Impeller high-temperature over-rotation test device

Abstract

The invention provides an impeller high-temperature over-rotation test device. The impeller high-temperature over-rotation test device comprises a long shaft, an impeller, a press-fitting assembly, a buffer assembly and a fixing piece. The long shaft comprises a first shaft body and a second shaft body which are concentric and different in diameter, the impeller is sleeved on the first shaft body, and press-fitting parts are formed at two ends. The first press-fitting assembly and the second press-fitting assembly are pressed on the press-fitting parts on the two sides of the impeller correspondingly, relative rotation is prevented through the rectangular keys, the double press-fitting assemblies are symmetrically arranged to balance axial force, and rotation stability is improved. The left / right clamping sleeve is matched with the conical surface of the left / right taper sleeve, and a tensioning wire groove is formed to adapt to impellers of different sizes and compensate size changes. The buffering assemblies are arranged in a mirror symmetry mode, the horn mouth design optimizes stress distribution, long-axis thermal expansion is absorbed, and vibration impact is resisted. The fixing piece provides axial fixing force, and the axial rigidity of the system is optimized. The device can ensure the reliable positioning of the impeller at high temperature and ultrahigh speed, and improves the test precision and reliability.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of impellers, and particularly relates to an impeller high-temperature super-rotation test device. BACKGROUND

[0002] As a key hot-end component, the turbine of a gas turbine works in a high-temperature and high-pressure gas environment and needs to withstand extremely high rotation speed and load. The design working rotation speed range of the turbine is 80000 revolutions per minute to 90000 revolutions per minute, and the use temperature is as high as 700 DEG C to 800 DEG C. Under such extreme working conditions, the material performance, structural strength and thermal stability of the turbine are all severely tested. In order to ensure the reliability and safety of the gas turbine in long-term operation, the high-temperature super-rotation performance test of the turbine must be carried out to verify whether the various performance indexes of the turbine under the design working conditions meet the requirements.

[0003] However, the existing turbine test device has many technical problems in the high-temperature super-rotation test.

[0004] Firstly, due to the difference in materials between the turbine and the rotating shaft, the thermal deformation amounts of the two are inconsistent under the high-temperature environment due to the difference in thermal expansion coefficients, which easily causes positioning failure of the turbine and even causes damage to the equipment.

[0005] Secondly, under the combined action of high-speed rotation and high temperature, the traditional test device is prone to thermal stress concentration, which causes thermal deformation of the turbine or the rotating shaft and affects the accuracy of the test data.

[0006] In addition, the existing device is difficult to maintain the stability of the axial pressing force under high temperature, which causes the turbine to move axially during rotation, affecting the safety and reliability of the test.

[0007] More importantly, there is a lack of effective thermal expansion compensation mechanism in the prior art, which cannot automatically adapt to the size change of the turbine and the rotating shaft under high temperature, so that it is difficult to maintain the accurate coaxial positioning of the turbine under extreme working conditions. This not only limits the test capacity of the test device, but also increases the risk of the turbine of the gas turbine in actual application.

[0008] Therefore, it has become a key problem to be solved in the current gas turbine technology research and development to develop a test device capable of stably and reliably fixing the turbine under high-temperature super-rotation conditions. SUMMARY

[0009] Based on this, it is necessary to solve the technical problems that the existing impeller high-temperature super-rotation test device is difficult to ensure the stable positioning of the impeller under high-temperature and super-high-speed rotation conditions, is easy to be affected by thermal expansion to cause positioning failure, and cannot accurately simulate the actual working environment of the gas turbine, and provide an impeller high-temperature super-rotation test device, so that the impeller can be reliably positioned under super-high-temperature (more than 700 DEG C) and super-high-speed (80000-90000 revolutions / minute) conditions, and the axial deformation caused by thermal expansion can be effectively compensated, the long-term stable operation of the test device can be ensured, and the test precision and reliability can be improved.

[0010] The present application provides an impeller high-temperature super-rotation test device, which comprises a long shaft, an impeller, a press-fitting assembly, a buffer assembly and a fixing piece. The long shaft comprises a first shaft body and a second shaft body which are concentrically arranged and have different diameters, and the diameter of the first shaft body is smaller than that of the second shaft body. The impeller is sleeved on the first shaft body of the long shaft, and the two ends of the inner ring of the impeller extend outward in the axial direction and form press-fitting parts. The first press-fitting assembly is sleeved on the first shaft body between the impeller and the long shaft, and is press-fitted on one of the press-fitting parts of the impeller. A plurality of rectangular keys distributed in a ring shape are inserted into the end surface of the first press-fitting assembly, and the two ends of the rectangular keys are respectively inserted into the second shaft body of the long shaft and the side wall of the impeller. The second press-fitting assembly is sleeved on the first shaft body on the other side of the impeller, and is press-fitted on the other press-fitting part of the impeller. The device provides high-strength support through the double-diameter structure of the long shaft, and realizes torque transmission and axial positioning through the precise fit of the press-fitting assembly and the impeller. The design of the rectangular keys effectively prevents the relative rotation of the impeller and the long shaft, ensures synchronous rotation, and balances the axial force through the symmetrical layout of the double press-fitting assemblies, reduces the deformation and stress concentration caused by unilateral stress, and improves the rotation stability and test precision of the impeller.

