Dynamic balancing assembly of a compressor and compressor
By combining floating balance blocks and follow-up balance blocks, the problem of dynamic balance being broken during compressor rotation is solved, resulting in more stable operation and reduced vibration and bearing load.
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Patents(China)
- Current Assignee / Owner
- ZHUHAI LANDA COMPRESSOR
- Filing Date
- 2023-12-25
- Publication Date
- 2026-06-23
Smart Images
Figure CN117759521B_ABST
Abstract
Description
Technical Field
[0001] This invention relates to the field of air conditioning technology, and in particular to a dynamic balancing assembly for a compressor and a compressor. Background Technology
[0002] A compressor includes moving parts such as a crankshaft, bearings, connecting rods, and pistons. The crankshaft is connected to the engine's main bearing housing via bearings. The crankshaft's cranks are connected to the connecting rods, which are connected to the pistons via pins. The crankshaft is typically driven by an electric motor or engine. When the drive source starts, the crankshaft begins to rotate, and the driving connecting rods reciprocate along with the crankshaft's rotation, thereby pushing the compressor's pistons to perform compression and exhaust operations. Due to the crankshaft's eccentric structure, a dynamic imbalance can occur during crankshaft rotation. In existing technology, at least two balance blocks (main balance block and auxiliary balance block) are used to construct a balancing system for the entire shaft system, achieving dynamic balance and thus ensuring smooth compressor operation.
[0003] However, when the compressor fluctuates up and down during rotation, the original balance system will be broken, and its dynamic balance will be in an unbalanced state. This will cause the bearings to bear a greater load, and may even cause vibration due to dynamic imbalance, leading to cracking of the compressor pipeline, thereby reducing the reliability of the compressor. Summary of the Invention
[0004] The purpose of this invention is to provide a dynamic balancing component and a compressor, which aims to solve the problem in the prior art that when the compressor floats up and down during rotation, the original dynamic balance is broken, resulting in an imbalance of the compressor shaft system.
[0005] This invention provides a dynamic balancing assembly for a compressor, comprising:
[0006] A floating balance block is sleeved on the shaft assembly of the compressor. The floating balance block includes a first counterweight and a second counterweight. The weight of the first counterweight is greater than the weight of the second counterweight, and the floating balance block can rotate and float with the shaft assembly.
[0007] A follow-up balance block is mounted on the thrust bracket of the compressor;
[0008] The first counterweight of the floating balance block can drive the follower balance block to rotate synchronously. When the floating balance block floats, the center of mass of the floating balance block deviates from the rotation center line of the shaft system assembly.
[0009] Optionally, the floating balance block includes a first fixed ring, the first counterweight and the second counterweight are respectively connected to both sides of the first fixed ring and extend radially outward, and the first fixed ring is fixed to the shaft assembly.
[0010] Optionally, the follow-up balance block includes a second fixed ring disposed on the thrust bracket of the compressor. The second fixed ring is provided with a mating groove, and the first counterweight is disposed in the mating groove and can float in the mating groove.
[0011] Optionally, the follow-up balance block further includes a third counterweight block connected to the second fixed ring and extending radially inward, the third counterweight block being disposed opposite to the mating groove, and the second counterweight block being close to the third counterweight block.
[0012] Optionally, the floating balance block is located above the follower balance block, and the mating groove is open above it, allowing the first counterweight block to float up and down within the mating groove.
[0013] Optionally, the extension length of the first counterweight is greater than the extension length of the second counterweight.
[0014] Optionally, both the first counterweight and the second counterweight are fan-shaped, and the side of both the first counterweight and the second counterweight facing the extension direction is an outward arc.
[0015] Optionally, the third counterweight is adapted to the shape of the second counterweight, and the whole formed by the third counterweight and the second counterweight has the same shape as the first counterweight.
[0016] Optionally, the difference between the weight of the first counterweight and the sum of the weights of the second and third counterweights is within a predetermined range.
[0017] The present invention also provides a compressor, including a dynamic balancing assembly, a thrust bracket and a shaft assembly as described in any of the above, wherein the floating balance block is sleeved on the shaft assembly of the compressor and the follower balance block is disposed on the thrust bracket of the compressor.
