T-shaped blade root blade collision damping device

Abstract

The invention relates to the field of rotating wheel discs, in particular to a T-shaped blade root blade collision damping device. Comprising a vibration assembly which is a blade with a T-shaped blade root structure; the supporting assembly is connected with the vibration assembly, and a non-bearing surface area is arranged on the supporting assembly; the damping groove is formed in the non-bearing surface area, a damping structure is arranged in the damping groove, energy dissipation can be achieved, and when the blade vibrates, the damping structure freely moves in the damping groove, and vibration energy is dissipated through mutual collision; the damping grooves are formed in the non-bearing surface areas of the T-shaped grooves of the wheel disc, the damping structures can freely move in the damping grooves and collide with one another, vibration kinetic energy is dissipated, and blade vibration can be remarkably reduced.

Description

Technical Field

[0001] This invention relates to the field of rotating disks, and more specifically to a T-shaped blade root collision damping device. Background Technology

[0002] In existing rotating machinery disks, blades, as one of the key components, face a complex mechanical environment. In particular, T-shaped root blades are prone to vibration under high-load operating conditions. The T-shaped root blade design has the advantages of simple structure, convenient assembly, and clear radial force, and has been widely used in rotating machinery. However, this design has certain limitations in reducing blade vibration.

[0003] During operation, blades are subjected to the combined effects of airflow pressure, thermal stress, and centrifugal stress. Under varying operating conditions, they are also subject to alternating stress. These factors can all lead to blade vibration and even fatigue fracture, posing a serious threat to the safe operation of rotating machinery. Especially with the continuous development of modern rotating machinery technology, the increasing operating load places higher demands on blade reliability. Traditional methods such as increasing blade thickness and changing blade shape can alleviate vibration problems to some extent, but they also bring the side effects of increased manufacturing costs and weight. This not only affects the overall performance of rotating machinery but may also limit its further development and optimization possibilities.

[0004] In addition, vibration reduction measures for T-shaped blade root blades are usually quite complex. They either require significant modifications to the structure of the T-shaped blade root blade itself or the addition of damping devices in the flow channel of the T-shaped blade root blade. The former not only increases the design difficulty but may also disrupt the optimized balance of the original structure, while the latter may have an adverse effect on the flow field and reduce the efficiency of rotating machinery. Summary of the Invention

[0005] To address the problems mentioned in the prior art, this invention proposes a T-shaped blade root collision damping device, which dissipates the vibration energy of the blade through the collision between the damping structures. It has the advantages of simple structure and convenient processing, and can effectively reduce blade vibration and improve the safety of blade operation.

[0006] To achieve the above objectives, the present invention adopts the following technical solution: This invention proposes a T-shaped blade root-blade collision damping device, comprising: A vibration assembly, wherein the vibration assembly is a blade with a T-shaped blade root structure; A support assembly, which is connected to a vibration assembly, has a non-load-bearing surface area on the support assembly; The damping groove is located in the non-load-bearing area. A damping structure is placed in the damping groove to dissipate energy. When the blade vibrates, the damping structure moves freely in the damping groove and dissipates vibration energy through mutual collision.

[0007] As a further improvement of the present invention, the damping structure is a damping sphere, and the damping sphere is a spherical structure.

[0008] As a further improvement of the present invention, the damping groove is provided with at least two damping balls, and adjacent damping balls can collide with each other to dissipate vibration energy.

[0009] As a further improvement of the present invention, the gap between the damping ball and the sidewall of the damping groove is 2mm to 5mm.

[0010] As a further improvement of the present invention, the gap between adjacent damping balls is 2mm to 5mm.

[0011] As a further improvement of the present invention, the diameter of the damping ball is 10mm to 20mm, and the damping ball is made of stainless steel.

[0012] As a further improvement of the present invention, the length of the damping groove is 100mm to 200mm and the depth is 30mm to 40mm.

[0013] As a further improvement of the present invention, the non-load-bearing surface region includes: The support component is a wheel, and the wheel is provided with a T-shaped groove that matches the T-shaped blade root structure; The upper shoulder of the T-slot is a non-load-bearing surface area.

[0014] As a further improvement of the present invention, there is a gap between the non-load-bearing surface area and the blade.

[0015] As a further improvement of the present invention, the gap between the non-load-bearing surface area and the blade is 0.5 mm to 1 mm.