[0011] In other embodiments, the first press-fit assembly includes a left clamp sleeve and a left taper sleeve, the left clamp sleeve has a second supporting plate sleeved on the first shaft body and a second annular retaining edge circumferentially arranged on the second supporting plate, the second annular retaining edge is press-fitted on the press-fit part of the corresponding side of the impeller, and the second annular retaining edge is close to the end face of the corresponding side of the impeller; the left taper sleeve has a first supporting plate sleeved on the first shaft body and a first annular retaining edge circumferentially arranged on the first supporting plate, the first annular retaining edge is sleeved on the second annular retaining edge, and the first annular retaining edge is provided with a first gap h1 to the end face of the impeller, and satisfies: 1mm≤h1≤2mm; the end faces of the first supporting plate and the second supporting plate are both provided with key holes corresponding to the rectangular keys. The cooperation design of the left clamp sleeve and the left taper sleeve realizes self-locking and elastic compensation functions through the taper surface, the first gap h1 provides necessary buffer space for high-temperature expansion and mechanical deformation, prevents the assembly from being stuck or damaged due to thermal stress, and at the same time, the design of the key holes ensures the accurate installation of the rectangular keys, realizes the reliable transmission of the torque, and prevents the relative rotation between the assemblies. This accurate mechanical connection method has higher positioning accuracy and reliability than the traditional key connection, can effectively reduce vibration and noise, and improve the overall performance of the system.

[0012] In other embodiments, the inner wall of the first annular retaining edge is tapered, and the radial thickness of the side of the first annular retaining edge away from the first supporting plate is smaller than the radial thickness of the side of the first annular retaining edge close to the first supporting plate; the outer wall of the second annular retaining edge is tapered corresponding to the inner wall of the first annular retaining edge. This corresponding taper design ensures that the left taper sleeve and the left clamp sleeve can form a perfect taper surface cooperation, and when the axial force acts, the two can tightly fit, realize efficient torque transmission and accurate axial positioning, and at the same time, this design is also convenient for installation and disassembly, and the thickness design optimizes the stress distribution, makes the tensioning force more uniform, reduces the risk of deformation or damage caused by local stress concentration, and improves the service life and reliability of the assembly.

[0013] In other embodiments, a plurality of first tensioning wire grooves are circumferentially arranged on the side of the second annular retaining edge close to the impeller. Under the action of the axial force, these wire grooves can produce slight elastic deformation, so that the inner diameter of the second annular retaining edge changes, thereby realizing the clamping or loosening of the press-fit part of the impeller. This elastic tensioning mechanism not only can adapt to impellers of different sizes, but also can compensate for the size changes caused by thermal expansion or mechanical wear, ensuring long-term stable fixing effect, and at the same time, the design of the tensioning wire grooves can also improve the elastic modulus of the assembly, enhance the resistance to vibration and impact, and improve the overall reliability of the system.

[0014] In other embodiments, the second pressing assembly includes a right clamp sleeve and a right taper sleeve, the right clamp sleeve has a third supporting plate sleeved on the first shaft body, and a third annular guard edge circumferentially arranged on the third supporting plate, the third annular guard edge is pressed on the pressing part of the corresponding side of the impeller, and the third annular guard edge is close to the end surface of the corresponding side of the impeller; the right taper sleeve has a fourth supporting plate sleeved on the first shaft body, and a fourth annular guard edge circumferentially arranged on the fourth supporting plate, the fourth annular guard edge is sleeved on the third annular guard edge, and the fourth annular guard edge is provided with a second gap h2 to the end surface of the impeller, and satisfies: 1mm≤h2≤2mm. The design principle of the right clamp sleeve and the right taper sleeve is the same as that of the left clamp sleeve and the left taper sleeve, and the tightening function is realized through the taper cooperation, and the second gap h2 provides necessary buffer space for high-temperature expansion and mechanical deformation, prevents the assembly from being stuck or damaged due to thermal stress, and at the same time, the gap cooperation can also realize accurate axial positioning through axial force adjustment during installation, forms a symmetrical fixed structure with the left taper sleeve, and improves the overall stability of the system.

[0015] In other embodiments, the inner wall of the fourth annular guard edge is tapered, and the radial thickness of the side of the fourth annular guard edge away from the fourth supporting plate is less than the radial thickness of the side of the fourth annular guard edge close to the fourth supporting plate; the outer wall of the third annular guard edge is tapered corresponding to the inner wall of the fourth annular guard edge. The taper design makes the right taper sleeve able to shrink radially when subjected to axial force, thereby realizing the tightening effect of the right clamp sleeve, improving the fixing effect of the impeller, and ensuring that the right taper sleeve and the right clamp sleeve can form perfect taper surface cooperation, and when the axial force acts, the two can tightly fit, realize efficient torque transmission and accurate axial positioning, and at the same time, the design is also convenient for installation and disassembly, and forms a symmetrical layout with the taper surface cooperation structure on the left side, enhances the balance and stability of the system, and the variable thickness design optimizes the stress distribution, makes the tightening force more uniform, and reduces the risk of deformation or damage caused by local stress concentration.

