A pipeline equivalent test apparatus and test method

Abstract

This invention provides a pipeline equivalent testing device and method, relating to the field of engine testing technology. The testing device includes a sleeve, a base, a central shaft hinged at one end to the base, and at least one annular counterweight fitted onto the central shaft. The base is rotatably mounted on the sleeve, which connects the base to an accessory interface. The counterweight includes at least one mass ring, one of which is fitted onto the central shaft. When the counterweight includes multiple mass rings, one of two adjacent mass rings is fitted onto the outer circumferential surface of the other mass ring. The pipeline equivalent to this testing device is the pipeline connected to the interface of an external engine accessory, achieving equivalence in mass, polar moment of inertia, and diametrical moment of inertia of the pipeline connected to the accessory, thus satisfying vibration testing of the accessory interface under actual assembly conditions.

Description

Technical Field

[0001] This invention relates to the field of engine testing technology, and in particular to a pipeline equivalent testing device and testing method. Background Technology

[0002] Accessories for aero engines are an important component of the engine system, participating in functions such as engine start-up, operational status control, and fuel / lubricating oil supply. Their assembly boundaries are characterized by multiple interfaces, complex configurations, and diverse structures. Accessories refer to finished components located outside the engine, such as fuel / lubricating oil heat exchangers, fuel pumps, lubricating oil pumps, nozzle afterburner regulators, and afterburner ignition nozzles.

[0003] Since the components operate in a complex vibration environment, vibration tests are required on the components and their connecting pipelines to ensure flight safety, improve system reliability, and save maintenance costs.

[0004] In related technologies, it is difficult to simulate actual assembly conditions by isolating the components from the engine assembly conditions for vibration testing. For example, the components outside the engine are connected to many pipelines, which can affect the modal characteristics of the components as the boundaries of the components. Therefore, isolating the components for vibration testing may result in over-testing or under-testing. Summary of the Invention

[0005] The purpose of this invention is to provide a pipeline equivalent testing device and testing method to solve the technical problem that vibration testing of engine accessories is difficult to simulate actual assembly conditions.

[0006] To achieve the above objectives, the present invention provides the following technical solution:

[0007] In a first aspect, the present invention provides a pipeline equivalent test device, wherein the pipeline is a pipeline connected to an external interface of an engine as an accessory, and the test device includes a sleeve, a base, a central shaft with one end hinged to the base, and at least one annular counterweight sleeved on the central shaft.

[0008] The base is rotatably mounted on the sleeve, and the sleeve is used to connect the base to the interface of the accessory.

[0009] The counterweight includes at least one mass ring, one of which is sleeved on the central shaft;

[0010] When the counterweight includes a plurality of mass rings, in two adjacent mass rings, one mass ring is fitted onto the outer circumferential surface of the other mass ring.

[0011] According to at least one embodiment of the present invention, the sleeve has a rotating cavity section and an opening formed on an end face of the sleeve, the opening communicating with the rotating cavity section;

[0012] The base has a substrate and a protrusion on the substrate. The orthographic projection of the protrusion onto the surface of the substrate is located within the surface of the substrate. The substrate is disposed in the rotating cavity section, and the protrusion matches the opening.

[0013] According to at least one embodiment of the present invention, the base further comprises a first connecting plate disposed on the surface of the protrusion facing away from the substrate;

[0014] The end of the central shaft has a second connecting plate that mates with the first connecting plate;

[0015] The test apparatus also includes locking bolts for fixing the first connecting plate and the second connecting plate, the locking bolts passing through the first connecting plate and the second connecting plate.

[0016] According to at least one embodiment of the present invention, the mass ring sleeved on the central shaft is detachably connected to the central shaft.

[0017] According to at least one embodiment of the present invention, the mass ring sleeved on the central shaft has at least one screw hole, the screw hole extending from the outer circumferential surface of the mass ring to the inner circumferential surface of the mass ring;

[0018] The test apparatus also includes screws that mate with the screw holes.

[0019] According to at least one embodiment of the present invention, when the counterweight includes a plurality of mass rings, in two adjacent mass rings, a first groove is formed on the outer circumferential surface of one mass ring, the first groove extends from one end face of the mass ring to the other end face, and a second groove is formed on the inner circumferential surface of the other mass ring that mates with the first groove.

[0020] The first groove and the corresponding second groove form an axially penetrating assembly hole through the counterweight.

[0021] The equivalent testing device also includes a fixing component that mates with the assembly hole, the fixing component being used to fix two adjacent mass rings.

