, and the plane passing through the overall center of mass of the lower balancing block 5 and the axis of the crankshaft 2 is the second center of mass plane. The angle between the first and second center of mass planes is β, which satisfies: 175°≤β≤185°. This ensures that the inertial forces of the balancing block 1 and the lower balancing block 5 are in opposite directions and, as far as possible, cancel out the inertial force of the moving scroll 3. For example, the angle β between the first and second center of mass planes can be 175°, 178°, 180°, or 185°.

[0114] Preferably, refer to the appendix Figure 11 As shown, β is 180°, which makes the inertial forces of the balance block 1 and the lower balance block 5 opposite in direction, maximizing the effect of canceling out the inertial force of the moving vortex disk 3.

[0115] In some embodiments of the present invention, reference is made to the appendix. Figure 1 To be continued Figure 3As shown, the scroll compressor 100 also includes a first bearing 6 and a second bearing 7, which together support the crankshaft 2. Specifically, the first bearing 6 is located on the crankshaft 2 between the moving scroll 3 and the balance block 1, and the second bearing 7 is located on the crankshaft 2 on the side of the lower balance block 5 away from the motor rotor 4. In a specific example, the inner ring of one of the first bearing 6 and the second bearing 7 is interference-fitted with the crankshaft 2, while the inner ring of the other is clearance-fitted with the crankshaft 2. This facilitates the assembly of the first bearing 6 and the second bearing 7 and prevents the crankshaft 2 from jamming while ensuring coaxiality. Furthermore, the first bearing 6 and the second bearing 7 can be rolling bearings or sliding bearings; there is no limitation here.

[0116] In some embodiments of the present invention, reference is made to the appendix. Figure 14 As shown, the lower balance block 5 is provided with a second positioning hole 51, which is used to position the lower balance block 5 in the circumferential direction of the crankshaft 2, which can effectively reduce the assembly error of the lower balance block 5 and the fluctuation of inertial force. By having two pins on the tooling pass through the first positioning hole 14 and the second positioning hole 51 respectively, the relative position of the balance block 1 and the lower balance block 5 in the radial direction of the crankshaft 2 can be defined.

[0117] In a further embodiment of the present invention, the second positioning hole 51 is located in the second centroid plane passing through the overall centroid of the lower balance block 5 and the axis of the crankshaft 2, so that the lower balance block 5 is axially symmetrical on both sides of the second centroid plane, thereby keeping the lower balance block 5 balanced and more stable.

[0118] In some embodiments of the present invention, reference is made to the appendix. Figure 3 As shown, the scroll compressor 100 also includes an eccentric sleeve 8 and a locating pin 9. Specifically, the eccentric sleeve 8 is located at one end of the crankshaft 2 and is eccentrically positioned to the crankshaft 2. The locating pin 9 is fixedly connected to one end of the crankshaft 2 and is used to connect the eccentric sleeve 8 and the crankshaft 2. The moving scroll 3 is located on the eccentric sleeve 8. The eccentric sleeve 8 has an inner hole. The eccentric sleeve 8 can rotate around the locating pin 9, and the moving scroll 3 can rotate around the eccentric sleeve 8.

[0119] In some embodiments of the present invention, reference is made to the appendix. Figure 11As shown, the mass of the balance block 1 is M1, and the distance between the center of mass of the balance block 1 and the axis of the crankshaft 2 is L1. M1 × L1 = U1, where U1 is the unbalance of the balance block 1. The mass of the lower balance block 5 is M2, and the distance between the center of mass of the lower balance block 5 and the axis of the crankshaft 2 is L2. M2 × L2 = U2, where U2 is the unbalance of the lower balance block 5, and satisfies the following conditions: 1700 gmm ≤ U1 ≤ 2300 gmm, 600 gmm ≤ U2 ≤ 1000 gmm. Within this range, U1 and U2 can accommodate moving scrolls 3 of different masses, making it easier for the balance block 1 and the lower balance block 5 to meet the dynamic balancing design of the shaft system, reducing the residual inertial force and torque of the shaft system, and ultimately reducing the vibration of the entire scroll compressor 100. For example, the unbalance U1 of the balancing block 1 can be 1700 gmm, 1800 gmm, 1900 gmm, 2000 gmm, 2100 gmm, 2200 gmm, or 2300 gmm. The unbalance U2 of the lower balancing block 5 can be 600 gmm, 700 gmm, 800 gmm, 900 gmm, or 1000 gmm.

