Rotating test device for avoiding harmful resonance frequencies at high rotational speeds

Abstract

The present invention discloses a rotor test device for avoiding harmful resonance frequencies at high speeds, comprising: a test support for enabling the rotor test device to avoid harmful resonance frequencies at high speeds, a torque transmission shaft member, and a bearing housing assembly. The test support is of a solid triangular structure, for detachably fixing to the test platform, and is provided with an installation through-hole vertically penetrating the plate surface at the upper end. The bearing housing assembly is fixedly installed axially in the installation through-hole, and a bearing housing hole axially penetrating the bearing housing assembly is provided at the end face. The torque transmission shaft member is rotatably installed in the bearing housing hole, and its input end is connected to a power input device, and its opposite output end is connected to a test piece. A lubricating oil path structure is further provided in the bearing housing assembly to enable the torque transmission shaft member to stably and reliably transmit power and torque. The present invention patent can avoid harmful resonance frequencies within the speed range and cover the speed ranges of various current rotors, thereby avoiding resonance during the test of the rotor at high speeds.

Description

Technical Field

[0001] The present invention relates to the technical field of aeroengines, and in particular, to a rotor test device for avoiding harmful resonance frequencies at high speeds. Background Art

[0002] The development of modern medium and small aeroengines aims to obtain higher engine performance, and at the same time, use lighter rotating and static parts. An important measure to achieve this goal is to increase the rotational speed of aeroengines, so that the rotors of medium and small aeroengines are developing in the direction of an increasing aspect ratio and becoming more "flexible", with an increasingly complex structure, and generally using flexible rotors with high rotational speeds and high strain energies. The rotational speeds of existing domestic and foreign aeroengine gas generator rotors are generally higher than 40,000 r / min, which increases the test risks. The main manifestation is that there are harmful high-speed resonance frequencies within the working speed range of the test support for the rotor, resulting in a large vibration acceleration reflected at this speed, endangering the safety of the rotor test at high speeds.

[0003] The existing solution is to use a test support with a hollow structure in the middle, as shown in Figure 1 .

[0004] Using a test support with a hollow structure in the middle part, its overall rigidity is reduced. Through finite element analysis and experimental verification, there are two orders of harmful resonance frequencies within the rotational speed range of the gas generator rotor (the vibration modes are torsion and bending-torsion), and the resonance speeds are close to the working speed of the gas generator rotor, resulting in the rotor being unable to run to the working speed due to excessive vibration during the test, endangering the test safety and affecting the progress of the model development. Summary of the Invention

[0005] The present invention provides a rotor test device for avoiding harmful resonance frequencies at high speeds to solve the technical problem that using a test support with a hollow structure in the middle part causes the rotor to be unable to run to the working speed due to excessive vibration during the test, endangering the test safety and affecting the progress of the model development.

[0006] The technical solution adopted by the present invention is as follows:

[0007] A rotor test device for avoiding harmful resonance frequencies at high speeds, comprising: a test support for enabling the rotor test device to avoid harmful resonance frequencies at high speeds, a torque transmission shaft member for stably transmitting power torque, and a bearing seat assembly for mounting and supporting the torque transmission shaft member; the test support is a solid triangular structure for detachably fixing to the test platform, and the upper end of the test support is provided with an installation through hole vertically penetrating the plate surface; the bearing seat assembly is axially fixedly installed in the installation through hole, the end face of the bearing seat assembly is provided with a bearing seat hole axially penetrating the bearing seat assembly, the torque transmission shaft member is axially rotatably installed in the bearing seat hole, and the input end of the torque transmission shaft member extending out of the bearing seat hole is used to be connected to a power input device, and its opposite output end extends out of the bearing seat hole and is used to be connected to a test piece; a lubricating oil path structure for lubricating the torque transmission shaft member is further provided in the bearing seat assembly, so that the torque transmission shaft member stably and reliably transmits power and torque.

[0008] Further, the test support is an integrally formed structure; each of the two lower bottom corners of the test support is provided with a sling screw hole for installing a sling and recessed inward, and an installation screw hole for installing and fixing a fastener of the test support and vertically penetrating the lower bottom corner; the lower bottom edge of the test support is recessed inward so that the relatively convex lower bottom surface forms a support bottom surface for supporting and positioning the test support.