[0022] According to at least one embodiment of the present invention, the fixing assembly includes a fixing bolt and two wedge blocks with through holes, wherein the size of the larger end of the wedge blocks is larger than the size of the mounting hole;

[0023] The two wedge-shaped blocks are respectively pressed into the assembly hole from both sides by the fixing bolts.

[0024] According to at least one embodiment of the present invention, the wedge block has wedge-shaped surfaces on both opposite sides.

[0025] According to at least one embodiment of the present invention, when the mass ring has both the first groove and the second groove, the phase difference between the first groove and the second groove on the same mass ring in the circumferential direction is 180°.

[0026] According to at least one embodiment of the present invention, the central axis is a hollow axis.

[0027] According to at least one embodiment of the present invention, the sleeve further has an internally threaded cavity adjacent to the rotating cavity section, wherein when the internally threaded cavity section is connected to the interface, the interface fixes the substrate in the rotating cavity section.

[0028] According to at least one embodiment of the present invention, when there are multiple counterweights, the distance between two adjacent counterweights along the axial direction of the central axis is greater than or equal to zero.

[0029] Secondly, the present invention also provides a pipeline equivalent test method, which uses the equivalent test device described in the first aspect to perform the pipeline equivalent test.

[0030] In one or more technical solutions provided in the exemplary embodiments of the present invention, at least one of the following beneficial effects can be achieved.

[0031] The pipeline equivalent testing device of the exemplary embodiment of the present invention is used to achieve equivalence of the mass characteristics of the assembly under vibration table conditions and actual engine assembly conditions. Specifically, the base is rotatably mounted on the sleeve and can rotate 360°. Simultaneously, the central shaft is hinged to the base and can be adjusted at least 180°. Therefore, the central shaft and the counterweight on the central shaft can be adjusted at any angle within a half-space relative to the sleeve, thereby achieving equivalence of the spatial angle of the polar inertia axis of the pipeline connected to the assembly. By setting different numbers of counterweights on the central shaft, adjusting the axial position of the counterweights on the central shaft, and setting different numbers of mass rings on each counterweight, characteristic parameters of different masses and moments of inertia can be obtained, thereby achieving equivalence of the mass, polar moment of inertia, and diametrical moment of inertia of the pipeline connected to the assembly. The pipeline equivalent testing device of the exemplary embodiment of the present invention meets the different counterweight requirements of the assembly interface of the engine under actual assembly conditions, has a simple structure, low production and maintenance costs, and high feasibility for adjusting mass characteristics. Attached Figure Description

[0032] The accompanying drawings illustrate exemplary embodiments of the invention and, together with the description thereof, serve to explain the principles of the invention. These drawings are included to provide a further understanding of the invention and are incorporated in and constitute a part of this specification.

[0033] Figure 1 This is an isometric structural schematic diagram of a pipeline equivalent test apparatus according to an embodiment of the present invention;

[0034] Figure 2 This is a three-dimensional exploded structural diagram of a pipeline equivalent test device according to an embodiment of the present invention;

[0035] Figure 3 This is an isometric structural diagram of the hinged portion of the base and the central shaft according to an embodiment of the present invention;

[0036] Figure 4 This is a schematic diagram of the rotation angle of the hinged portion of the sleeve, base, and central shaft according to an embodiment of the present invention;

[0037] Figure 5 This is a cross-sectional structural schematic diagram of the base and sleeve according to an embodiment of the present invention;

[0038] Figure 6 This is an isometric structural schematic diagram of a wedge block according to an embodiment of the present invention;

[0039] Figure 7 This is a schematic diagram illustrating the derivation of the polar rotational inertia of the pipeline equivalent test device according to an embodiment of the present invention.

[0040] Figure 8 This is a schematic diagram illustrating the derivation of the diameter rotational inertia of the pipeline equivalent test device according to an embodiment of the present invention.

[0041] Reference numerals: 10, counterweight; 11, mass ring; 111, first groove; 112, second groove; 113, screw hole; 114, screw;

[0042] 20. Central shaft; 22. Second connecting plate;

[0043] 30. Sleeve; 31. Rotating cavity section; 32. Internal threaded cavity section;

[0044] 40. Base; 41. First connecting plate; 42. Protrusion; 43. Base plate;

[0045] 50. Locking bolts;

[0046] 60. Fixing component; 61. Wedge block; 611. Wedge surface; 612. Through hole; 62. Fixing bolt. Detailed Implementation

[0047] In order to make the technical problems, technical solutions and beneficial effects to be solved by the present invention more clearly understood, the present invention is further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present invention and are not intended to limit the present invention.