[0016] In other embodiments, a plurality of second tensioning grooves are circumferentially arranged on the third supporting plate and the third annular retaining edge away from the impeller; a plurality of third tensioning grooves are circumferentially arranged on the third annular retaining edge close to the impeller; and the second tensioning grooves and the third tensioning grooves are staggered. The second tensioning grooves are similar to the first tensioning grooves, but the special layout on the right jacket can adapt to different stress conditions. Under the action of the axial force, these grooves can produce a slight elastic deformation, so that the inner diameter of the third annular retaining edge changes, thereby realizing the clamping or loosening of the impeller pressing part. The position and number of the third tensioning grooves can ensure that uniform tensioning force is generated under the action of the axial force, preventing impeller deformation or damage due to local stress concentration. Meanwhile, the multi-groove design can also improve the elastic modulus of the assembly and enhance the resistance to vibration and impact. The staggered distribution of the second tensioning grooves and the third tensioning grooves can compensate for each other through elastic deformation in different directions, reducing the dimensional deviation caused by deformation in a single direction. Meanwhile, this layout can also optimize the stress distribution, making the tensioning force more uniformly act on the impeller surface, improving the fixing effect and test accuracy.

[0017] In other embodiments, a ring groove is arranged on a section of the outer wall of the fourth annular retaining edge connected to the fourth supporting plate. The ring groove has the following functions: first, it can reduce the weight of the assembly, reduce the inertial force, and improve the dynamic response characteristics of the system; second, it can serve as a stress release area to reduce stress concentration caused by thermal expansion or mechanical load; and finally, it can also serve as a mounting and positioning mark to facilitate accurate assembly and debugging of the assembly. This multifunctional design reflects the ingenuity and practicality of engineering design, improving the overall performance and reliability of the assembly.

[0018] In other embodiments, a fixing member and a buffer assembly are further included. The fixing member is threadedly sleeved on the first shaft body, and the buffer assembly is arranged between the second pressing assembly and the fixing member. The fixing member is usually a fastening nut, which is threadedly sleeved on the first shaft body and tightly matched with the first shaft body through a threaded connection, thereby providing reliable axial fixing force. The threaded connection can also optimize the axial stiffness of the system by adjusting the pre-tightening force to meet the needs under different test conditions. The special position design of the buffer assembly enables it to fully play its buffering and compensation functions. In a high-temperature environment, the long shaft and the impeller will produce different thermal expansion amounts due to different materials. The buffer assembly can absorb this difference to prevent damage to the assembly due to excessive compression or positioning failure due to insufficient compression, ensuring stable performance of the system under various working conditions.

[0019] In other embodiments, the buffer assembly is two and is arranged in mirror symmetry, the buffer assembly has a fifth supporting plate, and a fifth annular flange is arranged circumferentially around the fifth supporting plate, and the fifth annular flange is outwardly expanded in a trumpet mouth shape, and the two buffer assemblies are arranged with the two fifth supporting plates opposite to each other after installation. The special layout of the two buffer assemblies and the trumpet mouth design enable them to produce cooperative elastic deformation when subjected to axial force, and the opposite arrangement of the fifth supporting plates forms an elastic buffer cavity that can absorb and disperse axial force, while the trumpet mouth design of the fifth annular flange optimizes stress distribution, making deformation more uniform. This design not only effectively compensates for thermal expansion of the long shaft, but also resists vibration and impact caused by unbalanced mass of the impeller, improves overall stability and reliability of the system, and its working principle is that at high temperature, the long shaft is elongated to push the buffer assembly, the trumpet mouth structure produces elastic deformation to absorb part of the elongation, and at the same time, through the interaction of the fifth supporting plates, the remaining axial force is uniformly transmitted to the second pressing assembly, ensuring that the impeller always maintains stable axial positioning. BRIEF DESCRIPTION OF DRAWINGS

[0020] Figure 1 is a partial sectional view of the present application.

[0021] Figure 2 is a structure schematic diagram of the long shaft in the present application.

[0022] Figure 3 is a front view and sectional view of the left cone sleeve in the present application.

[0023] Figure 4 is a three-dimensional structure schematic diagram of the left clamp sleeve in the present application.

[0024] Figure 5 is a front view of the left clamp sleeve in the present application.

[0025] Figure 6 is a three-dimensional structure schematic diagram of the right clamp sleeve in the present application.

[0026] Figure 7 is a sectional view of the right cone sleeve in the present application.

[0027] Figure 8 is a sectional view of the buffer assembly in the present application.

[0028] wherein:

[0029] 1. Long shaft; 101. First shaft body; 102. Second shaft body; 2. Left tapered sleeve; 201. First support plate; 202. First annular guard; 203. First shaft hole; 204. First keyhole; 3. Left clamping sleeve; 301. Second support plate; 302. Second annular guard; 303. Second shaft hole; 304. Second keyhole; 305. First tension groove; 4. Right clamping sleeve; 401. Third support plate; 402. Third annular guard ; 403, Third shaft hole; 404, Second tension groove; 405, Third tension groove; 5, Right cone sleeve; 501, Fourth support plate; 502, Fourth annular guard; 503, Fourth shaft hole; 504, Annular groove; 6, Buffer assembly; 601, Fifth support plate; 602, Fifth annular guard; 603, Fifth shaft hole; 7, Fixing component; 8, Rectangular key; 9, Impeller; 901, First pressing part; 902, Second pressing part of impeller. Detailed Implementation

[0030] The specific embodiments of the present invention will now be described with reference to the accompanying drawings.

