Balancing weight ring for dynamic balancing of thin-walled slender shaft parts

Abstract

The present invention discloses a balancing weight ring for dynamic balancing of thin-walled slender shaft parts. The thin-walled slender shaft parts are provided with an assembly hole for assembling the balancing weight ring. The balancing weight ring is cylindrical, and a through hole corresponding to the assembly hole of the part is symmetrically provided on the first end of the balancing weight ring, and an even number of grooves are evenly provided on the end face of the second end, and the grooves extend along the length direction of the balancing weight ring. The fan-shaped structure formed between adjacent grooves is a removal part according to the imbalance amount of the part; the balancing weight ring is evenly distributed to four quadrants, and the balancing angle α and the balancing weight quadrant are determined according to the angle between the dynamic balancing focus of the part and the assembly hole, and the quadrant symmetrically distributed with the balancing weight quadrant is the removal quadrant; when the balancing weight quadrant is located in a single quadrant, the removal amount of the removal quadrant is #imgabs0#, and when the balancing weight quadrant is located in two adjacent quadrants, the removal amounts of the two removal quadrants are respectively: #imgabs1##imgabs2# The balancing weight block can accurately determine the removal length through the removal formula to maximize the imbalance amount that can be removed by the balancing weight ring.

Description

Technical Field

[0001] The present invention relates to the technical field of dynamic balance testing, and in particular to a balancing weight ring for dynamic balancing of thin-walled slender shaft parts. Background Art

[0002] Aircraft engines typically operate at speeds exceeding 10,000 rpm, placing high demands on the dynamic balance of thin-walled, slender shafts. Dynamic imbalance typically must not exceed 50 g / mm. However, as thin-walled, slender shafts grow longer and their diameters increase, dynamic balancing becomes increasingly challenging, leading to lower part qualification rates.

[0003] A common method of dynamically balancing shaft components on the market is to fit a weight ring around the outer periphery of the shaft component. For example, patent publication number CN215178366U discloses a shaft dynamic balancing adjustment structure, which includes a weight ring connected to the shaft. The weight ring is provided with a weight-removing portion for reducing the weight of the weight ring based on the dynamic balancing test data of the shaft. The weight ring is fixed to the shaft by glue. The side wall of the weight ring is provided with an assembly surface for mounting a bearing, facing its central axis. The assembly surface is provided with a disassembly groove for disassembling the bearing, along a direction toward the central axis of the weight ring. There are two disassembly grooves, and the line connecting the centers of the two disassembly grooves passes through the central axis of the weight ring. The weight-removing portion includes a plurality of weight-removing holes provided on the side wall of the weight ring. The weight-removing portion includes a weight-removing groove provided from the side wall of the weight ring toward the central axis of the weight ring. The weight-removing groove is connected to the disassembly groove. The deweighting portion includes a plurality of deweighting holes opened on the side wall of the counterweight ring and a deweighting groove opened from the side wall of the counterweight ring toward the central axis of the counterweight ring. The present application has the effect of facilitating dynamic balancing of shafts.

[0004] Some shaft parts are limited by their special uses. For example, thin-walled, slender shaft parts, which are core components in the field of aero-engines, often cannot meet their usage requirements by adding a counterweight ring on their outer periphery. Generally, a counterweight ring needs to be installed in the inner hole of the thin-walled, slender shaft part. However, there is currently no literature recording how to perform counterweight removal after the counterweight ring is installed in the inner hole of the shaft part. Therefore, it is impossible to provide meaningful reference value for how to set a counterweight ring in the thin-walled, slender shaft parts on aero-engines for dynamic balancing. Summary of the Invention

[0005] The technical problem to be solved by the present invention is to overcome the defects of the prior art and provide a balancing weight ring for dynamic balancing that is inserted into the inner hole of a thin-walled, slender shaft-like component.

[0006] The purpose of the present invention is achieved through the following technical solutions:

[0007] A balancing weight ring for dynamic balancing of thin-walled, slender shaft-like parts. The thin-walled, slender shaft-like part has an assembly hole for assembling the balancing weight ring. The balancing weight ring is cylindrical, with a first end portion symmetrically provided with through holes corresponding to the assembly holes of the part, and an end surface of the second end portion uniformly provided with an even number of grooves extending along the length of the balancing weight ring. The fan-shaped structure formed between adjacent grooves serves as a material removal portion based on the imbalance of the part.