[0016] Compared with the prior art, the present invention achieves the following technical effects: This invention arranges the damping groove in the non-load-bearing surface area of ​​the T-groove of the wheel disc, without modifying the blade body structure or encroaching on the flow channel. This completely avoids the problems of mechanical balance disruption or aerodynamic efficiency reduction caused by structural modifications in traditional technologies. In addition, when the blade vibrates, the damping structure can move freely and collide with each other within the damping groove, dissipating the vibration kinetic energy. This can significantly reduce blade vibration, which is beneficial to extending the service life of the blade and reducing equipment downtime maintenance costs and potential safety hazards caused by blade damage. This invention, through its designed damping structure, enables blades to effectively absorb and dissipate vibration energy during operation, thereby reducing vibration intensity. Simultaneously, the invention has minimal impact on the blade flow field and does not alter the original aerodynamic performance, ensuring that the blade's efficiency remains unaffected after the damping is increased. This makes it easy to improve existing blade designs without requiring large-scale adjustments to the overall blade structure; local optimization at key locations is sufficient to achieve vibration reduction, significantly shortening the development cycle and lowering development costs. Attached Figure Description

[0017] Figure 1 This is a schematic diagram of the overall assembly structure of the present invention; Figure 2 This is a schematic diagram of the assembly of the damping ball and the wheel of the present invention; Figure 3 This is a schematic diagram of the damping groove structure of the present invention; Figure 4 This is an assembly cross-sectional view of the present invention.

[0018] Reference numerals: 1. Blade; 2. Disc; 3. Damping groove; 4. Blade body; 5. T-shaped blade root; 6. Damping ball. Detailed Implementation In the following description, only certain exemplary embodiments are briefly described. As those skilled in the art will recognize, the described embodiments can be modified in various ways without departing from the spirit or scope of the invention. Therefore, the drawings and description are considered to be exemplary in nature and not restrictive.

[0019] 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.

[0020] 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 indicated technical features. 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.

[0021] 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.

[0022] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can include direct contact between the first and second features, or contact between the first and second features through another feature between them. Furthermore, "above," "over," and "on top" of the second feature includes the first feature being directly above or diagonally above the second feature, or simply indicates that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature includes the first feature being directly above or diagonally above the second feature, or simply indicates that the first feature is at a lower horizontal level than the second feature.

[0023] 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.

[0024] 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.

[0025] 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.

[0026] The accompanying drawings illustrate various structural schematic diagrams according to embodiments disclosed in this invention. These drawings are not to scale, and some details have been enlarged for clarity, and some details may have been omitted. The shapes of the various regions and layers shown in the drawings, as well as their relative sizes and positional relationships, are merely exemplary and may deviate from reality due to manufacturing tolerances or technical limitations. Furthermore, those skilled in the art can design regions / layers with different shapes, sizes, and relative positions as needed.

[0027] See Figure 1 This invention proposes a T-shaped blade root-blade collision damping device, comprising: Vibration assembly, wherein the vibration assembly is a blade 1 having a T-shaped blade root 5 structure; A support assembly, which is connected to a vibration assembly, has a non-load-bearing surface area on the support assembly; The damping groove 3 is located in the non-load-bearing surface area. The damping structure placed in the damping groove 3 can dissipate energy. When the blade 1 vibrates, the damping structure moves freely in the damping groove 3 and dissipates vibration energy through mutual collision.

[0028] The embodiments of the present invention will now be described in detail with reference to the accompanying drawings.

[0029] join Figure 1 The blade 1 of the present invention is composed of a blade body 4 and a blade root, wherein the blade root is a T-shaped blade root 5. The wheel 2 is provided with a T-shaped groove corresponding to the T-shaped blade root 5, wherein the T-shaped groove is connected to the T-shaped blade root 5. The blade body 4 is embedded in the T-shaped groove of the wheel 2 through the T-shaped blade root 5 to form a rigid connection, which ensures that the blade 1 can stably transmit power during high-speed rotation.

[0030] See Figure 2 or Figure 3 In this embodiment, the T-slot is an inverted T-shape. When the T-shaped blade root 5 is embedded in the T-slot, the T-shaped blade root 5 will contact the lower groove wall of the T-slot. The lower groove wall, as the main bearing surface, bears the main centrifugal load generated when the blade 1 rotates, ensuring the reliability of the connection between the blade 1 and the wheel 2. The upper groove shoulder areas at both ends of the T-slot are non-bearing surface areas. Specifically, the upper groove shoulder areas maintain a gap of 0.5mm to 1mm with the flange surface of the T-shaped blade root 5. This gap ensures that the blade 1 will not make hard contact with the wheel 2 when vibrating, avoiding additional stress and noise caused by hard collision, and at the same time providing space for the subsequent damping structure.