[0031] like Figures 1-8 As shown in the figure, this embodiment discloses a high-temperature over-rotation test device for impellers, including a long shaft 1, an impeller 9, a press-fit assembly, a buffer assembly 6, and a fixing component 7. It enables the testing of the impeller 9 under ultra-high temperatures (above 700°C) and over-rotation (80,000 rpm to 90,000 rpm), overcoming the thermal expansion caused by ultra-high temperatures and over-rotation, thus ensuring stable and reliable rotation of the impeller 9. Through the coordinated operation of a precisely designed structure and components, the device ensures stable and reliable operation of the impeller 9 under extreme high-temperature and high-speed rotation conditions. This is crucial for simulating the performance testing of the impeller 9 under real-world working conditions, helping to identify potential problems early, optimize product design, and improve product reliability and service life.

[0032] like Figure 2 As shown, the long shaft 1 in this embodiment includes a first shaft 101 and a second shaft 102 that are concentrically arranged and have different diameters. The diameter of the first shaft 101 is smaller than the diameter of the second shaft 102. As the main support structure of the entire test device, the long shaft 1 has a specially designed double-diameter structure that not only provides sufficient strength and rigidity to withstand the huge centrifugal force generated by the high-speed rotation of the impeller 9, but also effectively disperses stress concentration, reduces the risk of fatigue fracture, and provides a precise positioning reference for the installation of other components.

[0033] like Figure 1As shown, the impeller 9 in the embodiment is sleeved on the first shaft body 101 of the long shaft 1, and the two ends of the inner ring of the impeller 9 extend outward in the axial direction and form the first pressing portion 901 and the impeller second pressing portion 902; the structural design of the impeller 9 not only increases the contact area with the long shaft 1, improves the torque transmission efficiency, but also effectively disperses the axial pressure and reduces local stress concentration, and the first pressing portion 901 and the impeller second pressing portion 902 provide a stable mounting position for the pressing assembly, ensuring the axial positioning accuracy of the impeller 9 during high-speed rotation.

[0034] As shown in the figure, Figure 1 the first pressing assembly in the embodiment is sleeved on the first shaft body 101 between the impeller 9 and the long shaft 1, is pressed on the first pressing portion 901 of the impeller 9, and a plurality of rectangular keys 8 are inserted on the end face of the first pressing assembly in a ring-shaped distribution, and the two ends of the rectangular keys 8 are respectively inserted into the second shaft body 102 of the long shaft 1 and the side wall of the impeller 9; the first pressing assembly realizes reliable connection between the impeller 9 and the long shaft 1 through precise mechanical cooperation and fixation of the rectangular keys 8, the rectangular keys 8 not only transmit torque, but also prevent the impeller 9 from slipping relative to the long shaft 1, ensuring synchronous rotation of the two, and this design effectively improves the overall rigidity and dynamic response characteristics of the system.

[0035] As shown in the figure, Figure 1 the second pressing assembly in the embodiment is sleeved on the first shaft body 101 on the other side of the impeller 9, and is pressed on the impeller second pressing portion 902 of the impeller 9. The second pressing assembly works cooperatively with the first pressing assembly to axially position and fix the impeller 9 from both sides, and this symmetrical design can effectively balance the axial force, reduce deformation and stress concentration caused by unilateral stress, improve the rotation stability and test accuracy of the impeller 9, and facilitate installation and debugging.

[0036] In the embodiment, the first pressing assembly includes a left clamp sleeve 3 and a left taper sleeve 2.

[0037] Specifically, as shown in the figure, Figures 4-5 the left clamp sleeve 3 in the embodiment has a second supporting plate 301 sleeved on the first shaft body 101, and a second annular guard edge 302 annularly arranged around the second supporting plate 301, the second supporting plate 301 and the second annular guard edge 302 are an integral structure, the second annular guard edge 302 is pressed on the first pressing portion 901 of the impeller 9, and the second annular guard edge 302 is close to the end face of the first pressing portion 901 of the impeller 9; the left clamp sleeve 3 realizes axial positioning and partial torque transmission function through precise cooperation of the second supporting plate 301 with the first shaft body 101 and pressing of the second annular guard edge 302 on the first pressing portion 901 of the impeller 9, and the design of close to the end face of the impeller 9 can effectively reduce axial movement and improve positioning accuracy, while providing a basis for subsequent tension adjustment.

[0038] As shown in the drawings, Figure 3 The left cone sleeve 2 in this embodiment has a first supporting plate 201 sleeved on the first shaft body 101, and a first annular guard 202 arranged circumferentially around the first supporting plate 201. The first supporting plate 201 and the first annular guard 202 are of an integrated structure, thereby improving the overall strength.