[0120] In some embodiments of the present invention, 1900 gmm ≤ U1 ≤ 2200 gmm, and 700 gmm ≤ U2 ≤ 950 gmm, making it easier for the balance block 1 and the lower balance block 5 to meet the dynamic balance design of the shaft system, reducing the residual inertial force and torque of the shaft system, and ultimately reducing the vibration of the entire scroll compressor 100. For example, the unbalance U1 of the balance block 1 can be 1900 gmm, 2000 gmm, 2100 gmm, or 2200 gmm. The unbalance U2 of the lower balance block 5 can be 700 gmm, 750 gmm, 800 gmm, 900 gmm, or 950 gmm.

[0121] In some embodiments of the present invention, reference is made to the appendix. Figure 11 As shown, L1 and L2 satisfy: 0.9 ≤ L1 / L2 ≤ 1.3. Further, the distances between the axes of the balance block 1, the lower balance block 5, and the crankshaft 2 are defined, allowing the balance block 1 and the lower balance block 5 to accommodate moving scrolls 3 of different masses and easily meet the requirements of shaft dynamic balancing design. For example, L1 / L2 can be 0.9, 1, 1.1, 1.2, or 1.3.

[0122] The following is for reference. Figures 1 to 14 A scroll compressor 100 according to a specific embodiment of the present invention is described.

[0123] Specifically, such as Figures 1 to 14 As shown, the scroll compressor 100 includes a balance block 1, a crankshaft 2, a moving scroll 3, a motor rotor 4, a lower balance block 5, a first bearing 6, and a second bearing 7.

[0124] Furthermore, the motor rotor 4 is mounted on and connected to the crankshaft 2, and the rotation of the motor rotor 4 drives the crankshaft 2 to rotate. The moving scroll 3 is eccentrically connected to one end of the crankshaft 2, that is, the rotation axis of the moving scroll 3 is parallel to and spaced apart from the axis of the crankshaft 2. The balance block 1 is located between the motor rotor 4 and the moving scroll 3 of the scroll compressor 100, and is connected to the crankshaft 2. The lower balance block 5 is connected to the side of the motor rotor 4 away from the moving scroll 3 to ensure that the inertial torque formed between the lower balance block 5 and the balance block 1 is as large as possible, thereby reducing the residual inertial torque of the shaft system. The lower balance block 5 is provided with two mounting holes 52, which connect the lower balance block 5 to the motor rotor 4 from two different points to ensure the stability of the connection between the lower balance block 5 and the motor rotor 4. The first bearing 6 is located on the crankshaft 2 and between the moving scroll 3 and the balance block 1, and the second bearing 7 is located on the crankshaft 2 and on the side of the lower balance block 5 away from the motor rotor 4.

[0125] In addition, the plane passing through the overall center of mass of the balance block 1 and the axis of the crankshaft 2 is the first center of mass plane, and the plane passing through the overall center of mass of the lower balance block 5 and the axis of the crankshaft 2 is the second center of mass plane. The angle β between the first center of mass plane and the second center of mass plane is 180°, so that the inertial forces of the balance block 1 and the lower balance block 5 are opposite in direction, maximizing the effect of canceling out the inertial force of the moving scroll 3.

[0126] Furthermore, the balance block 1 is a single piece and includes a fixing part 11, a connecting part 12, and a counterweight part 13. The fixing part 11 is used to connect to the crankshaft 2 of the scroll compressor 100 and is located on the side of the motor rotor 4 of the scroll compressor 100 facing the moving scroll 3, so that the balance block 1 can be connected to and fixed on the crankshaft 2; the connecting part 12 is used to connect the fixing part 11 and the counterweight part 13 and to a certain extent shift the center of mass of the balance block 1 in the radial outward direction along the crankshaft 2; the counterweight part 13 is used to shift the center of mass of the balance block 1 in the radial outward direction along the crankshaft 2 as much as possible, and the inertial force of the balance block 1 can be adjusted by changing the thickness of the counterweight part 13.

[0127] Furthermore, the fixing part 11, the connecting part 12, and the counterweight part 13 are arranged and connected in sequence in the radial outward direction of the crankshaft 2. Along the axial direction of the crankshaft 2, the distance between the center of mass of the counterweight part 13 and the moving scroll 3 is smaller than the distance between the center of mass of the connecting part 12 and the moving scroll 3. And along the radial direction of the crankshaft 2, the distance between the center of mass of the counterweight part 13 and the axis of the crankshaft 2 is greater than the distance between the center of mass of the connecting part 12 and the axis of the crankshaft 2, so that the eccentricity of the counterweight part 13 is greater than the eccentricity of the connecting part 12, thereby increasing the eccentricity of the balance block 1.