[0048] Accessories are located outside the aero-engine and participate in engine start-up, operational status control, and fuel / lubricating oil supply. Their assembly boundaries are characterized by multiple interfaces, complex configurations, and diverse structures. Under actual assembly conditions, the interfaces of aero-engine accessories are connected to various pipelines. If vibration testing is to be performed on accessories, they must be isolated and placed on a vibration table for testing. In this case, the accessories cannot be installed with the corresponding pipelines according to actual assembly conditions, which may result in the test response function being larger or smaller than the response function obtained from vibration testing under actual assembly conditions.

[0049] To address the aforementioned issues, the pipeline equivalent testing device provided in the exemplary embodiment of the present invention can be connected to the boundary interface of the assembly, thereby performing equivalent testing on the mass, polar moment of inertia, and diametrical moment of inertia of the pipeline connected to the assembly under actual assembly conditions.

[0050] Figure 1 This is an isometric structural schematic diagram of a pipeline equivalent test apparatus according to an embodiment of the present invention; Figure 2 This is a three-dimensional exploded view of the pipeline equivalent test apparatus according to an embodiment of the present invention. Figure 1 and Figure 2 As shown, the pipeline equivalent test apparatus provided in the exemplary embodiment of the present invention is a pipeline connected to an external accessory interface of the engine. The test apparatus includes a sleeve 30, a base 40, a central shaft 20 with one end hinged to the base 40, and at least one annular counterweight 10 sleeved on the central shaft 20. The base 40 is rotatably mounted on the sleeve 30, and the sleeve 30 is used to connect the base 40 to the accessory interface. The counterweight 10 includes at least one mass ring 11, and one of the at least one mass ring 11 is sleeved on the central shaft 20.

[0051] When the counterweight 10 includes a plurality of mass rings 11, in two adjacent mass rings 11, one mass ring 11 is fitted onto the outer circumferential surface of the other mass ring 11.

[0052] In practical applications, based on the modal characteristics of the assembly under actual assembly conditions, the spatial position between the central shaft 20 and the sleeve 30, the number of counterweights 10, the number of mass rings 11 of each counterweight 10, and the axial position of the counterweights 10 on the central shaft 20 are adjusted. The spatial angle of the polar inertia axis, mass, polar moment of inertia, and diametrical moment of inertia are changed. When adjusting the parameters for the first time, the modal characteristics are calculated using finite element software. Then, the equivalent test device for the pipeline is connected to the base 40 on the corresponding interface of the assembly through the sleeve 30, and a vibration test is performed on the vibration table. Then, the spatial position between the central shaft 20 and the sleeve 30, the number of counterweights 10, the number of mass rings 11 of each counterweight 10, and the axial position of the counterweights 10 on the central shaft 20 are adjusted again until the modal characteristics of the assembly under actual assembly conditions are reproduced. The equivalent test device for the polar inertia axis spatial angle, mass, polar moment of inertia and diametrical moment of inertia of the pipeline connected to the accessories can meet the different counterweight requirements of the engine accessory interface under actual assembly conditions. The pipeline equivalent test device has a simple structure, low cost and high mass adjustability.

[0053] Figure 3 This is an isometric structural diagram of the hinged portion of the base and the central shaft according to an embodiment of the present invention; Figure 4 This is a schematic diagram of the rotation angle of the hinged portion of the sleeve, base, and central shaft according to an embodiment of the present invention; Figure 5 This is a cross-sectional structural schematic diagram of the base and sleeve according to an embodiment of the present invention. Figures 3-5 As shown, in the pipeline equivalent test apparatus provided by the exemplary embodiment of the present invention, the sleeve 30 has a rotating cavity section 31 and an opening formed on the end face of the sleeve 30, the opening communicating with the rotating cavity section 31; the base 40 has a base plate 43 and a protrusion 42 provided on the base plate 43, the orthographic projection of the protrusion 42 on the surface of the base plate 43 is located in the surface of the base plate 43, the base plate 43 is provided in the rotating cavity section 31, and the protrusion 42 matches the opening.

[0054] The base 40 also has a first connecting plate 41 disposed on the surface of the protrusion 42 opposite to the substrate 43; the end of the central shaft 20 has a second connecting plate 22 that cooperates with the first connecting plate 41; the test device also includes a locking bolt 50 for fixing the first connecting plate 41 and the second connecting plate 22, the locking bolt 50 passing through the first connecting plate 41 and the second connecting plate 22.