[0039] The first annular guard 202 is sleeved on the second annular guard 302, and a first gap h1 is provided between the first annular guard 202 and the end face of the first pressing portion 901 of the impeller 9, and satisfies: 1mm≤h1≤2mm. The left cone sleeve 2 can form a precise conical surface cooperation with the left clamp sleeve 3, and the first gap h1 provides a necessary buffer space for high-temperature expansion and mechanical deformation, thereby preventing the components from being stuck or damaged due to thermal stress, and meanwhile, the gap cooperation can also realize accurate axial positioning through axial force adjustment during installation.

[0040] As shown in the drawings, Figure 3 and Figure 4 Key holes corresponding to the rectangular keys 8 are formed on the end faces of the first supporting plate 201 and the second supporting plate 301. The design of the key holes ensures that the rectangular keys 8 can be accurately installed, realizes reliable transmission of torque, and prevents relative rotation between the components. This precise mechanical connection method has higher positioning accuracy and reliability than the traditional key connection, can effectively reduce vibration and noise, and improves the overall performance of the system.

[0041] In this embodiment, the inner wall of the first annular guard 202 is tapered, and the radial thickness of the side of the first annular guard 202 away from the first supporting plate 201 is smaller than the radial thickness of the side of the first annular guard 202 close to the first supporting plate 201; the outer wall of the second annular guard 302 is tapered corresponding to the inner wall of the first annular guard 202. (This corresponding taper design ensures that the left cone sleeve 2 and the left clamp sleeve 3 can form a perfect conical surface cooperation, and when the axial force acts, the two can tightly fit, realizing efficient torque transmission and accurate axial positioning, and at the same time, this design is also convenient for installation and disassembly, and the thickness design optimizes the stress distribution, making the tensioning force more uniform, reducing the risk of deformation or damage caused by local stress concentration.

[0042] In this embodiment, a plurality of annularly distributed first tensioning wire grooves 305 are formed on the side of the second annular guard 302 close to the impeller 9. Under the action of the axial force, these wire grooves can produce slight elastic deformation, so that the inner diameter of the second annular guard 302 changes, thereby realizing clamping or loosening of the first pressing portion 901 of the impeller 9. This elastic tensioning mechanism not only can adapt to impellers 9 of different sizes, but also can compensate for the size changes caused by thermal expansion or mechanical wear, ensuring long-term stable fixing effect.

[0043] In this embodiment, the second press-fitting assembly includes a right clamping sleeve 4 and a right conical sleeve 5.

[0044] Specifically, such as Figure 6 As shown, the right sleeve 4 in this embodiment has a third support plate 401 sleeved on the first shaft 101 and a third annular guard 402 circumferentially arranged around the third support plate 401. The third support plate 401 and the third annular guard 402 are an integral structure.

[0045] The third annular guard 402 is press-fitted onto the second press-fit part 902 of the impeller 9, and the third annular guard 402 is infinitely close to the end face of the second press-fit part 902 of the impeller 9. The right sleeve 4 corresponds to the left sleeve 3. Through the cooperation of the third support plate 401 and the first shaft 101, and the press-fitting of the third annular guard 402 onto the second press-fit part 902 of the impeller 9, axial positioning and partial torque transmission functions are realized. Its design of being infinitely close to the end face of the impeller 9 can effectively reduce axial movement and improve positioning accuracy. Working together with the left sleeve 3, it ensures the stable rotation of the impeller 9.

[0046] like Figure 7 As shown, in this embodiment, the right conical sleeve 5 has a fourth support plate 501 sleeved on the first shaft 101, and a fourth annular guard 502 circumferentially arranged around the fourth support plate 501. The fourth support plate 501 and the fourth annular guard 502 are an integral structure.

[0047] The fourth annular guard 502 is fitted onto the third annular guard 402, and a second gap h2 is provided between the fourth annular guard 502 and the end face of the second press-fit part 902 of the impeller 9, satisfying: 1mm≤h2≤2mm. The design principle of the right tapered sleeve 5 is the same as that of the left tapered sleeve 2, achieving the tensioning function through tapered fit. The setting of the second gap h2 provides necessary buffer space for high-temperature expansion and mechanical deformation, preventing component jamming or damage caused by thermal stress. At the same time, this gap fit can also achieve precise axial positioning by adjusting the axial force during installation, forming a symmetrical fixed structure with the left tapered sleeve 2, improving the overall stability of the system.

[0048] In this embodiment, the inner wall of the fourth annular guard 502 is tapered, and the radial thickness of the fourth annular guard 502 on the side away from the fourth support plate 501 is less than the radial thickness of the fourth annular guard 502 on the side close to the fourth support plate 501. Its variable thickness design optimizes the stress distribution, makes the tension force more uniform, and reduces the risk of deformation or damage caused by local stress concentration. It echoes the design of the left cone sleeve 2 to form a complete fixing system.

[0049] The outer wall of the third annular edge 402 is tapered corresponding to the inner wall of the fourth annular edge 502. This tapered design allows the right tapered sleeve 5 to shrink radially when subjected to axial force, thereby tightening the right clamp sleeve 4, improving the fixing effect of the impeller 9, and ensuring that the right tapered sleeve 5 and the right clamp sleeve 4 form a perfect conical surface fit, which can tightly fit when subjected to axial force, achieving efficient torque transmission and accurate axial positioning. At the same time, this design also facilitates installation and disassembly, improving maintenance efficiency. The conical surface fit structure on the left side forms a symmetrical layout, enhancing the balance and stability of the system.