[0008] Evenly distribute the balancing weight rings to four quadrants. Determine the balancing angle α and the balancing weight quadrant according to the angle between the dynamic balancing point of the part and the assembly hole. The quadrant symmetrically distributed with the balancing weight quadrant is the material removal quadrant.

[0009] When the counterweight quadrant is located in a single quadrant, the removal amount of the removal quadrant is

[0010] When the counterweight quadrants are located in two adjacent quadrants, the removal amounts of the two removal quadrants are:

[0011]

[0012] Where M is the dynamic unbalance, D is the outer radius of the balancing weight ring where the parts are assembled, and ρ = 4.083.

[0013] Furthermore, the number of grooves on the balance weight ring is four.

[0014] Furthermore, the fitting clearance between the balancing weight ring and the inner hole of the component is 0 to 0.016 mm.

[0015] Furthermore, the length of the removed portion of the balancing weight ring is greater than or equal to 80% of the total length of the balancing weight ring.

[0016] Furthermore, the total length of the balancing weight ring is 6% to 8% of the parts assembly.

[0017] Furthermore, the wall thickness of the removed material portion of the balancing weight ring is 2.5 to 3.5 mm.

[0018] Furthermore, the wall thickness difference of the removed material portion of the balancing weight ring is less than or equal to 0.05 mm.

[0019] Furthermore, the arc length of each groove on the balancing weight ring is 20% of the diameter of the balancing weight ring.

[0020] Furthermore, blind rivets are installed in the part assembly holes and the through holes of the balance weight ring, and the blind rivets are clearance-matched with the through holes.

[0021] Furthermore, the clearance fit accuracy is 0 to 0.016 mm.

[0022] Compared with the prior art, the present invention has the following beneficial effects:

[0023] The balancing weight block of the present invention is set in the inner hole of the part to dynamically balance the part. The removal length of the balancing weight ring can be accurately determined through the removal formula, so as to maximize the imbalance amount that can be removed by the balancing weight ring, which can greatly increase the success rate of the part's dynamic balancing in one time, and the dynamic balance of the part can be ultimately controlled within 10g.mm with extremely high precision. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] Figure 1 This is a cross-sectional schematic diagram of a thin-walled, slender shaft component according to Example 1 of the present invention undergoing a dynamic balancing test;

[0025] Figure 2 for Figure 1 A magnified view of the structure of the middle balance weight ring assembly;

[0026] Figure 3 This is a schematic structural diagram of the balancing weight ring according to Example 1 of the present invention;

[0027] Figure 4 This is a schematic diagram of the dynamic balancing removal of the balancing weight ring according to Example 2 of the present invention;

[0028] Figure 5 This is a structural front view of the combined tooling according to Example 3 of the present invention;

[0029] Figure 6 This is a right side view of the structure of the combined tooling described in Example 3 of the present invention. DETAILED DESCRIPTION

[0030] In order to clearly illustrate the technical features of this solution, the technical solution is described in detail below through specific implementation methods and in conjunction with the accompanying drawings.

[0031] In the following description, many specific details are set forth to facilitate a full understanding of the present application. However, the present application may also be implemented in other ways different from those described herein. Therefore, the scope of protection of the present application is not limited to the specific embodiments disclosed below.

[0032] In addition, in the description of the present application, it should be understood that the terms "center", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "axial", "radial", "circumferential" and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present application. In addition, the terms "first" and "second" are used for descriptive purposes only, and cannot be understood as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Therefore, features defined as "first" and "second" may explicitly or implicitly include one or more of such features. In the description of the present application, "multiple" means two or more, unless otherwise clearly and specifically defined.

[0033] In this application, unless otherwise expressly specified or limited, terms such as "installed," "connected," "connect," and "fixed" should be understood in a broad sense. For example, they may refer to fixed connection, detachable connection, or integration; mechanical connection, electrical connection, or communication; direct connection or indirect connection through an intermediate medium; and internal communication between two components or interaction between two components. Those skilled in the art will understand the specific meanings of the above terms in this application based on specific circumstances.