[0128] Specifically, the fixing part 11 is annular and disposed on the crankshaft 2. The connecting part 12 is connected to the outer peripheral wall of the fixing part 11, making the connecting part 12 and the fixing part 11 an integral unit. The connecting part 12 includes a first connecting part 121 and a second connecting part 122 arranged and connected along the radial direction of the crankshaft 2. The first connecting part 121 is connected to the radial outer side of the fixing part 11, the second connecting part 122 is connected to the radial outer side of the first connecting part 121, and the counterweight part 13 is connected to the side of the second connecting part 122 facing the moving scroll 3. Along the radial direction of the crankshaft 2, the outer wall surface of the counterweight part 13 is located radially outer of the outer wall surface of the second connecting part 122, and the inner wall surface of the counterweight part 13 is located radially inner of the outer wall surface of the second connecting part 122.

[0129] Furthermore, the surface of the first connecting portion 121 that is away from the moving scroll 3 and the surface of the second connecting portion 122 that is away from the moving scroll 3 are flush. In the direction toward the moving scroll 3, the first connecting portion 121 extends beyond the second connecting portion 122, and the counterweight portion 13 is connected to the radially outer side of the portion of the first connecting portion 121 that extends beyond the second connecting portion 122. The two surfaces of the first connecting portion 121 that face and are away from the moving scroll 3, the two surfaces of the second connecting portion 122 that face and are away from the moving scroll 3, and the two surfaces of the counterweight portion 13 that face and are away from the moving scroll 3 are all planar and perpendicular to the axis of the crankshaft 2.

[0130] Furthermore, the thickness of the counterweight 13 along the crankshaft 2 axis is H1, the distance between the surface of the connecting part 12 that is furthest from the moving scroll 3 and the surface of the connecting part 12 that is furthest from the moving scroll 3 is H2, and the distance between the surface of the counterweight 13 that is furthest from the moving scroll 3 and the surface of the connecting part 12 that is furthest from the moving scroll 3 is H3. H1, H2, and H3 satisfy the following conditions: 0.8≤H2 / H1≤2.0, 1.2≤H3 / H2≤2.0, and H1+H2>H3. This facilitates the connection between the connecting part 12 and the counterweight 13 and improves the reliability of the connection, thereby enhancing the overall stability and strength of the balance block 1 connection.

[0131] Furthermore, the projections of the connecting part 12 and the counterweight part 13 onto the plane perpendicular to the crankshaft 2 axis are fan-shaped annular. The outer diameter of the counterweight part 13 is R11, and its inner diameter is R12. The outer diameter of the connecting part 12 is R21, and its inner diameter is R22. R11, R12, R21, and R22 satisfy the following conditions: 1.5 ≤ R11 / R12 ≤ 2.5, 1.5 ≤ R21 / R22 ≤ 2.5, and 1.0 ≤ R21 / R12 ≤ 2.0. Each of the connecting part 12 and the counterweight part 13 has two end faces in the circumferential direction of the crankshaft 2, and any end face of the connecting part 12 is flush with the end face of the counterweight part 13 at the same end, facilitating the production, processing, and installation of the balance block 1. The central angle of the connecting part 12 and the counterweight part 13 is α and satisfies: 90° ≤ α ≤ 180°.

[0132] Furthermore, the mass of the balance block 1 is M1, the distance between the center of mass of the balance block 1 and the axis of the crankshaft 2 is L1, M1×L1=U1, the mass of the lower balance block 5 is M2, the distance between the center of mass of the lower balance block 5 and the axis of the crankshaft 2 is L2, M2×L2=U2, and satisfying: 1900gmm≤U1≤2200gmm, 700gmm≤U2≤950gmm, 0.9≤L1 / L2≤1.3.

[0133] Furthermore, the balance block 1 is provided with a first positioning hole 14, which is located in a first center-of-gravity plane passing through the overall center of gravity of the balance block 1 and the axis of the crankshaft 2. The first positioning hole 14 can be located at any position on the counterweight part 13 and the connecting part 12. The lower balance block 5 is provided with a second positioning hole 51, which is located in a second center-of-gravity plane passing through the overall center of gravity of the lower balance block 5 and the axis of the crankshaft 2. The first positioning hole 14 and the second positioning hole 51 are used to position the balance block 1 and the lower balance block 5 in the circumferential direction of the crankshaft 2, which can effectively reduce the assembly error of the balance block 1 and the lower balance block 5 and the fluctuation of inertial force. By having two pins on the tooling of the motor rotor 4 pass through the first positioning hole 14 and the second positioning hole 51 respectively, the relative position of the balance block 1 and the lower balance block 5 in the radial direction of the crankshaft 2 can be defined.