[0018] This invention discloses a dynamic balancing assembly for a compressor and the compressor itself. By mounting a floating balance block on the compressor's shaft assembly, the weight of the first counterweight of the floating balance block is greater than the weight of the second counterweight. The floating balance block can rotate and float with the shaft assembly. The floating balance block is mounted on the compressor's thrust bracket. The first counterweight of the floating balance block drives the floating balance block to rotate synchronously. When the floating balance block floats, its center of mass deviates from the rotation center line of the shaft assembly, thereby constructing a new shaft balance to ensure the dynamic balance of the compressor and thus make the compressor operate more smoothly. Attached Figure Description
[0019] To more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings used in the following description of the embodiments will be briefly introduced. Obviously, the drawings described below are some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.
[0020] Figure 1 A cross-sectional structural diagram of the compressor provided by the present invention;
[0021] Figure 2 for Figure 1 A magnified structural diagram of part A in the middle;
[0022] Figure 3 This is a schematic diagram of the crankshaft provided by the present invention;
[0023] Figure 4 This is a schematic diagram of the structure of the floating balance block provided by the present invention;
[0024] Figure 5 This is a schematic diagram of the structure of the follower balance block provided by the present invention;
[0025] Figure 6 An exploded structural diagram of the dynamic balancing assembly, thrust bracket, and sliding bearing provided by the present invention;
[0026] Figure 7 A schematic diagram of the non-centrosymmetric state of the floating balance block and the follower balance block provided by the present invention;
[0027] Figure 8 for Figure 7 A magnified structural diagram of part B in the middle;
[0028] Figure 9 This is a schematic diagram of the centrally symmetrical state of the floating balance block and the follower balance block provided by the present invention.
[0029] Markings in the image:
[0030] 10. Compressor; 11. Dynamic balancing assembly; 111. Floating balance block; 1111. First counterweight; 1112. Second counterweight; 1113. First fixed ring; 112. Follower balance block; 1121. Second fixed ring; 11211. Mating groove; 1122. Third counterweight; 12. Shaft assembly; 121. Crankshaft; 122. Main balance block; 123. Secondary balance block; 13. Thrust bracket; 14. Sliding bearing. Detailed Implementation
[0031] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of the present invention. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.
[0032] It should be understood that, when used in this specification and the appended claims, the terms "comprising" and "including" indicate the presence of the described features, integrals, steps, operations, elements and / or components, but do not exclude the presence or addition of one or more other features, integrals, steps, operations, elements, components and / or collections thereof.
[0033] It should also be understood that the terminology used in this specification is for the purpose of describing particular embodiments only and is not intended to limit the invention. As used in this specification and the appended claims, the singular forms “a,” “an,” and “the” are intended to include the plural forms unless the context clearly indicates otherwise.
[0034] It should also be further understood that the term "and / or" as used in this specification and the appended claims refers to any combination of one or more of the associated listed items and all possible combinations, and includes such combinations.
[0035] Please see Figures 1-3 The shaft assembly 12 includes a crankshaft 121, a main balance block 122, and a secondary balance block 123. During normal operation of the compressor 10 (when the crankshaft 121 does not move up or down), the main balance block 122 and the secondary balance block 123 can achieve dynamic balance of the crankshaft 121, enabling the compressor 10 to operate smoothly. However, when the crankshaft 121 moves up or down during operation, the original dynamic balance is broken, causing the shaft assembly 12 to wobble and affecting the normal operation of the compressor 10. To enable the compressor 10 to operate smoothly, the inventors have proposed a dynamic balancing assembly 11 for the compressor 10. The dynamic balancing assembly 11 can achieve a new dynamic balance for the shaft assembly 12 after the original dynamic balance is broken by the movement of the crankshaft 121. The specific implementation method will be described in the following embodiments.
[0036] This invention provides a dynamic balancing assembly 11 for a compressor 10. The dynamic balancing assembly 11 includes: a floating balance block 111, which is sleeved on the shaft assembly 12 of the compressor 10. The floating balance block 111 includes a first counterweight 1111 and a second counterweight 1112. The weight of the first counterweight 1111 is greater than the weight of the second counterweight 1112, and the floating balance block 111 can rotate and float with the shaft assembly 12; and a follower balance block 112, which is disposed on the thrust bracket 13 of the compressor 10. The first counterweight 1111 of the floating balance block 111 can drive the follower balance block 112 to rotate synchronously. When the floating balance block 111 floats, the center of mass of the floating balance block 111 deviates from the rotation center line of the shaft assembly 12. In this embodiment, when the crankshaft 121 of the compressor 10 floats up and down during normal operation, the original dynamic balance of the shaft assembly 12 is broken. At the same time, the floating balance block 111 floats with the crankshaft 121, and a certain height difference is generated between the first counterweight block 1111 and the mating groove 11211. Since the weight of the first counterweight block 1111 of the floating balance block 111 is greater than the weight of the second counterweight block 1112, the center of mass of the floating balance block 111 deviates from the rotation center line of the shaft assembly 12. At this time, the force generated by the floating balance block 111 on the crankshaft 121 participates in the broken dynamic balance, establishes a new dynamic balance for the shaft assembly 12, and makes the compressor 10 run more smoothly.