[0034] In this application, unless otherwise expressly specified and limited, a first feature "above" or "below" a second feature may be that the first and second features are in direct contact, or the first and second features are in indirect contact through an intermediate medium. In the description of this specification, the description with reference to the terms "one embodiment", "some embodiments", "example", "specific example", or "some examples" means that the specific features, structures, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the present application. In this specification, the schematic representation of the above terms does not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described may be combined in an appropriate manner in any one or more embodiments or examples.

[0035] Example 1

[0036] A method for dynamic balancing of thin-walled, slender shaft parts, using a balancing weight ring 2 to meet the dynamic balancing requirements of a part 1 (i.e., a thin-walled, slender shaft part), specifically comprising the following steps:

[0037] S1. After performing a dynamic balancing test on part 1 and determining the weight and imbalance, the required length and direction of the balancing weight ring 2 are determined.

[0038] S2. Remove the balancing weight ring 2 as required; based on the structural characteristics of the part and the assembly and use characteristics, drill two symmetrical balancing weight ring assembly holes on the outer surface of the part that do not affect the assembly and the rigidity of the part, with a hole diameter of approximately 2 to 3 mm;

[0039] S3. Place the balancing weight ring 2 into the balancing weight ring assembly hole in the inner hole of the part to perform dynamic balancing.

[0040] Among them, such as Figure 3 As shown, the balancing weight ring 2 is cylindrical, with a through hole 21 symmetrically provided at the first end thereof for connection with the component 1, and an even number of grooves 22 uniformly provided on the end surface of the second end thereof, the grooves extending along the length of the balancing weight ring. The fan-shaped structure 23 formed between adjacent grooves 22 is a portion for removing material according to the imbalance of the component. The first end of the balancing weight ring is symmetrically provided with slots 24 on both sides of the through hole 21. The slots 24 are used for assembling the balancing weight ring 2 to the inner hole of the component 1 using a combined tool (this combined tool will be mentioned in Example 3). In this embodiment, there are four grooves 22 on the balancing weight ring, that is, four fan-shaped structures 23 are evenly distributed on the balancing weight ring for removing material according to the dynamic balancing requirements.

[0041] like Figure 1 and Figure 2 As shown, the inner diameter of the balancing weight ring 2 on part 1 is less than or equal to the inner diameter of the part end, ensuring that the balancing weight ring 2 can be inserted through the inner hole from one end of part 1. The clearance between the balancing weight ring and the inner hole of the part at the assembly point is 0 to 0.016mm. The inner hole length of the part where the balancing weight ring is assembled must be greater than or equal to 10mm.

[0042] In addition, this dynamic balancing method also makes the following provisions for the balancing weight ring 2: the length of the removed material of the balancing weight ring must be greater than or equal to 80% of the total length of the balancing weight ring; the total length of the balancing weight ring is 6% to 8% of the total length of the part; the wall thickness of the removed material of the balancing weight ring is 2.5 to 3.5 mm; the wall thickness difference of the removed material of the balancing weight ring must be less than or equal to 0.05 mm (which can be appropriately relaxed to 0.1 mm according to the nature of the industry), and there is no requirement for the material of the balancing weight ring, as long as it meets the basic usage requirements; the arc length of each groove on the balancing weight ring is 20% of the diameter of the balancing weight ring

[0043] See also Figure 1 and Figure 2 ( Figure 1The dimension markings are only used as examples of the parts in Example 4 and do not constitute a limitation on the size of the parts. The assembly hole of the balancing weight ring on part 1 is a countersunk hole with a cone apex angle of 100° and a large head diameter generally not exceeding 6.5mm. The countersunk hole and the through hole 21 on the balancing weight ring are assembled by a blind rivet 3. The conical surface of the blind rivet 3 should fit closely with the conical surface of the countersunk hole. The blind rivet and the countersunk hole have a transition fit with a transition fit accuracy of (-0.004) to 0.012mm. The blind rivet 3 has a clearance fit with the through hole 21 with a clearance fit accuracy of 0 to 0.016mm. The structure of the blind rivet is a common countersunk solid rivet.

[0044] It should be noted that if the dynamic balance in step S3 still fails, use a drill to drill through the blind rivet 3 and remove the blind rivet, remove the balancing weight ring 2, and repeat S1 to S3 until the dynamic balance meets the requirements. The operation of removing the blind rivet is to use an ordinary electric drill to select the corresponding drill bit according to the diameter of the blind rivet, drill through the blind rivet, and then use an ordinary punch to knock out the blind rivet. The balancing weight ring can then be removed.