[0134] In addition, the scroll compressor 100 also includes an eccentric sleeve 8 and a locating pin 9. Specifically, the eccentric sleeve 8 is located at one end of the crankshaft 2 and is eccentrically positioned to the crankshaft 2. The locating pin 9 is fixedly connected to one end of the crankshaft 2 and is used to connect the eccentric sleeve 8 and the crankshaft 2. The moving scroll 3 is located on the eccentric sleeve 8. The eccentric sleeve 8 has an inner hole and can rotate around the locating pin 9. The moving scroll 3 can also rotate around the eccentric sleeve 8.

[0135] Table 1 shows the key geometric dimensions and proportions of the balance block 1 used in scroll compressors 100 with different displacements. For ease of manufacturing and standardization, generally only the thickness of the counterweight part 13, i.e., H1 and H3, needs to be adjusted to adjust the imbalance of the balance block 1 (see Table 2). The overall eccentricity of the balance block 1 is between the inner diameter R22 and the outer diameter R21 of the connecting part 12, i.e., the center of mass is projected within the connecting part 12.

[0136] Table 1. Size proportions and eccentricities of the counterweights

[0137] R21 R22 R11 / R12 R21 / R22 R21 / R12 H3 / H2 H2 / H1 Eccentricity mm mm mm Balance weight 1 (Model 1) 30 15 2 2 1.5 1.661 1.170 17.0 Balance weight 2 (Model 2) 30 15 2 2 1.5 1.581 1.240 16.7 Balance weight 3 (Model 3) 30 15 2 2 1.5 1.581 1.348 16.3 Balance weight 4 (Model 4) 30 15 2 2 1.5 1.613 1.240 16.7

[0138] Table 2 shows the shaft system balancing calculations for scroll compressors 100 with different displacements. The unbalance (product of mass, eccentricity, and center of mass direction vector) of the moving scroll 3, crankshaft 2, and motor rotor 4 is a fixed value. By optimizing the unbalance of balance block 1 and lower balance block 5, the total unbalance of the shaft system is reduced to zero. Specifically, because the center of mass of balance block 1 is on the opposite side of the crankshaft 2 axis from the centers of mass of moving scroll 3, lower balance block 5, etc. (the angle between their planes is 180°), its unbalance is negative.

[0139] Table 2. Imbalance of various components in the shaft system of a scroll compressor (unit: g / mm)

[0140] Components Model 1 Model 2 Model 3 Model 4 Moving scroll 1101 1053 998 943 Crankshaft and motor rotor 190 186 189 193 Balance block -2145 -2045 -1941 -2023 Lower balance block 854 806 754 887 Shaft system total 0 0 0 0

[0141] Table 3 shows the measured first-order vibration amplitude of the scroll compressor 100 at 8000 rpm. Due to the deviation between the center of mass of the actually machined parts and the theoretical design position, it is impossible to achieve an ideal balance position, and the vibration value is greater than zero. As the imbalance of the moving scroll 3 increases, the vibration increases, but the overall amplitude is relatively small.

[0142] Table 3. First-order vibration amplitude of scroll compressor (unit: m / s2)

[0143] model Model 1 Model 2 Model 3 Model 4 amplitude 9.6 8.8 6.5 4.6

[0144] The present invention also proposes an air conditioning system 200 having the scroll compressor 100 of the above embodiments.

[0145] According to the air conditioning system 200 of the present invention, by arranging the scroll compressor 100 of the above embodiment, the distance between the center of mass of the counterweight 13 and the moving scroll 3 in the axial direction of the crankshaft 2 is smaller than the distance between the center of mass of the connecting part 12 and the moving scroll 3, and the distance between the center of mass of the counterweight 13 and the axis of the crankshaft 2 in the radial direction of the crankshaft 2 is greater than the distance between the center of mass of the connecting part 12 and the axis of the crankshaft 2, the inertial force of the balance block 1 can be maximized. Furthermore, by placing the lower balance block 5 on the side of the motor rotor 4 away from the moving scroll 3 and the balance block 1 on the side of the motor rotor 4 facing the moving scroll 3, the inertial torque formed between the balance block 1 and the lower balance block 5 is increased, which can meet the shaft dynamic balance requirements in the compact space of the scroll compressor 100, reduce the residual inertial force and torque of the shaft system, and ultimately reduce the vibration of the entire scroll compressor 100.