[0050] In this embodiment, as shown in Figure 6 The third supporting plate 401 and the third annular edge 402 are circumferentially provided with a plurality of second tightening grooves 404 distributed in a ring shape away from the side of the impeller 9; the second tightening grooves 404 are similar to the first tightening grooves 305, but the special layout on the right clamp sleeve 4 can adapt to different stress conditions. Under the action of axial force, these grooves can produce slight elastic deformation, causing the inner diameter of the third annular edge 402 to change, thereby achieving clamping or loosening of the second pressing part 902 of the impeller 9. This elastic tightening mechanism not only adapts to impellers 9 of different sizes, but also compensates for size changes caused by thermal expansion or mechanical wear, ensuring long-term stable fixing effect.

[0051] The third annular edge 402 is circumferentially provided with a plurality of third tightening grooves 405 distributed in a ring shape close to the side of the impeller 9; the position and number of the third tightening grooves 405 can ensure uniform distribution of tightening force under the action of axial force, preventing deformation or damage of the impeller 9 caused by local stress concentration. At the same time, this multi-groove design can also improve the elastic modulus of the component, enhance the resistance to vibration and impact, and improve the overall reliability of the system.

[0052] In this embodiment, the second tightening grooves 404 and the third tightening grooves 405 are distributed staggered. Through mutual compensation of elastic deformation in different directions, the size deviation caused by deformation in a single direction is reduced. At the same time, this layout can also optimize stress distribution, making the tightening force more uniformly act on the surface of the impeller 9, improving the fixing effect and test accuracy.

[0053] In this embodiment, the fourth annular edge 502 is provided with a ring groove 504 on a section of the outer wall connected to the fourth supporting plate 501. The ring groove 504 has the following effects: first, it can reduce the weight of the component, reduce the inertial force, and improve the dynamic response characteristics of the system; second, the ring groove 504 can act as a stress release area to reduce stress concentration caused by thermal expansion or mechanical load; finally, the ring groove 504 can also serve as a mounting and positioning mark, facilitating accurate assembly and debugging of the component. This multifunctional design reflects the ingenuity and practicality of engineering design.

[0054] This embodiment also includes a fastener 7 and a buffer assembly 6.

[0055] The fastener 7 is usually a fastening nut, which is threaded onto the first shaft 101. It is tightly fitted to the first shaft 101 through a threaded connection, providing a reliable axial fixing force. The threaded connection can also optimize the axial stiffness of the system by adjusting the preload, so as to meet the requirements under different test conditions.

[0056] like Figure 8 As shown, the buffer assembly 6 is positioned between the second press-fit assembly and the fixing member 7. The special positioning design of the buffer assembly 6 enables it to fully exert its buffering and compensation functions. In high-temperature environments, the long shaft 1 and the impeller 9 will have different amounts of thermal expansion due to their different materials. The buffer assembly 6 can absorb this difference, preventing component damage due to excessive compression or positioning failure due to insufficient compression, and ensuring that the system maintains stable performance under various operating conditions.

[0057] In this embodiment, there are two buffer components 6 arranged in a mirror-symmetrical manner. Each buffer component 6 has a fifth support plate 601 and a fifth annular guard 602 arranged around the fifth support plate 601. The fifth support plate 601 and the fifth annular guard 602 are integral structures, and the fifth annular guard 602 expands outward with a flared shape. After the two buffer components 6 are installed, the two fifth support plates 601 are arranged opposite to each other. The special layout and flared design of the two buffer components 6 enable them to generate synergistic elastic deformation when subjected to axial force. The relative arrangement of the fifth support plate 601 forms an elastic buffer cavity that can absorb and disperse axial force. At the same time, the flared design of the fifth annular guard 602 optimizes stress distribution and makes deformation more uniform. This design can not only effectively compensate for the thermal expansion of the long shaft 1, but also resist the vibration and impact caused by the unbalanced mass of the impeller 9, thereby improving the overall stability and reliability of the system. Its working principle is that at high temperature, the long shaft 1 elongates and pushes the buffer component 6. The flared structure generates elastic deformation to absorb part of the elongation. At the same time, through the interaction of the fifth support plate 601, the remaining axial force is evenly transmitted to the second press-fit component, ensuring that the impeller 9 always maintains a stable axial position.

[0058] The technical solution adopted in this invention is to fix the impeller 9 on the long shaft 1 and connect the long shaft 1 to the testing machine to simulate the working environment of the impeller 9 in a gas turbine and conduct tests on the impeller 9. This method can realistically reproduce the stress state and thermal environment of the impeller 9 in actual operation. By precisely controlling parameters such as temperature, speed, and load, the performance indicators of the impeller 9, such as strength, fatigue life, and thermal stability, can be comprehensively evaluated, providing reliable data support for product optimization design. Furthermore, this testing method can identify potential design defects or manufacturing problems in advance, avoiding malfunctions during actual use and greatly improving the reliability and safety of the product.