[0031] See Figure 3In this embodiment, the damping groove 3 is directly set in the non-load-bearing surface area of ​​the T-groove of the wheel disk 2. Specifically, the damping groove 3 extends along the length direction of the upper groove shoulder area. The length of the damping groove 3 is 100mm to 200mm and the depth is 30mm to 40mm. In this embodiment, the length is preferably 100mm and the depth is 30mm. The damping groove 3 with this size limitation can completely avoid the main load-bearing path of the blade 1, thereby avoiding weakening the structural strength of the wheel disk 2. If the damping groove 3 is set on the main load-bearing path, it will have an adverse effect on the stress distribution of the wheel disk 2 and reduce the load-bearing capacity of the wheel disk 2. However, in this embodiment, the damping groove 3 is set in the non-load-bearing surface area, and the damping effect is achieved without affecting the overall strength of the wheel disk 2.

[0032] See Figure 2 or Figure 4 In this embodiment, two or more damping balls 6 are placed in the damping groove 3. This embodiment uses three damping balls 6, but the actual number is not limited to this. The number of damping balls 6 can be appropriately increased according to different usage scenarios, such as the operating speed and vibration frequency of the blade 1. In this embodiment, the damping balls 6 are preferably made of stainless steel, which has the characteristics of high density and high hardness. High density provides sufficient inertial force, enabling the damping balls 6 to have good motion response during vibration; high hardness ensures that the damping balls 6 will not undergo plastic deformation under long-term impact, guaranteeing the long-term stability and reliability of the damping structure.

[0033] In this embodiment, the diameter of the damping ball 6 is 10mm to 20mm, preferably 10mm; the gap between the damping ball 6 and the inner wall of the damping groove 3 is controlled to be 2mm to 5mm, preferably 2mm; the gap between adjacent balls is also 2mm to 5mm, preferably 2mm. The above-defined gap range has been experimentally verified. This range not only ensures that the damping ball 6 can roll freely within the damping groove 3, allowing it to fully respond to the vibration of the blade 1, but also limits its displacement amplitude, ensuring collision efficiency. If the gap is too large, the damping ball 6 may experience excessive displacement during vibration, resulting in insufficient collision and reduced damping effect. If the gap is too small, it will restrict the free rolling of the damping ball 6, or even prevent it from moving, thus failing to achieve the ideal damping effect. Therefore, the above-described gap limitation ensures the achievement of the ideal damping effect.

[0034] After the device is installed, when the blade 1 vibrates due to the airflow, the vibration energy generated will be transmitted to the wheel disk 2 through the blade root. Since the blade root and the T-slot of the wheel disk 2 are rigidly connected, the vibration energy of the blade 1 can be transmitted to the non-load-bearing surface area on the wheel disk 2.

[0035] The vibrational energy transmitted to the wheel 2 causes the damping balls 6 in the damping groove 3 to begin moving under inertia, resulting in three-dimensional inelastic collisions between the damping balls 6 and the groove wall, and between adjacent damping balls 6. Through the collision process, kinetic energy can be dissipated and converted into other forms of energy, thereby significantly reducing the amplitude of the blade 1. This three-dimensional inelastic collision can absorb and dissipate vibrational energy from multiple directions, and has a better damping effect than a collision in a single direction.

[0036] The embodiment, through the aforementioned gap design, enables the damping balls 6 to collide with each other at high frequency within the damping groove 3. This high-frequency collision synchronizes the collision frequency of the damping balls 6 with the vibration frequency of the blade 1, thereby improving the efficiency of kinetic energy dissipation. When the collision frequency matches the vibration frequency, vibration energy absorption is maximized, achieving a better damping effect. Furthermore, since the damping groove 3 is located in the non-load-bearing area of ​​the wheel disc 2, the damping balls 6 do not contact the blade 1, thus completely avoiding aerodynamic interference. Compared to traditional methods that use drilling or external dampers on the blade body 4, which disrupt the aerodynamic profile of the blade 1, affecting airflow and reducing engine performance, this device does not disrupt the aerodynamic profile, ensuring that the aerodynamic performance of the blade 1 remains unaffected.

[0037] When the blade 1 is stationary, the damping ball 6 is naturally positioned at the bottom of the damping groove 3. The damping ball 6 does not contact the blade 1, and the gap between them is 0.5mm to 1mm. This gap can prevent friction when the blade 1 starts, reduce starting energy consumption, and also help protect the surface of the damping ball 6 and the blade 1, thus extending their service life.

[0038] When blade 1 starts running, its amplitude begins to increase. The damping ball 6, excited by acceleration, begins to roll and collides with the inner wall of the damping groove 3. This collision process dissipates the vibration energy of blade 1, effectively suppressing further increases in amplitude and allowing blade 1 to quickly enter a stable operating state. When blade 1 is in stable operation, airflow excitation causes high-frequency micro-amplitude vibrations. At this time, the vibration energy can be dissipated through continuous collisions between the damping balls 6. The gap design between adjacent damping balls 6 allows multiple damping balls 6 to form a collision chain, enabling the vibration energy to be transferred and diffused between them, further improving the damping effect and ensuring that the vibration amplitude of blade 1 remains at a low level during stable operation.