[0146] The present invention also proposes a vehicle 300 having the air conditioning system 200 of the above embodiments.

[0147] According to the vehicle 300 of the present invention, by setting the air conditioning system 200 of the above embodiment, the distance between the center of mass of the counterweight 13 and the moving scroll 3 in the axial direction of the crankshaft 2 is smaller than the distance between the center of mass of the connecting part 12 and the moving scroll 3, and the distance between the center of mass of the counterweight 13 and the axis of the crankshaft 2 in the radial direction of the crankshaft 2 is greater than the distance between the center of mass of the connecting part 12 and the axis of the crankshaft 2, thereby maximizing the inertial force of the balance block 1. Furthermore, by placing the lower balance block 5 on the side of the motor rotor 4 away from the moving scroll 3 and placing the balance block 1 on the side of the motor rotor 4 facing the moving scroll 3, the inertial torque formed between the balance block 1 and the lower balance block 5 is increased, which can meet the shaft dynamic balance requirements in the compact space of the scroll compressor 100, reduce the residual inertial force and torque of the shaft system, and ultimately reduce the vibration of the entire scroll compressor 100, thereby improving the comfort of the vehicle 300.

[0148] Here, please refer to the appendix. Figure 15 As shown, vehicle 300 can be a new energy vehicle. In some embodiments, the new energy vehicle can be a pure electric vehicle with an electric motor as the main driving force. In other embodiments, the new energy vehicle can also be a hybrid vehicle with both an internal combustion engine and an electric motor as the main driving force. Regarding the internal combustion engine and electric motor mentioned in the above embodiments that provide driving power for the new energy vehicle, the internal combustion engine can use gasoline, diesel, hydrogen, etc. as fuel, and the way to provide electrical energy to the electric motor can be a power battery, hydrogen fuel cell, etc., without special limitation. It should be noted that this is merely an exemplary description of the structure of new energy vehicles, etc., and is not intended to limit the scope of protection of this invention.

[0149] Furthermore, in some embodiments, the scroll compressor 100 applicable to the aforementioned new energy vehicles according to embodiments of the present invention can be an electric compressor including a drive unit and a compression unit. The drive unit in the electric compressor drives the compression unit to perform compression work. For example, the drive unit can be a drive motor including a motor rotor 4 and a stator. Additionally, in some embodiments, the electric compressor can be a horizontal compressor, and the drive unit and compression unit can be arranged laterally.

[0150] Other configurations and operations of the balance block 1, scroll compressor 100, air conditioning system 200, and vehicle 300 according to embodiments of the present invention are known to those skilled in the art and will not be described in detail here.

[0151] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. Moreover, without contradiction, those skilled in the art can combine and integrate the different embodiments or examples described in this specification, as well as the features of different embodiments or examples.

[0152] Although embodiments of the invention have been shown and described, those skilled in the art will understand that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of the invention, the scope of which is defined by the claims and their equivalents.

Claims

1. A balance block for a scroll compressor, characterized in that, include: A fixing part, which is used to connect to the crankshaft of the scroll compressor and is located on the side of the motor rotor of the scroll compressor facing the moving scroll. The connecting part and the counterweight part, the fixing part, the connecting part and the counterweight part are arranged sequentially and connected in the radially outward direction of the crankshaft. Along the axial direction of the crankshaft, the distance between the center of mass of the counterweight part and the moving scroll is less than the distance between the center of mass of the connecting part and the moving scroll. Furthermore, along the radial direction of the crankshaft, the distance between the center of mass of the counterweight part and the axis of the crankshaft is greater than the distance between the center of mass of the connecting part and the axis of the crankshaft. The thickness of the counterweight part along the crankshaft axis is H1. The distance between the surface of the connecting part that is furthest from the moving scroll and the surface of the connecting part that is furthest from the moving scroll is H2, and satisfies: 0.8≤H2 / H1≤2.

0. The distance between the surface of the counterweight part that is furthest from the moving scroll and the surface of the connecting part that is furthest from the moving scroll is H3, and satisfies: 1.2≤H3 / H2≤2.

0.

2. The balance block for a scroll compressor according to claim 1, characterized in that, The fixing part is annular and located on the crankshaft, and the connecting part is connected to the radial outer side of the fixing part.