[0037] Furthermore, such as Figure 4 As shown, the floating balance block 111 also includes a first fixed ring 1113. The first counterweight 1111 and the second counterweight 1112 are respectively connected to both sides of the first fixed ring 1113 and extend radially outward. The first fixed ring 1113 is fixed to the shaft assembly 12. In this embodiment, the first fixed ring 1113 is fixed to the crankshaft 121 by an interference fit or a threaded fit, and rotates or floats synchronously with the crankshaft 121 during operation.
[0038] It should be explained that an interference fit refers to a dimensional fit between two parts, where the size of one part is slightly larger than the size of the other part. This design allows for the creation of a certain pressure or friction between the two parts, ensuring a secure connection. Preferably, the first fixing ring 1113 can be fixed to the crankshaft 121 via an interference fit, meaning the size of the crankshaft 121 is slightly larger than the size of the first fixing ring 1113, allowing the first fixing ring 1113 to be tightly connected to the crankshaft 121.
[0039] Furthermore, such as Figure 5 and Figure 6As shown, the follow-up balance block 112 includes a second fixed ring 1121 disposed on the thrust bracket 13 of the compressor 10. The second fixed ring 1121 is provided with a mating groove 11211. The first counterweight block 1111 is disposed in the mating groove 11211 and can float in the mating groove 11211. In this embodiment, the mating groove 11211 is a concave groove. The mating groove 11211 is engaged with the first counterweight 1111 of the floating balance block 111. When the compressor 10 is in normal working condition (i.e., the crankshaft 121 does not float during rotation), the first counterweight 1111 will be embedded in the mating groove 11211. The second fixed ring 1121 of the follower balance block 112 is located on the sliding bearing 14 of the thrust bracket 13. When the shaft assembly 12 rotates, it will drive the floating balance block 111 to rotate synchronously. The floating balance block 111 will drive the follower balance block 112 to rotate synchronously through the first counterweight 1111. The sliding bearing 14 provides relative rotation between the follower balance block 112 and the thrust bracket 13.
[0040] Furthermore, the follow-up balance block 112 also includes a third counterweight block 1122 connected to the second fixed ring 1121 and extending radially inward. The third counterweight block 1122 is positioned opposite to the mating groove 11211, and the second counterweight block 1112 is close to the third counterweight block 1122. In this embodiment, when the compressor 10 is in normal operating condition (i.e., the crankshaft 121 does not float during rotation), the second counterweight block 1112 is close to the third counterweight block 1122, and the second counterweight block 1112 and the third counterweight block 1122 are tangent. The balance of the entire shaft assembly 12 is provided by the main balance block 122 and the secondary balance block 123 on the crankshaft 121, and is independent of the floating balance block 111.
[0041] Furthermore, such as Figures 6 to 9 As shown, the floating balance block 111 is located above the follower balance block 112, and is open above the mating groove 11211. The first counterweight block 1111 can float up and down in the mating groove 11211. In this embodiment, since the floating balance block 111 is located above the follower balance block 112 and is open above the mating groove 11211, when the crankshaft 121 floats during the operation of the compressor 10, the floating balance block 111 and the crankshaft 121 float upward together and disengage from the bottom of the mating groove 11211. The first counterweight block 1111 of the floating balance block 111 is no longer completely fitted into the mating groove 11211. Because the dynamic balancing system of the original shaft assembly 12, constructed by the main balance block 122 and the auxiliary balance block 123, has been disrupted due to the floating of the crankshaft 121, a new eccentric counterweight is needed to overcome the unbalanced force. At this time, the first counterweight block 1111 of the floating balance block 111 has floated upward together with the crankshaft 121, and a certain height difference H (e.g., ...) is generated between it and the mating groove 11211 of the following balance block 112. Figure 8As shown, the first counterweight 1111 and the second counterweight 1112, together with the third counterweight 1122 in the follow-up balance block 112, no longer form a centrally symmetrical whole. The no longer centrally symmetrical structure will generate new torque and centrifugal force on the crankshaft 121 to construct a new shaft balance, so as to ensure the dynamic balance of the compressor 10 and thus make the compressor 10 run more smoothly.