[0009] Further, the bearing seat assembly includes a hollow cylindrical bearing seat main body, and a first end cover member and a second end cover member respectively provided at both ends of the bearing seat main body; the installation through hole is a stepped hole axially arranged, the second end of the bearing seat main body protrudes outward to form a limit flange, the bearing seat main body is axially installed in the installation through hole, and the limit flange abuts against the first limit step of the stepped hole for limiting, and the second end of the bearing seat main body is detachably fixed to the limit flange by fastening screws sequentially arranged in the circumferential direction; the central hole of the bearing seat main body forms the bearing seat hole, and the first end cover member and the second end cover member are respectively installed on the outer circles of the input end and the output end of the torque transmission shaft member, and the first end cover member and the second end cover member are respectively detachably fixed to the bearing seat main body for axially positioning the torque transmission shaft member and sealing both ends of the bearing seat hole.

[0010] Further, the bearing seat assembly further includes a first adjustment pad for adjusting the axial installation position of the bearing seat main body relative to the test support; the first adjustment pad is installed on the outer circle of the bearing seat main body and is located between the limit flange and the first limit step.

[0011] Further, the torque transmission shaft member includes a torque transmission shaft axially passing through the bearing seat hole, and bearings mounted on the outer circles of the input end and the output end of the torque transmission shaft; the input end of the torque transmission shaft extending out of the bearing seat hole is used to connect the power input device, and its opposite output end is used to connect the test piece, and second limiting steps for positioning are respectively provided on the outer circles of the input end and the output end of the torque transmission shaft; the bearings are located in the bearing seat hole, and the inner ends of the bearings abut and are limited against the corresponding second limiting steps, and their opposite outer ends abut and are limited against the corresponding first end cover member or second end cover member.

[0012] Further, the torque transmission shaft includes a spline shaft for transmitting torque and a connecting shaft; the spline shaft is axially rotatably supported in the bearing, and external splines are machined on the outer circle of the input end of the spline shaft for connecting with the power input device; the connecting shaft is in a hollow cylindrical shape, one end of which is fixedly sleeved on the outer circle of the output end of the spline shaft through a connecting member, and internal splines are provided on the inner wall of its opposite end for connecting with the test piece.

[0013] Further, the first end cover member includes a first labyrinth ring for sealing and a first limiting end plate; the first labyrinth ring is mounted on the outer circle of the input end of the spline shaft, and the inner end abuts and is limited against the corresponding bearing; the first limiting end plate is sleeved on the outer circle of the first labyrinth ring, abuts and is limited against the outer end of the first labyrinth ring, and the first limiting end plate is detachably fixed to the bearing seat main body through a compression screw.

[0014] Further, the second end cover member includes a second labyrinth ring for sealing, a disc spring for applying an initial pressure to the bearing, and a second limiting end plate; the second labyrinth ring is mounted on the outer circle of the output end of the spline shaft, and its inner end abuts and is limited against the corresponding bearing, and its opposite outer end abuts and is limited against the end of the connecting shaft; the disc spring and the second limiting end plate are respectively mounted on the outer circle of the second labyrinth ring, and the disc spring is located between the corresponding bearing and the second limiting end plate, and the second limiting end plate is detachably fixed to the bearing seat main body through a compression screw.

[0015] Further, the lubricating oil path structure includes lubricating oil paths provided in the bearing seat main body and the first limiting end plate, an oil path inlet and an oil path outlet opened on the bearing seat main body and connecting the lubricating oil paths, an oil supply nozzle connected to the oil path inlet, an oil return nozzle connected to the oil path outlet, and an injection ring; the injection ring is sleeved on the outer circle of the second labyrinth ring and is limited between the disc spring and the corresponding bearing; the lubricating oil paths communicate with the two end faces of the bearing seat main body, and the bearings, the first labyrinth ring, the second labyrinth ring and the injection ring.

[0016] Further, the rotor test device further includes an acceleration sensor for measuring the vibration acceleration during the test and a temperature sensor for monitoring the working temperature of the bearing; the acceleration sensor is arranged on the test support; the temperature sensor is arranged on the bearing seat main body.