[0045] Example 2

[0046] This embodiment illustrates the removal of the balancing weight ring. For the time being, the assembly holes of the balancing weight ring on the part are not drilled based on the direction of the dynamic balancing focus of the part. The balancing weight ring is evenly distributed to four quadrants. The balancing weight angle α and the balancing weight quadrant are determined according to the angle between the dynamic balancing focus of the part and the assembly hole. The quadrant symmetrically distributed with the balancing weight quadrant is the removal quadrant.

[0047] When the counterweight quadrant is located in a single quadrant, for example in the first quadrant, that is, the counterweight angle α = 45°, then the material removal quadrant is the third quadrant, and the material removal amount in the third quadrant is

[0048] When the counterweight quadrants are located in two adjacent quadrants, such as Figure 4 As shown, assuming that the counterweight is in the first and second quadrants, the removal amount (i.e., the removal length) in the third and fourth quadrants is:

[0049]

[0050] Where M is the dynamic unbalance (g), D is the outer radius of the balance weight ring where the parts are assembled (mm), and ρ is the coefficient. Among them D 平衡块 is the outer diameter of the balance weight ring, S 平衡块 is the area of the multiple fan-shaped structures of the balance weight ring, H 平衡块 is the thickness of the balance weight ring at the counterweight, ρ 平衡块 is the density of the balance weight ring (g / cm 3), K is the number of weights in the balance weight ring, and after calculation, ρ=4.083.

[0051] In Example 1, the assembly hole of the balancing weight ring on the part is drilled according to the dynamic balancing focus, that is, the assembly hole is located in the direction of the dynamic balancing focus of the part, so the balancing weight angle α is 0°. At this time, the balancing weight quadrants are the first and second quadrants, the material removal quadrants are the third and fourth quadrants, and the material removal amount of the balancing weight ring is

[0052] Example 3

[0053] This embodiment provides a combined tooling for assembling the balancing weight ring to the inner hole of a part in embodiment 1, such as Figure 5 and Figure 6 As shown, the combined tooling includes a handle 41, a limit step 42, a stop 43, a support rod 44 and a sector tooth end 45 arranged in sequence, and a slot 24 (see Figure 3 ) cooperates with the fan-shaped tooth end 45 of the combined tooling, and the fan-shaped tooth end can be extended from the first end portion of the balancing weight ring. Two fan-shaped teeth 451 are evenly arranged on the outer periphery of the fan-shaped tooth end 45. The thickness of the fan-shaped teeth 451 is adapted to the width of the slot 24. After the fan-shaped tooth end 45 is extended into the balancing weight ring 2, the fan-shaped teeth 451 can be rotated to be clamped into the balancing weight ring slot 24 to limit the balancing weight ring.

[0054] The sector tooth end 45, support rod 44, and stop 43 of the assembly fixture can be extended into the inner hole of part 1 until the end surface of the stop step 42 contacts the end surface of part 1. The distance from the end surface of the sector tooth 451 closest to the support rod 44 to the end surface of the stop step 42 of the assembly fixture is equal to the distance from the through hole 21 of the component balance weight ring to the end surface of part 1.

[0055] The process of assembling the balancing weight ring with the combined tooling is as follows: two V-shaped blocks are placed at both ends of the part, the balancing weight ring 2 is fixed to the fan-shaped tooth end 45 of the combined tooling (the slot and the fan-shaped tooth match), the combined tooling together with the balancing weight ring 2 is inserted into the inner hole of the large end of the part 1, the combined tooling is rotated axially, and the through hole 21 of the balancing weight ring is aligned with the assembly hole of the balancing weight ring on the part by visual inspection. Then the blind rivet 3 is inserted into the rivet fixture (a common fixture used for pulling the core of the blind rivet), ensuring that the blind rivet 3 fits with the end face of the rivet fixture, the rivet fixture is held in hand, and the blind rivet 3 is aligned with the assembly hole and inserted so that the conical surface of the blind rivet 3 fits with the chamfer of the conical surface of the assembly hole, and then the handle of the rivet fixture is pressed inward with both hands to pull out the core of the blind rivet 3. After the core is pulled, the rivet naturally expands and tightens in the assembly hole and the through hole 21, and then the combined tooling can be taken out.