[0059] Specifically, the installation process in the present embodiment is as follows:

[0060] The left cone sleeve 2 is interference fitted on the long shaft 1 and abuts against the large end face of the long shaft 1, and the two rectangular keys 8 are fixed on the long shaft 1 and pass through the left cone sleeve 2, limiting the circumferential rotation of the left cone sleeve 2. The right end of the rectangular key 8 is clamped into the left end key groove of the impeller 9, driving the impeller 9 to rotate and transmit torque. This precise mechanical connection ensures efficient transmission of torque. The interference fit design of the left cone sleeve 2 provides sufficient friction to prevent loosening, and the precise key groove fit of the rectangular key 8 achieves circumferential positioning to prevent relative rotation. This dual positioning mechanism greatly improves the reliability and safety of the system. At the same time, this design facilitates installation and disassembly, improving maintenance efficiency. In high-temperature environments, the interference fit and key connection can maintain stable performance and prevent connection failure due to thermal expansion.

[0061] The left clamp sleeve 3 has a tensioning slot around the circumference. The tensioning slot is designed to pass through, and under the action of the axial force, the inner hole diameter changes, allowing the left clamp sleeve 3 to clamp or loosen the left end cylindrical surface of the impeller 9. The through design of the tensioning slot allows the left clamp sleeve 3 to uniformly elastically deform when subjected to an axial force. By precisely controlling the size of the axial force, the left clamp sleeve 3 can achieve precise clamping or loosening of the left end cylindrical surface of the impeller 9. This elastic tensioning mechanism not only adapts to impellers 9 of different sizes, but also compensates for size changes due to thermal expansion or mechanical wear, ensuring long-term stable fixing effect. At the same time, the design of the tensioning slot can also improve the elastic modulus of the assembly, enhance the resistance to vibration and impact, and improve the overall reliability of the system.

[0062] The right clamp sleeve 4 has 8 tensioning slots in different directions around the circumference. When the fixing member 7 is tightened, the fixing member 7 pushes the two counter-mounted (two fifth supporting plates 601 are oppositely arranged, and the fifth ring-shaped protective edge 602 in the shape of a trumpet is expanded outward) buffer assemblies 6 and the right cone sleeve 5 to move left. The large hole diameter of the right clamp sleeve 4 cooperating with the taper surface of the right cone sleeve 5 decreases, clamping the right end cylindrical surface of the impeller 9, and the small hole diameter decreases, clamping the cylindrical surface of the long shaft 1, completing the positioning of the impeller 9, making the impeller 9 coaxial with the long shaft 1. Through the tightening action of the fixing member 7, a series of precise mechanical movements are triggered: first, the axial force of the fixing member 7 pushes the buffer assembly 6, and the special design of the buffer assembly 6 causes it to elastically deform, absorbing part of the axial force and uniformly transmitting it to the right cone sleeve 5. The taper design of the right cone sleeve 5 converts the axial force into a radial force, causing the right clamp sleeve 4 to contract radially, clamping the right end cylindrical surface of the impeller 9 with the large hole and clamping the cylindrical surface of the long shaft 1 with the small hole. This dual clamping mechanism ensures the precise coaxial positioning of the impeller 9 and the long shaft 1. At the same time, the special layout of the 8 tensioning slots optimizes the stress distribution, making the tensioning force more uniform and reducing the risk of deformation or damage caused by local stress concentration. This intelligent tensioning system can automatically adapt to size changes under different working conditions, ensuring long-term stable fixing effect.

[0063] Due to the different materials of the impeller 9 and the long shaft 1, when the long shaft 1 is excessively elongated due to thermal deformation in a high-temperature environment, the positioning of the impeller 9 will fail, which may cause danger and damage the equipment. The specially designed buffer assembly 6 is used to compensate for the elongation of the long shaft 1 in a high-temperature environment, so as to ensure that the axial compression force meets the positioning requirements of the impeller 9.

[0064] In a high-temperature environment, the long shaft 1 and the impeller 9 will have different thermal expansion amounts due to the different materials. Without a buffering mechanism, the difference will cause the axial compression force to be too large or too small. If the axial compression force is too large, the assembly may be damaged. If the axial compression force is too small, the positioning will fail. The buffer assembly 6 can absorb part of the elongation of the long shaft 1 through its elastic deformation capacity, and simultaneously uniformly transmit the remaining axial force to the second pressing assembly, so as to ensure that the impeller 9 always maintains stable axial positioning. The mirror-symmetrical design and the horn structure further optimize the stress distribution and improve the buffering effect and system stability. This intelligent buffering mechanism greatly improves the adaptability and reliability of the device, so that the device can operate stably for a long time under extreme working conditions.

[0065] After the impeller 9 is installed, the left end of the long shaft 1 is connected with the testing machine, and then the high-temperature over-speed test can be performed.