[0042] In this embodiment, combined with Figure 5 and Figure 9 As shown, when the compressor 10 is in standard operating condition (i.e., when the crankshaft 121 does not float during rotation), the height from the bottom of the first mating groove 11211 to the upper surface of the outer periphery of the second fixed ring 1121 is flush with the height of the third counterweight 1122.
[0043] It needs to be explained that the center of mass is the central point of the mass of an object or system. In an object of uniform density, the center of mass usually coincides with the geometric center, but for objects with irregular shapes or non-uniform densities, the center of mass may deviate from the geometric center. In this embodiment, when the compressor 10 is in standard operating condition (i.e., when the crankshaft 121 does not float during rotation), the first counterweight 1111 engages with the mating groove 11211, and the second counterweight 1112 and the third counterweight 1122 are close to each other and tangent. The floating balance block 111 and the following balance block 112 form a centrally symmetrical whole, and the center of mass of the centrally symmetrical whole coincides with the rotation center line of the shaft assembly 12. When the crankshaft 121 floats during the operation of the compressor 10, the first counterweight 1111 disengages from the mating groove 11211 and floats upward. The floating balance block 111 and the following balance block 112 no longer form a centrally symmetrical whole, that is, a non-centrally symmetrical whole, and the center of mass of the non-centrally symmetrical whole deviates from the rotation center line of the shaft assembly 12. It should be noted that the above-mentioned central symmetry refers not only to the overall mass of the floating balance block 111 and the follower balance block 112 being symmetrical and uniformly distributed, but also to the shape and structure of the floating balance block 111 and the follower balance block 112 being centrally symmetrical.
[0044] Furthermore, such as Figure 4 As shown, the extension length of the first counterweight 1111 is greater than the extension length of the second counterweight 1112. In this embodiment, since the weight of the first counterweight 1111 is greater than the weight of the second counterweight 1112, when manufacturing the two counterweights, in order to make the weight of the first counterweight 1111 greater than the weight of the second counterweight 1112, the extension length of the first counterweight 1111 can be increased.
[0045] In another embodiment, the radial extension length of the first counterweight 1111 is greater than the radial extension length of the second counterweight 1112, or the circumferential extension length of the first counterweight 1111 is greater than the circumferential extension length of the second counterweight 1112, thereby achieving the goal that the weight of the first counterweight 1111 is greater than that of the second counterweight 1112. It should be noted that the first counterweight 1111 and the second counterweight 1112 are made of the same material and have the same density; therefore, the factor determining their weight difference is volume. The volume of the first counterweight 1111 needs to be greater than that of the second counterweight 1112. The above are merely illustrative examples of several preferred embodiments; in other embodiments, there are many other implementation methods.
[0046] Furthermore, both the first counterweight 1111 and the second counterweight 1112 are fan-shaped, and the side of both the first counterweight 1111 and the second counterweight 1112 facing the extending direction is an outer arc. In this embodiment, the side of the first counterweight 1111 facing the extending direction is an outer arc, and the curvature of the outer arc is the same as that of the second fixing ring 1121. The mating groove 11211 is an arc-shaped groove corresponding to the first counterweight 1111. The side of the second counterweight 1112 facing the extending direction is also an outer arc, and the side of the third counterweight 1122 facing the extending direction of the mating groove 11211 is an inner arc. The outer arc of the second counterweight 1112 is close to the inner arc of the third counterweight 1122, and the curvature of the outer arc of the second counterweight 1112 is the same as that of the inner arc of the third counterweight 1122, so they can be mated together, making the second counterweight 1112 and the third counterweight 1122 form a whole.
[0047] Furthermore, the third counterweight 1122 is shaped to match the second counterweight 1112, and the overall shape formed is identical to that of the first counterweight 1111. In this embodiment, both the third counterweight 1122 and the second counterweight 1112 are fan-shaped, and their shapes are nearly identical. The width of the second counterweight 1112 gradually increases along the radial direction away from the first fixed ring 1113, while the width of the third counterweight 1122 gradually decreases along the radial direction towards the second fixed ring 1121. When the compressor 10 is in normal operating condition (i.e., when the crankshaft 121 does not float during rotation), the overall shape formed by the second counterweight 1112 and the third counterweight 1122 is nearly identical to that of the first counterweight 1111.