[0017] The present invention has the following beneficial effects:

[0018] This invention patent aims to solve the resonance problem existing in the high-speed test of an aero-engine rotor, and designs a test support that avoids harmful resonance frequencies within the rotational speed range, improving the resonance frequency of the test support. At the same time, a rotor test device with this test support, bearing housing assembly, and torque transmission shaft component is designed for the aero-engine rotor test, covering the rotational speed ranges of various current rotors, making its harmful resonance frequencies outside the highest rotational speed range and having a certain margin, avoiding resonance during the high-speed test of the rotor. At the same time, it ensures the effectiveness of the bearing housing assembly and torque transmission shaft component structures within this test support, and the torque transmission shaft component can stably and reliably transmit power and torque, thus bringing safety guarantee to the test. In the prior art, as described in the background art part, to obtain higher engine performance, mainly lighter rotating and stationary parts are used. Therefore, the test supports of existing aero-engine rotor test devices generally adopt a Figure 1 hollow structure in the middle as shown in the attached figure, thus resulting in the technical problem that "the rotor cannot reach the operating speed due to excessive vibration during the test, endangering the test safety and affecting the progress of model development". In the present invention, to solve this existing technical problem, after long-term exploration, a large number of tests, and designs, technical means to solve this technical problem are proposed, that is, the test support in the present invention is a solid triangular structure. The "solid" structure can effectively increase the structural stiffness, thus avoiding the resonance frequency at high rotational speeds. The "triangular" structure increases the structural stability and support rigidity, so there are no harmful resonance frequencies within the rotational speed range of the gas generator rotor and has a large margin, which can meet the requirements of existing aero-engine rotor tests. At the same time, to reduce the weight increase problem of the test device caused by the solid structure setting of the test support, in the present invention, the design of the bearing housing assembly, torque transmission shaft component, and lubricating oil path structure is coordinated, making the overall structure of the test device simple, stable, and reliable in operation. In addition, the present invention has been verified by tests. The test support with the rotor has successfully run to the target rotational speed of the gas generator rotor, and the vibration acceleration on the test support within the test rotational speed range is very small, especially there is no harmful resonance at high rotational speeds. The test results prove to be feasible and have been successfully applied to the rotor tests of other models, and can also guide the design of test supports for other similar structures.

[0019] In addition to the purposes, features, and advantages described above, the present invention has other purposes, features, and advantages. The following will refer to the drawings to further elaborate on the present invention in detail. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] The drawings forming a part of this application are used to provide a further understanding of the present invention. The schematic embodiments of the present invention and their descriptions are used to explain the present invention and do not constitute an improper limitation of the present invention. In the drawings:

[0021] Figure 1 is a front view structural schematic diagram of an existing test support;

[0022] Figure 2 is a sectional view structural schematic diagram of a rotor test device according to a preferred embodiment of the present invention;

[0023] Figure 3 is Figure 2 a front view structural schematic diagram of the test support in

[0024] Figure 4 is Figure 2 an assembly schematic diagram of a bearing housing assembly and a torque transmission shaft member in

[0025] Figure 5 is Figure 4 a front view structural schematic diagram of

[0026] Legend Explanation

[0027] 10. Test support; 101. Installation through hole; 102. Hoisting ring threaded hole; 103. Installation threaded hole; 104. Support bottom surface; 105. First limiting step; 20. Torque transmission shaft member; 21. Torque transmission shaft; 211. Spline shaft; 212. Connecting shaft; 213. Connecting member; 22. Bearing; 30. Bearing housing assembly; 301. Bearing housing hole; 31. Bearing housing body; 311. Limiting flange; 32. First end cover member; 321. First labyrinth ring; 322. First limiting end plate; 323. Compression screw; 33. Second end cover member; 331. Second labyrinth ring; 332. Disc spring; 333. Second limiting end plate; 34. Fastening screw; 35. First adjusting pad; 36. Second adjusting pad; 40. Lubricating oil path structure; 41. Lubricating oil path; 42. Oil supply nozzle; 43. Oil return nozzle; 44. Oil injection ring; 50. Acceleration sensor; 60. Temperature sensor. Detailed Embodiment

[0028] The following will describe the embodiments of the present invention in detail with reference to the accompanying drawings. However, the present invention can be implemented in many different ways defined and covered by the following.