[0056] Example 4

[0057] Provide a specific example of dynamic balancing of thin-walled slender shafts: Figure 1 The total length of the part is approximately 1.6m. The diameter of the part at the balancing weight ring assembly is Φ65.2±0.1mm, and the assembly hole is 784.5mm from the end face of the part. The balancing weight ring is approximately 120mm long, and the removable portion is a symmetrical fan-shaped structure with a wall thickness of approximately 3mm. The removable length is approximately 100mm, and the through-hole diameter is Φ2.5(+0.1,0).

[0058] After the part is dynamically balanced, the position of the balancing weight ring assembly hole is kept consistent with the key direction of dynamic balancing. After the balancing weight ring is removed, the balancing weight ring is installed into the inner hole of the part through the combined tooling of Example 3, thereby ensuring that the dynamic balance of the part is qualified. In this embodiment, the maximum imbalance that can be removed by the balancing weight ring is about 67.6g.

[0059] Obviously, the above embodiments are merely examples for the purpose of clearly illustrating the technical solutions of the present invention, and are not intended to limit the implementation methods of the present invention. Those skilled in the art will appreciate that other variations or modifications can be made based on the above description. It is not necessary and impossible to enumerate all implementation methods here. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present invention shall be included within the scope of protection of the claims of the present invention.

Claims

1. A balancing weight ring for dynamic balancing of thin-walled slender shaft parts, characterized in that: The thin-walled, slender shaft is provided with an assembly hole for assembling a balancing weight ring. The balancing weight ring is cylindrical, with a through hole corresponding to the assembly hole symmetrically provided at the first end of the balancing weight ring, and an even number of grooves uniformly provided on the end surface of the second end. The grooves extend along the length of the balancing weight ring, and the fan-shaped structure formed between adjacent grooves is a material removal portion based on the imbalance of the part. Evenly distribute the balancing weight rings to four quadrants. Determine the balancing angle α and the balancing weight quadrant according to the angle between the dynamic balancing point of the part and the assembly hole. The quadrant symmetrically distributed with the balancing weight quadrant is the material removal quadrant. When the counterweight quadrant is located in a single quadrant, the removal amount of the removal quadrant is When the counterweight quadrants are located in two adjacent quadrants, the removal amounts of the two removal quadrants are: Where M is the dynamic unbalance, D is the outer radius of the balancing weight ring where the parts are assembled, and ρ = 4.

083.

2. The balancing weight ring for dynamic balancing of thin-walled slender shaft parts according to claim 1, characterized in that: There are four grooves on the balance weight ring.

3. The balancing weight ring for dynamic balancing of thin-walled slender shaft parts according to claim 1, characterized in that: The clearance between the balancing weight ring and the inner hole of the part is 0~0.016mm.

4. The balancing weight ring for dynamic balancing of thin-walled slender shaft parts according to claim 1, characterized in that: The length of the removed portion of the balancing weight ring is greater than or equal to 80% of the total length of the balancing weight ring.

5. The balancing weight ring for dynamic balancing of thin-walled slender shaft parts according to claim 1, characterized in that: The total length of the balancing weight ring is 6% to 8% of the parts assembly.

6. The balancing weight ring for dynamic balancing of thin-walled slender shaft parts according to claim 1, characterized in that: The wall thickness of the removed material part of the balancing weight ring is 2.5 to 3.5 mm.

7. The balancing weight ring for dynamic balancing of thin-walled slender shaft parts according to claim 6, characterized in that: The wall thickness difference of the removed part of the balancing weight ring is less than or equal to 0.05mm.

8. The balancing weight ring for dynamic balancing of thin-walled slender shaft parts according to claim 1, characterized in that: The arc length of each groove on the balancing weight ring is 20% of the diameter of the balancing weight ring.

9. The balancing weight ring for dynamic balancing of thin-walled slender shaft parts according to claim 1, characterized in that: Blind rivets are installed in the assembly holes of the parts and the through holes of the balancing weight ring, and the blind rivets are clearance-matched with the through holes.

10. The balancing weight ring for dynamic balancing of thin-walled slender shaft parts according to claim 9, characterized in that: The clearance fit accuracy is 0 to 0.016 mm.

Images