[0048] Furthermore, the difference between the weight of the first counterweight 1111 and the sum of the weights of the second counterweight 1112 and the third counterweight 1122 is within a predetermined range. In this embodiment, since the overall shape formed by the second counterweight 1112 and the third counterweight 1122 should be nearly identical to the shape of the first counterweight 1111 when the compressor 10 is in normal working condition (i.e., when the crankshaft 121 is not floating during rotation), an ideal difference can be set as a reference threshold when manufacturing these counterweights. When the difference between the weight of the first counterweight 1111 and the sum of the weights of the second counterweight 1112 and the third counterweight 1122 is much smaller than the ideal difference, it can be considered that the overall shape formed by the second counterweight 1112 and the third counterweight 1122 is nearly identical to the shape of the first counterweight 1111.
[0049] Furthermore, when the compressor 10 is not running, its shaft assembly 12 is in close contact with the thrust surface of the thrust bracket 13. When the compressor 10 starts, the distance between the shaft assembly 12 and the calibration reference surface will change, and the original balance will become unbalanced. It should be explained that the calibration reference surface refers to a standard surface used to measure and calibrate whether the shaft assembly 12 changes position relative to the normal operating process during operation.
[0050] The balancing verification requires the shaft system assembly 12 to be in force and torque balance. When performing dynamic balancing verification on the shaft system assembly 12, the product of the distance of each counterweight (moving disc, crankshaft 121, main balancing block 122, auxiliary balancing block 123, etc.) relative to the verification reference plane and its center of mass will affect the verification result. In the compressor 10, the floating amount of the moving disc is small, and the distance between the moving disc and the reference plane remains basically unchanged, but the other counterweights will have a large floating amount. This phenomenon will cause the dynamic balance of the compressor 10 shaft system assembly 12 to be in an unbalanced state during normal rotation.
[0051] Specifically, in the original equilibrium system, the force balance and moment balance (i.e., equilibrium equations) for equilibrium verification are:
[0052] Force balance:
[0053] M1*X1+M2*X2+M5*X5+M6*X6+M4*X4+M3*X3=0;
[0054] Torque balance:
[0055] M1*X1*Z1+M2*X2*Z2+M5*X5*Z5+M6*X6*Z6+M4*X4*Z4+M3*X3*Z3=0, where M1 is the mass of the moving disk, X1 is the eccentricity of the moving disk's center of gravity, and Z1 is the distance from the moving disk's center of gravity to the calibration reference plane; M2 is the mass of the crankshaft, X2 is the eccentricity of the crankshaft's center of gravity, and Z2 is the distance from the crankshaft's center of gravity to the calibration reference plane; M3 is the mass of the main balance block base plate, X3 is the eccentricity of the main balance block base plate, and Z3 is the mass of the main balance block base plate. M4 is the distance from the center of mass of the main balance block substrate to the verification reference plane; X4 is the mass of the main balance block counterweight; Z3 is the distance from the center of mass of the main balance block counterweight to the verification reference plane; M5 is the mass of the secondary balance block substrate; X5 is the distance from the center of mass of the secondary balance block substrate; Z5 is the distance from the center of mass of the secondary balance block substrate to the verification reference plane; M6 is the mass of the secondary balance block counterweight; X6 is the distance from the center of mass of the secondary balance block counterweight; Z6 is the distance from the center of mass of the secondary balance block counterweight to the verification reference plane.
[0056] When the compressor starts, the distance between the shaft assembly and the verification reference plane will change, and the original balance will become unbalanced. That is, Z2 to Z8 (ignoring the floating balance block for now) will become relatively smaller. Therefore, a pair of centers of mass that are balanced at rest but will be offset during motion can be introduced to construct a new balance system, thereby establishing a new balance to ensure the reliable operation of the shaft assembly. Specifically, when the original balance is broken, the force balance and torque balance (i.e., the balance equation) for the balance verification in the new balance system are:
[0057] Force balance:
[0058] M1*X1+M2*X2+M5*X5+M6*X6+M4*X4+M3*X3+M7*X7+M8*X8=0;
[0059] Torque balance:
[0060] M1*X1*Z1+M2*X2*Z2'+M5*X5*Z5'+M6*X6*Z6'+M4*X4*Z4'+M3*X3*Z3'+M7*X7*Z7'+M8*X8*Z8'=0, where Z2'~Z8' indicates that after the balance state is broken, the distance between the center of mass of the shaft assembly 12 and the verification reference plane will be relatively smaller than Z2~Z8; M7 is the counterweight mass of the follower balance block 112, X7 is the center of mass eccentricity of the counterweight of the follower balance block 112; M8 is the counterweight mass of the floating balance block 111, X8 is the center of mass eccentricity of the floating balance block 111.