[0066] The present application adopts a gapless positioning structure, so that the impeller 9 is reliably positioned on the rotating shaft. The specially designed buffer assembly 6 ensures that the axial force meets the positioning requirements of the impeller 9 in a high-temperature environment. The gapless positioning structure ensures the zero-gap fit between the impeller 9 and the long shaft 1 through precise mechanical design and manufacturing process. This design eliminates the vibration and noise caused by the gap in the traditional structure, improves the dynamic response characteristics and test accuracy of the system. At the same time, the gapless design can also prevent the fretting wear caused by the gap, prolonging the service life of the assembly. The special design of the buffer assembly 6 is the key innovation to solve the thermal expansion problem in a high-temperature environment. The elastic deformation capacity of the buffer assembly 6 can automatically compensate for the thermal expansion of the long shaft 1, so as to ensure that the axial compression force always remains in the optimal range. This intelligent buffering mechanism greatly improves the adaptability and reliability of the device, so that the device can operate stably for a long time under extreme working conditions. Through actual use verification, the present application indeed meets the design requirements. In a high-temperature and high-load test state, the present application effectively solves the problems of thermal expansion, thermal deformation, thermal stress, thermal centering, etc. caused by different materials of the impeller 9 and the rotating shaft, greatly improving the reliability and safety of the test.

[0067] The above description is an explanation of the present application, not a limitation of the application. The scope of the present application is defined in the claims. Within the protection scope of the present application, any form of modification can be made.

Claims

1. A high-temperature overspeed test device for impellers, characterized in that, include: The long shaft includes a first shaft and a second shaft that are concentrically arranged and have different diameters, wherein the diameter of the first shaft is smaller than the diameter of the second shaft; An impeller is fitted onto a first shaft body with a long shaft, and the two ends of the inner ring of the impeller extend outward along the axial direction to form a press-fit part; The first pressing assembly is sleeved on the first shaft body between the impeller and the long shaft. The first pressing assembly is pressed onto one of the pressing parts of the impeller, and a plurality of rectangular keys distributed in a ring are inserted through the end face of the first pressing assembly. The two ends of the rectangular keys are respectively inserted into the second shaft body of the long shaft and the side wall of the impeller. The second press-fitting assembly is sleeved on the first shaft body on the other side of the impeller, and the second press-fitting assembly is press-fitted onto another press-fitting part of the impeller; A buffer assembly is disposed between the second press-fit assembly and the fixing member.

2. The impeller high-temperature overspeed test device as described in claim 1, characterized in that: The first press-fit assembly includes: The left jacket has a second support plate sleeved on the first shaft and a second annular guard edge circumferentially arranged on the second support plate. The second annular guard edge is press-fitted onto the press-fitting part on the corresponding side of the impeller, and the second annular guard edge is infinitely close to the end face of the corresponding side of the impeller. And, the left cone sleeve, which has a first support plate sleeved on the first shaft body, and a first annular guard edge circumferentially arranged on the first support plate, the first annular guard edge being sleeved on the second annular guard edge, and the first annular guard edge being provided with a first gap h1 from the impeller end face, and satisfying: 1mm≤h1≤2mm. Both the first support plate and the second support plate have keyholes corresponding to the rectangular key on their end faces.

3. The impeller high-temperature overspeed test device as described in claim 2, characterized in that: The inner wall of the first annular guard is tapered, and the radial thickness of the first annular guard away from the first support plate is less than the radial thickness of the first annular guard close to the first support plate. The outer wall of the second annular guard has a tapered setting corresponding to the inner wall of the first annular guard.

4. The impeller high-temperature overspeed test device as described in claim 3, characterized in that: The second annular guard has multiple annularly distributed first tension grooves on the side near the impeller.

5. The impeller high-temperature overspeed test device as described in claim 1, characterized in that: The second press-fit assembly includes: The right sleeve has a third support plate sleeved on the first shaft and a third annular guard edge circumferentially arranged around the third support plate. The third annular guard edge is press-fitted onto the press-fitting part on the corresponding side of the impeller, and the third annular guard edge is infinitely close to the end face of the corresponding side of the impeller. And, the right cone sleeve, which has a fourth support plate sleeved on the first shaft, and a fourth annular guard circumferentially arranged on the fourth support plate, the fourth annular guard sleeved on the third annular guard, and the fourth annular guard is provided with a second gap h2 from the impeller end face, and satisfies: 1mm≤h2≤2mm.

6. The impeller high-temperature overspeed test device as described in claim 5, characterized in that: The inner wall of the fourth annular guard is tapered, and the radial thickness of the fourth annular guard away from the fourth support plate is less than the radial thickness of the fourth annular guard close to the fourth support plate. The outer wall of the third annular guard has a tapered setting corresponding to the inner wall of the fourth annular guard.

7. The impeller high-temperature overspeed test device as described in claim 6, characterized in that: The third support plate and the third annular guard are provided with multiple annularly distributed second tension grooves on the side away from the impeller. The third annular guard has multiple annularly distributed third tension grooves on the side near the impeller. Furthermore, the second tensioning groove and the third tensioning groove are staggered.

8. The impeller high-temperature overspeed test device as described in claim 6, characterized in that: A ring groove is provided on the outer wall of the section where the fourth annular guard edge connects to the fourth support plate.

9. The impeller high-temperature overspeed test device as described in claim 1, characterized in that: Also includes: The fastener is threaded onto the first shaft.

10. The impeller high-temperature overspeed test device as described in claim 9, characterized in that: The buffer assembly consists of two components arranged in a mirror-symmetrical manner. Each buffer assembly has a fifth support plate and a fifth annular guard surrounding the fifth support plate. The fifth annular guard expands outward in a funnel shape, and the two fifth support plates are positioned opposite each other after the two buffer assemblies are installed.

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