[0029] Refer to Figure 2, a preferred embodiment of the present invention provides a rotor test device for avoiding harmful resonance frequencies at high speeds, comprising: a test support 10 for enabling the rotor test device to avoid harmful resonance frequencies at high speeds, a torque transmission shaft member 20 for stably transmitting power torque, and a bearing block assembly 30 for mounting and supporting the torque transmission shaft member 20. The test support 10 is a solid triangular structure for detachably fixing to the test platform, and an installation through hole 101 vertically penetrating the plate surface is provided at the upper end of the test support 10. The bearing block assembly 30 is axially fixedly installed in the installation through hole 101. A bearing block hole 301 axially penetrating the bearing block assembly 30 is provided at the end face of the bearing block assembly 30. The torque transmission shaft member 20 is rotationally installed axially in the bearing block hole 301. The input end of the torque transmission shaft member 20 extending out of the bearing block hole 301 is used to be connected to a power input device, and its opposite output end extends out of the bearing block hole 301 and is used to be connected to a test piece. A lubricating oil path structure 40 for lubricating the torque transmission shaft member 20 is further provided in the bearing block assembly 30, so that the torque transmission shaft member 20 can stably and reliably transmit power and torque.

[0030] This invention patent aims to solve the resonance problem existing in the high-speed test of an aero-engine rotor, design a test support 10 that avoids harmful resonance frequencies within the speed range, improve the resonance frequency of the test support 10. At the same time, design a rotor test device with the test support 10, the bearing block assembly 30 and the torque transmission shaft member 20 for aero-engine rotor tests, covering the speed ranges of various current rotors, making its harmful resonance frequencies outside the highest speed range and having a certain margin, avoiding resonance during the high-speed test of the rotor, and at the same time ensuring the effectiveness of the bearing block assembly 30 and the torque transmission shaft member 20 structures within the test support 10, and the torque transmission shaft member 20 can stably and reliably transmit power and torque, thus bringing safety guarantee to the test; in the prior art, as described in the background art part, in order to obtain higher engine performance, mainly lighter rotating and static parts are used. Therefore, the test supports of existing engine rotor test devices generally adopt, for example, the attached Figure 1The middle hollow structure shown causes the technical problem that "during the test, the rotor cannot reach the operating speed due to excessive vibration, endangering the test safety and affecting the development progress of the model." In the present invention, to solve this existing technical problem, after long-term exploration, a large number of tests and designs, a technical means to solve this technical problem is proposed, that is, the test support 10 in the present invention is a solid triangular structure. The "solid" structure can effectively increase the structural stiffness, thus avoiding the resonance frequency at high speeds. The "triangular" structure increases the structural stability and support rigidity, so that there is no harmful resonance frequency within the rotational speed range of the gas generator rotor, and there is a large margin, which can meet the existing aviation engine rotor test requirements. At the same time, to reduce the weight increase problem of the test device caused by the solid structure setting of the test support 10, in the present invention, the design of the bearing seat assembly 30, the torque transmission shaft member 20 and the lubricating oil path structure 40 is cooperatively set, so that the overall structure of the test device is simple, and the operation is stable and reliable. In addition, the present invention has been verified by tests. The test support 10 with the rotor has successfully run to the target speed of the gas generator rotor, and the vibration acceleration on the test support 10 within the test speed range is very small, especially there is no harmful resonance at high speeds. The test results prove to be feasible and have been successfully applied to the rotor tests of other models, and can also guide the design of the rotor test supports of other similar structures.