[0061] The present invention also provides a compressor, including the dynamic balancing assembly 11, the thrust bracket 13 and the shaft assembly 12 as described above, wherein the floating balance block 111 is sleeved on the shaft assembly 12 of the compressor 10, the follower balance block 112 is disposed on the thrust bracket 13 of the compressor 10, and a sliding bearing 14 is provided between the thrust bracket 13 and the follower balance block 112.
[0062] The various embodiments in this specification are described in a progressive manner, with each embodiment focusing on its differences from other embodiments. Similar or identical parts between embodiments can be referred to interchangeably. For the apparatus disclosed in the embodiments, since it corresponds to the method disclosed in the embodiments, the description is relatively simple; relevant parts can be referred to in the method section. It should be noted that those skilled in the art can make various improvements and modifications to this invention without departing from its principles, and these improvements and modifications also fall within the protection scope of the claims of this invention.
[0063] It should also be noted that, in this specification, relational terms such as "first" and "second" are used only to distinguish one entity or operation from another, and do not necessarily require or imply any such actual relationship or order between these entities or operations. Furthermore, the terms "comprising," "including," or any other variations thereof are intended to cover non-exclusivity.
[0064] The term "comprises" implies that a process, method, article, or apparatus that comprises a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such a process, method, article, or apparatus. Unless otherwise specified, an element defined by the phrase "comprises a..." does not exclude the presence of other identical elements in the process, method, article, or apparatus that includes said element.
Claims
1. A dynamic balancing assembly for a compressor, characterized in that, include: A floating balance block is sleeved on the shaft assembly of the compressor. The floating balance block includes a first counterweight and a second counterweight. The weight of the first counterweight is greater than the weight of the second counterweight, and the floating balance block can rotate and float with the shaft assembly. A follow-up balance block is mounted on the thrust bracket of the compressor; The first counterweight of the floating balance block can drive the follower balance block to rotate synchronously. When the floating balance block floats, the center of mass of the floating balance block deviates from the rotation center line of the shaft system assembly.
2. The dynamic balancing assembly for the compressor according to claim 1, characterized in that, The floating balance block includes a first fixed ring, and the first counterweight and the second counterweight are respectively connected to the two sides of the first fixed ring and extend radially outward. The first fixed ring is fixed to the shaft assembly.
3. The dynamic balancing assembly for the compressor according to claim 2, characterized in that, The follow-up balance block includes a second fixed ring disposed on the thrust bracket of the compressor. The second fixed ring is provided with a mating groove. The first counterweight is disposed in the mating groove and can float in the mating groove.
4. The dynamic balancing assembly for the compressor according to claim 3, characterized in that, The follow-up balance block also includes a third counterweight block connected to the second fixed ring and extending radially inward. The third counterweight block is disposed opposite to the mating groove, and the second counterweight block is close to the third counterweight block.
5. The dynamic balancing assembly for the compressor according to claim 4, characterized in that, The floating balance block is located above the follower balance block, and the mating groove is open above it, allowing the first counterweight block to float up and down within the mating groove.
6. The dynamic balancing assembly for the compressor according to claim 4, characterized in that, The extension length of the first counterweight is greater than the extension length of the second counterweight.
7. The dynamic balancing assembly for the compressor according to claim 4, characterized in that, Both the first and second counterweights are fan-shaped, and the side of both the first and second counterweights facing the extension direction is an outward arc.
8. The dynamic balancing assembly for the compressor according to claim 7, characterized in that, The third counterweight is adapted to the shape of the second counterweight, and the whole formed by the third counterweight and the second counterweight has the same shape as the first counterweight.
9. The dynamic balancing assembly for the compressor according to claim 4, characterized in that, The difference between the weight of the first counterweight and the sum of the weights of the second and third counterweights is within a predetermined range.
10. A compressor, characterized in that, Includes the dynamic balancing assembly, thrust bracket, and shaft assembly as described in any one of claims 1-9, wherein the floating balance block is sleeved on the shaft assembly of the compressor, and the follower dynamic balance block is disposed on the thrust bracket of the compressor.