[0039] When routine maintenance is required, blade 1 and wheel 2 can be disassembled, and maintenance personnel can directly replenish or replace damping balls 6 from the damping groove 3. When replenishing or replacing damping balls 6, it is necessary to check whether the size and material of damping balls 6 meet the requirements, and ensure that the gap between damping balls 6 and the inner wall of damping groove 3 and between adjacent damping balls 6 is within the specified range. At the same time, it is also necessary to clean damping groove 3 to remove any possible impurities and dirt, and ensure that damping balls 6 can roll freely in damping groove 3. Through regular routine maintenance, the performance of the damping structure can be kept at its best, extending the overall service life of blade 1 device and ensuring the safe and stable operation of the equipment.

[0040] This embodiment provides a specific implementation method in which a damping device is installed on the blades of a gas turbine compressor. The gas turbine compressor has 84 blades, corresponding to 84 discs. The damping grooves on the discs are 150mm long and 35mm deep. Each damping groove contains 3 damping balls with a diameter of 15mm and a gap of 3mm between adjacent damping balls. At the rated speed, the blade amplitude is significantly reduced. Therefore, this device achieves a significant effect in reducing vibration amplitude.

[0041] The damping device in this embodiment, with its connection between the T-shaped blade root and the T-slot, and the arrangement of the damping groove and damping ball, effectively controls blade vibration. Its working principle is based on vibration energy transfer and energy dissipation through damping ball collisions, exhibiting good damping effects under various operating conditions. Simultaneously, the convenient daily maintenance scheme reduces equipment maintenance costs and operational risks. This device has broad application prospects in fields such as aero-engines and gas turbines. The foregoing has shown and described the basic principles, main features, and advantages of the present invention. It will be apparent to those skilled in the art that the invention is not limited to the details of the exemplary embodiments described above, and that the invention can be implemented in other specific forms without departing from its spirit or essential characteristics. Therefore, the embodiments should be considered illustrative and non-limiting in all respects, and the scope of the invention is defined by the appended claims rather than the foregoing description. Thus, all variations falling within the meaning and scope of equivalents of the claims are intended to be included within the scope of the invention. No reference numerals in the claims should be construed as limiting the scope of the claims.

[0042] Furthermore, it should be understood that although this specification describes embodiments, not every embodiment contains only one independent technical solution. This narrative style is merely for clarity. Those skilled in the art should consider the specification as a whole, and the technical solutions in each embodiment can be appropriately combined to form other embodiments that can be understood by those skilled in the art. The above content is only for illustrating the technical concept of the present invention and should not be construed as limiting the scope of protection of the present invention. Any modifications made based on the technical concept proposed in this invention shall fall within the scope of protection of the claims of this invention.

Claims

1. A T-shaped blade root-blade collision damping device, characterized in that, include: A vibration assembly, wherein the vibration assembly is a blade with a T-shaped blade root structure; A support assembly, which is connected to a vibration assembly, has a non-load-bearing surface area on the support assembly; The damping groove is located in the non-load-bearing area. A damping structure is placed in the damping groove to dissipate energy. When the blade vibrates, the damping structure moves freely in the damping groove and dissipates vibration energy through mutual collision.

2. The T-shaped blade root-blade collision damping device according to claim 1, characterized in that, The damping structure is a damping sphere, which is a spherical structure.

3. The T-shaped blade root collision damping device according to claim 2, characterized in that, The damping groove is provided with at least two damping balls, and adjacent damping balls can collide with each other to dissipate vibration energy.

4. A T-shaped blade root-blade collision damping device according to any one of claims 1 to 3, characterized in that, The gap between the damping ball and the sidewall of the damping groove is 2mm to 5mm.

5. The T-shaped blade root-blade collision damping device according to claim 1, characterized in that, The gap between adjacent damping balls is 2mm to 5mm.

6. The T-shaped blade root-blade collision damping device according to claim 1, characterized in that, The diameter of the damping ball is 10mm to 20mm, and the damping ball is made of stainless steel.

7. The T-shaped blade root-blade collision damping device according to claim 1, characterized in that, The damping groove has a length of 100mm to 200mm and a depth of 30mm to 40mm.

8. The T-shaped blade root-blade collision damping device according to claim 1, characterized in that, The non-load-bearing surface area includes: The support component is a wheel, and the wheel is provided with a T-shaped groove that matches the T-shaped blade root structure; The upper shoulder of the T-slot is a non-load-bearing surface area.

9. The T-shaped blade root-blade collision damping device according to claim 8, characterized in that, There is a gap between the non-load-bearing surface area and the blade.

10. The T-shaped blade root collision damping device according to claim 9, characterized in that, The gap between the non-load-bearing surface area and the blade is 0.5mm to 1mm.

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