[0031] Optionally, as Figure 2 and Figure 3 shown, the test support 10 is an integrally formed structure, with a simple processing technology, and the overall structure has high strength and good stability. At each of the two lower bottom corners of the test support 10, there are provided internal concave lifting ring threaded holes 102 for installing lifting rings, and installation threaded holes 103 that vertically penetrate the lower bottom corners and are used for installing and fixing fasteners of the test support 10. In this optional solution, the lifting rings with the same thread specification are connected to the lifting ring threaded holes 102 to play a load-bearing role during transportation. The test support 10 and the test platform are connected and fastened by an internal hexagonal screw passing through the installation threaded holes 103, and the disassembly and assembly are convenient. The lower bottom edge of the test support 10 is concave so that the relatively convex lower bottom surface forms a supporting bottom surface 104 for supporting and positioning the test support 10. In this optional solution, the entire test support 10 contacts the test platform through the supporting bottom surface 104, reducing the contact area, and then improving the processing accuracy of the supporting bottom surface 104 to ensure the contact accuracy with the test platform.

[0032] Optionally, as Figure 2 and Figure 4As shown in the figure, the bearing housing assembly 30 includes a hollow cylindrical bearing housing body 31, and a first end cover member 32 and a second end cover member 33 respectively disposed at both ends of the bearing housing body 31. The mounting through hole 101 is a stepped hole arranged axially. A limiting flange 311 protrudes outward from the second end of the bearing housing body 31. The bearing housing body 31 is axially installed in the mounting through hole 101, and the limiting flange 311 abuts against the first limiting step 105 of the stepped hole for positioning. And the second end of the bearing housing body 31 is detachably fixed to the limiting flange 311 by fastening screws 34 sequentially arranged circumferentially. The central hole of the bearing housing body 31 forms a bearing housing hole 301. The first end cover member 32 and the second end cover member 33 are respectively installed on the outer circles of the input end and the output end of the torque transmission shaft member 20, and the first end cover member 32 and the second end cover member 33 are respectively detachably fixed to the bearing housing body 31 to axially position the torque transmission shaft member 20 and block both ends of the bearing housing hole 301.

[0033] In this alternative solution, as Figure 4 shown, the bearing housing assembly 30 further includes a first adjusting pad 35 for adjusting the axial mounting position of the bearing housing body 31 relative to the test support 10. The first adjusting pad 35 is installed on the outer circle of the bearing housing body 31 and is located between the limiting flange 311 and the first limiting step 105. The function of the first adjusting pad 35 is that when the axial distance is too small after the torque transmission shaft member 20 is connected to the power input of the power input device, the axial distance can be adjusted by adding the first adjusting pad 35 to reduce the thickness of the limiting flange 311.

[0034] In this alternative solution, as Figure 4 shown, the torque transmission shaft member 20 includes a torque transmission shaft 21 axially passing through the bearing housing hole 301, and bearings 22 installed on the outer circles of the input end and the output end of the torque transmission shaft 21. The input end of the torque transmission shaft 21 extending out of the bearing housing hole 301 is used to connect the power input device, and its opposite output end is used to connect the test piece. Second limiting steps for positioning protrude on the outer circles of the input end and the output end of the torque transmission shaft 21. The bearings 22 are located in the bearing housing hole 301, and the inner ends of the bearings 22 abut against and are limited by the corresponding second limiting steps, and their opposite outer ends abut against and are limited by the corresponding first end cover member 32 or second end cover member 33.

[0035] In a specific embodiment of this alternative solution, as Figure 4As shown, the torque transmission shaft 21 includes a spline shaft 211 for transmitting torque and a connecting shaft 212. The spline shaft 211 is rotatably supported in the bearing 22 along the axial direction, and external splines are machined on the outer circle of the input end of the spline shaft 211 for connecting with a power input device. The connecting shaft 212 is in the shape of a hollow cylinder. One end of it is fixedly sleeved on the outer circle of the output end of the spline shaft 211 through a connecting member 213, and internal splines are provided on the inner wall of the other opposite end for connecting with a test piece; the connecting member 213 includes a pressing plate and a locking screw. The pressing plate is pressed against the step surface in the inner cavity of the connecting shaft 212, and the connecting shaft 212 and the spline shaft 211 are locked and fixed through the locking screw passing through the pressing plate and the spline shaft 211. With this structural arrangement of the torque transmission shaft 21, while stably and effectively transmitting torque, it can also be connected to different test pieces by replacing the connecting shafts 212 of different structural types. At the same time, the structural strength of the spline shaft 211 is ensured, and the structure of the torque transmission shaft 21 is simple and easy to machine.