3. The balance block for a scroll compressor according to claim 1, characterized in that, The connecting portion includes a first connecting portion and a second connecting portion arranged radially and connected along the crankshaft. The first connecting portion is connected to the radially outer side of the fixed portion, and the second connecting portion is connected to the radially outer side of the first connecting portion. The counterweight portion is connected to the side of the second connecting portion facing the moving scroll. Along the radial direction of the crankshaft, the outer wall surface of the counterweight portion is located radially outer of the outer wall surface of the second connecting portion, and the inner wall surface of the counterweight portion is located radially inner of the outer wall surface of the second connecting portion.

4. The balance block for a scroll compressor according to claim 3, characterized in that, The surface of the first connecting part away from the moving scroll plate and the surface of the second connecting part away from the moving scroll plate are flush.

5. The balance block for a scroll compressor according to claim 3, characterized in that, In the direction toward the moving scroll, the first connecting portion extends beyond the second connecting portion, and the counterweight portion is connected to the radially outer side of the portion of the first connecting portion that extends beyond the second connecting portion; Alternatively, in the direction toward the moving scroll, the second connecting portion extends beyond the first connecting portion.

6. The balance block for a scroll compressor according to claim 3, characterized in that, The two surfaces of the first connecting part facing away from and away from the moving scroll, the two surfaces of the second connecting part facing away from and away from the moving scroll, and the two surfaces of the counterweight part facing away from and away from the moving scroll are all planes and perpendicular to the axis of the crankshaft.

7. The balance block for a scroll compressor according to claim 1, characterized in that, The projections of the connecting part and the counterweight part onto the plane perpendicular to the crankshaft axis are fan-shaped.

8. The balance block for a scroll compressor according to claim 7, characterized in that, The outer diameter of the counterweight is R11, and the inner diameter of the counterweight is R12, and the following condition is met: 1.5≤R11 / R12≤2.

5.

9. The balance block for a scroll compressor according to claim 7, characterized in that, The outer diameter of the connecting part is R21, and the inner diameter of the connecting part is R22, and satisfies: 1.5≤R21 / R22≤2.

5.

10. The balance block for a scroll compressor according to claim 7, characterized in that, The inner diameter of the counterweight is R12, and the outer diameter of the connecting part is R21, and the following condition is met: 1.0≤R21 / R12≤2.

0.

11. The balance block for a scroll compressor according to claim 7, characterized in that, Each of the connecting part and the counterweight part has two end faces in the circumferential direction of the crankshaft, and any one end face of the connecting part is flush with the end face of the counterweight part at the same end.

12. The balance block for a scroll compressor according to claim 11, characterized in that, The central angle between the connecting part and the counterweight part is α and satisfies: 90°≤α≤180°.

13. The balance block for a scroll compressor according to claim 1, characterized in that, The balance block is provided with a first positioning hole, which is located in a first center plane passing through the overall center of mass of the balance block and the axis of the crankshaft, and the balance block is a single piece.

14. A scroll compressor, characterized in that, include: Crankshaft; A moving scroll, wherein the moving scroll is eccentrically connected to one end of the crankshaft; An electric motor rotor, which is mounted on and connected to the crankshaft; The balance block for a scroll compressor according to any one of claims 1-13, wherein the fixing part is connected to the crankshaft and located between the motor rotor and the moving scroll; The lower balance block is connected to the side of the motor rotor away from the moving scroll.

15. The scroll compressor according to claim 14, characterized in that, The plane passing through the overall center of mass of the balance block and the crankshaft axis is the first center of mass plane, and the plane passing through the overall center of mass of the lower balance block and the crankshaft axis is the second center of mass plane. The angle between the first center of mass plane and the second center of mass plane is β and satisfies: 175°≤β≤185°.

16. The scroll compressor according to claim 15, characterized in that, The value of β is 180°.

17. The scroll compressor according to claim 14, characterized in that, The scroll compressor also includes: A first bearing is disposed on the crankshaft and located between the moving scroll and the balance block; The second bearing is disposed on the crankshaft and located on the side of the lower balance block away from the motor rotor.

18. The scroll compressor according to claim 14, characterized in that, The lower balance block is provided with a second positioning hole, which is located in the second center plane passing through the overall center of mass of the lower balance block and the axis of the crankshaft.

19. An air conditioning system, characterized in that, Including the scroll compressor according to any one of claims 14-18.

20. A vehicle, characterized in that, Including the air conditioning system according to claim 19.

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