[0036] In this alternative solution, as Figure 4 shown, the first end cover member 32 includes a first labyrinth ring 321 for sealing and a first limiting end plate 322. The first labyrinth ring 321 is installed on the outer circle of the input end of the spline shaft 211, and the inner side end abuts against the corresponding side of the bearing 22 for limiting. The first limiting end plate 322 is sleeved on the outer circle of the first labyrinth ring 321, abuts against the outer side end of the first labyrinth ring 321 for limiting, and the first limiting end plate 322 is detachably fixed to the bearing seat main body 31 through a pressing screw 323. In this alternative solution, the first labyrinth ring 321 is used to seal oil through the labyrinth teeth in an oil supply and rotation environment, thus effectively preventing the lubricating oil from leaking out through the gap between the first limiting end plate 322 and the torque transmission shaft 21; the first limiting end plate 322 is used to block the oil passage during the test process to avoid oil leakage, and at the same time axially limit the first labyrinth ring 321, thereby positioning the corresponding bearing. The structural arrangement is simple and has the functions of blocking oil leakage and axial positioning at the same time.

[0037] In this alternative solution, as Figure 4As shown, the second end cover member 33 includes a second labyrinth ring 331 for sealing, a disc spring 332 for applying an initial pressure to the bearing 22, and a second limiting end plate 333. The second labyrinth ring 331 is installed on the outer circumference of the output end of the spline shaft 211, and its inner end abuts against the corresponding side of the bearing 22 for limiting, and its opposite outer end abuts against the end of the connecting shaft 212 for limiting. The disc spring 332 and the second limiting end plate 333 are respectively installed on the outer circumference of the second labyrinth ring 331, and the disc spring 332 is located between the corresponding side of the bearing 22 and the second limiting end plate 333, and the second limiting end plate 333 is detachably fixed to the bearing housing main body 31 by a compression screw 323. In this alternative solution, the second labyrinth ring 331 is used to seal oil through the labyrinth teeth in the oil supply and rotation environment, so as to effectively prevent the lubricating oil from leaking out through the gap between the second limiting end plate 333 and the torque transmission shaft 21; the second limiting end plate 333 is used to block the oil passage during the test to avoid oil leakage, and at the same time axially limit the disc spring 332, so that the disc spring 332 applies an initial axial force to the corresponding side bearing, ensuring the effective assembly and reliable operation of the bearing. This structure is simple, and at the same time has the functions of blocking oil leakage and axial positioning. Further, as Figure 4 shown, the second end cover member 33 further includes a second adjusting pad 36, which is arranged between the end faces of the second limiting end plate 333 and the bearing housing main body.

[0038] Optionally, as Figure 4 shown, the lubricating oil path structure 40 includes a lubricating oil path 41 arranged in the bearing housing main body 31 and the first limiting end plate 322, an oil path inlet and an oil path outlet opened on the bearing housing main body 31 and connecting the lubricating oil path 41, an oil supply nozzle 42 connected to the oil path inlet, an oil return nozzle 43 connected to the oil path outlet, and an oil injection ring 44. The oil injection ring 44 is sleeved on the outer circumference of the second labyrinth ring 331 and is limited between the disc spring 332 and the corresponding side of the bearing 22. The lubricating oil path 41 communicates with the two end faces of the bearing housing main body 31, and the bearing 22, the first labyrinth ring 321, the second labyrinth ring 331 and the oil injection ring 44. During operation, oil is supplied through the oil supply nozzle 42, and the supplied oil reaches the first end cover member 32 and the oil injection ring 44 through the lubricating oil path 41. The lubricating oil paths 41 of the first end cover member 32 and the oil injection ring 44 supply oil to the corresponding side of the bearing 22 respectively, ensuring the effective lubrication and reliable operation of the bearing 22, and the oil supply returns by gravity and finally reaches the oil return nozzle 43 and flows into the tester. The structure of the lubricating oil path structure 40 is simple, and the bearing in the bearing housing is effectively lubricated and operates reliably.

[0039] Optionally, as Figure 2 and Figure 5As shown in the figure, the rotor test device further includes an acceleration sensor 50 for measuring the vibration acceleration during the test, and a temperature sensor 60 for monitoring the working temperature of the bearing 22. The acceleration sensor 50 is arranged on the test support 10; in this alternative solution, an M5 threaded hole is designed on the top surface of the test support 10 for installing the vibration acceleration sensor in the vertical direction of the test support 10 during the test. At the same time, threaded holes are arranged on the two opposite sides of the test support 10 to install the vibration acceleration sensor for monitoring the vibration acceleration parameters during the test. In the present invention, two types of vibration acceleration sensors, namely vertical and horizontal, are designed, and their main function is to monitor the vibration acceleration value of the support during the test to make the monitoring results more accurate. The temperature sensor 60 is arranged on the bearing seat main body 31. In this alternative solution, the bearing seat main body 31 is designed with a compression bolt for pressing the temperature sensor 60 for respectively monitoring the temperature of the outer ring of the bearing during the test.

[0040] The above are only the preferred embodiments of the present invention and are not intended to limit the present invention. For those skilled in the art, the present invention can have various modifications and changes. Any modifications, equivalent replacements, improvements, etc. made within the spirit and principle of the present invention shall be included within the protection scope of the present invention.

Claims

1. A rotor test device for avoiding harmful resonance frequencies at high rotational speeds, characterized in that, Comprising: A test support (10) for avoiding the harmful resonance frequency at high rotational speeds of the rotor test device, a torque transmission shaft member (20) for stably transmitting power torque, and a bearing housing assembly (30) for mounting and supporting the torque transmission shaft member (20); The test support (10) is a solid triangular structure for detachably fixing to the test platform, and an installation through hole (101) vertically penetrating the plate surface is provided at the upper end of the test support (10); The bearing housing assembly (30) is axially fixedly installed in the installation through hole (101). A bearing housing hole (301) axially penetrating the bearing housing assembly (30) is provided at the end face of the bearing housing assembly (30). The torque transmission shaft member (20) is rotatably installed axially in the bearing housing hole (301). The input end of the torque transmission shaft member (20) extending out of the bearing housing hole (301) is used to be connected to the power input device, and its opposite output end extends out of the bearing housing hole (301) and is used to be connected to the test piece; A lubricating oil path structure (40) for lubricating the torque transmission shaft member (20) is further provided in the bearing housing assembly (30) to enable the torque transmission shaft member (20) to stably and reliably transmit power and torque; The test support (10) is an integrally formed structure; at each of the two lower bottom corners of the test support (10), a lifting ring threaded hole (102) recessed for installing a lifting ring and an installation threaded hole (103) vertically penetrating the lower bottom corner and for installing and fixing a fastener of the test support (10) are provided; the lower bottom edge of the test support (10) is recessed so that the relatively convex lower bottom surface forms a supporting bottom surface (104) for supporting and positioning the test support (10); The bearing housing assembly (30) includes a hollow cylindrical bearing housing main body (31), and a first end cover member (32) and a second end cover member (33) respectively provided at both ends of the bearing housing main body (31); the installation through hole (101) is a stepped hole axially provided. A limiting flange (311) protrudes from the second end of the bearing housing main body (31). The bearing housing main body (31) is axially installed in the installation through hole (101), and the limiting flange (311) abuts against the first limiting step (105) of the stepped hole for limiting. The second end of the bearing housing main body (31) is detachably fixed to the limiting flange (311) by fastening screws (34) sequentially provided in the circumferential direction; the central hole of the bearing housing main body (31) forms the bearing housing hole (301), and the first end cover member (32) and the second end cover member (33) are respectively installed on the outer circles of the input end and the output end of the torque transmission shaft member (20), and the first end cover member (32) and the second end cover member (33) are respectively detachably fixed to the bearing housing main body (31) for axially positioning the torque transmission shaft member (20) and sealing both ends of the bearing housing hole (301).

2. The rotor test device for avoiding the harmful resonance frequency at high rotational speeds according to claim 1, wherein The bearing housing assembly (30) further includes a first adjusting pad (35) for adjusting the axial installation position of the bearing housing main body (31) relative to the test support (10); The first adjusting pad (35) is installed on the outer circle of the bearing seat body (31) and is located between the limiting flange (311) and the first limiting step (105).

3. The rotor test device for avoiding harmful resonance frequencies at high speeds according to claim 1, characterized in that The torque transmission shaft member (20) includes a torque transmission shaft (21) axially passing through the bearing seat hole (301), and bearings (22) installed on the outer circles of the input end and the output end of the torque transmission shaft (21); The input end of the torque transmission shaft (21) extending out of the bearing seat hole (301) is used to connect the power input device, and the opposite output end is used to connect the test piece, and second limiting steps for positioning are respectively provided on the outer circles of the input end and the output end of the torque transmission shaft (21); The bearings (22) are located in the bearing seat hole (301), and the inner ends of the bearings (22) are abutted and limited against the corresponding second limiting steps, and the opposite outer ends are abutted and limited against the corresponding first end cover member (32) or the second end cover member (33).

4. The rotor test device for avoiding harmful resonance frequencies at high speeds according to claim 3, characterized in that The torque transmission shaft (21) includes a spline shaft (211) for transmitting torque and a connecting shaft (212); The spline shaft (211) is axially rotatably supported in the bearing (22), and external splines are machined on the outer circle of the input end of the spline shaft (211) for connecting with the power input device; The connecting shaft (212) is in the shape of a hollow cylinder, one end of which is fixedly sleeved on the outer circle of the output end of the spline shaft (211) through a connecting member (213), and internal splines are provided on the inner wall of the opposite end for connecting with the test piece.

5. The rotor test device for avoiding harmful resonance frequencies at high speeds according to claim 4, characterized in that The first end cover member (32) includes a first labyrinth ring (321) for sealing and a first limiting end plate (322); The first labyrinth ring (321) is installed on the outer circle of the input end of the spline shaft (211), and the inner end abuts against the corresponding bearing (22) for limiting; The first limiting end plate (322) is sleeved on the outer circle of the first labyrinth ring (321), abuts against the outer end of the first labyrinth ring (321) for limiting, and the first limiting end plate (322) is detachably fixed to the bearing seat body (31) through a compression screw (323).

6. The rotor test device for avoiding harmful resonance frequencies at high speeds according to claim 5, characterized in that The second end cover member (33) includes a second labyrinth ring (331), a disc spring (332) for applying an initial pressure to the bearing (22), and a second limiting end plate (333); The second labyrinth ring (331) is installed on the outer circle of the output end of the spline shaft (211), and its inner end abuts against the corresponding bearing (22) for limiting, and the opposite outer end abuts against the end of the connecting shaft (212) for limiting; The disc spring (332) and the second limiting end plate (333) are respectively installed on the outer circle of the second labyrinth ring (331), and the disc spring (332) is located between the corresponding bearing (22) and the second limiting end plate (333), and the second limiting end plate (333) is detachably fixed to the bearing housing body (31) by a compression screw (323).

7. The rotor test device for avoiding harmful resonance frequencies at high speeds according to claim 6, wherein The lubricating oil path structure (40) includes a lubricating oil path (41) provided in the bearing housing body (31) and the first limiting end plate (322), an oil path inlet and an oil path outlet opened on the bearing housing body (31) and connecting the lubricating oil path (41), an oil supply nozzle (42) connected to the oil path inlet, an oil return nozzle (43) connected to the oil path outlet, and an oil injection ring (44); The oil injection ring (44) is sleeved on the outer circle of the second labyrinth ring (331) and is limited between the disc spring (332) and the corresponding bearing (22); The lubricating oil path (41) communicates with the two end faces of the bearing housing body (31), and the bearing (22), the first labyrinth ring (321), the second labyrinth ring (331) and the oil injection ring (44).

8. The rotor test device for avoiding harmful resonance frequencies at high speeds according to claim 3, wherein The rotor test device further includes an acceleration sensor (50) for measuring the vibration acceleration during the test, and a temperature sensor (60) for monitoring the working temperature of the bearing (22); The acceleration sensor (50) is provided on the test support (10); The temperature sensor (60) is provided on the bearing housing body (31).

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