[0055] In practical applications, the central shaft 20 is hinged to the first connecting plate 41 via the second connecting plate 22. After the first connecting plate 41 is connected to the sleeve 30 via the protrusion 42 and the base plate 43, the sleeve 30 can be fixedly connected to the interface of the accessory. A three-dimensional spherical coordinate system is established at the center of the protrusion 42. The first connecting plate 41 is rotatably disposed in the rotating cavity 31 of the sleeve 30 via the base plate 43. Therefore, the adjustment range of the angle α of the first connecting plate 41 in the XOZ plane is [0, 2π], and the adjustment range of the angle β of the second connecting plate 22 in the XOY plane is [0, π]. The plane containing the first connecting plate 41 is parallel to the plane containing the second connecting plate 22. Based on this, the spatial angle of the polar inertial axis of the central shaft 20 is determined by both α and β. Therefore, any angle between the central shaft 20 and the sleeve 30 in the half-space outside the end face of the sleeve 30 facing the central shaft 20 is adjustable. That is, the angle between the polar inertia axis of the pipeline equivalent device and the interface of the accessory in half space can be adjusted arbitrarily.

[0056] It should be noted that the hinge between the second connecting plate 22 and the first connecting plate 41 is a hinge before the angle is adjusted. Once the angle β between them is adjusted to the correct position, it can be fixed to maintain that angle. When the sleeve 30 is connected to the accessory interface, the end face of the accessory interface extends into the rotating cavity section 31 and abuts against the end face of the base plate 43, while the other end face of the base plate 43 abuts against the inner side of the end plate of the sleeve 30. The diameter of the protrusion 42 is smaller than that of the base plate 43, and it extends outward from the opening of the end plate of the sleeve 30. Thus, the base plate 43 can be fixed in the rotating cavity section 31 after adjusting the rotation angle α. At this point, the spatial angle of the polar inertia axis of the central axis 20 in half-space can be determined, thereby achieving equivalence with the spatial angle of the polar inertia axis of the accessory pipeline.

[0057] like Figure 3 As shown, both the second connecting plate 22 and the first connecting plate 41 have through holes that fit together. The locking bolt 50 can pass through the second connecting plate 22 and the first connecting plate 41 at the top to form a hinged connection. The relative positions of the second connecting plate 22 and the first connecting plate 41 are fixed by using a nut at the bottom to lock the bolt 50.

[0058] like Figure 2As shown, in order to achieve the simulation equivalence of the pipeline equivalent test device and flexibly obtain characteristic parameters with different masses and moments of inertia, the mass ring 11 sleeved on the central shaft 20 is detachably connected to the central shaft 20. That is, the axial position of the entire counterweight 10 on the central shaft 20 can be adjusted. For example, when multiple counterweights 10 are required on the central shaft 20 for equivalence, by adjusting the mass ring 11 sleeved on the central shaft 20, the multiple counterweights 10 arranged along the axial direction of the central shaft 20 can be arranged in an adjacent or spaced manner, that is, the distance between two adjacent counterweights 10 is greater than or equal to zero.

[0059] When the distance between two adjacent counterweights 10 is zero, an equivalent method can be used by making a mass ring 11 with a larger axial width.

[0060] There are several ways to detachably connect the mass ring 11, which is fitted onto the central shaft 20, to the central shaft 20.

[0061] For example, a detachable connection can be formed by keyway bonding or by screw fixing.

[0062] For example, the mass ring 11 sleeved on the central shaft 20 has at least one screw hole 113, which extends from the outer circumferential surface of the mass ring 11 to the inner circumferential surface of the mass ring 11; the test device also includes a screw 114 that mates with the screw hole 113.

[0063] Specifically, the mass ring 11 has three screw holes 113 along its circumference. The screw holes 113 form a through hole from the outer circumferential surface of the mass ring 11 to the inner circumferential surface. The mass ring 11 is fixed to the central shaft 20 by screwing screws 114 into the screw holes 113 and abutting against the central shaft 20. For example, the screw holes 113 are countersunk holes formed on the outer circumferential surface of the mass ring 11, or the screws 114 are screws without large-diameter nuts, and their length is less than or equal to the length of the screw holes 113, so that the screws 114 are completely submerged in the screw holes 113 and do not affect the assembly of the outer mass ring 11.

[0064] For example, the phase difference between the three screw holes 113 on the mass ring 11 is 90°, but it can also be 30°, 60°, 120°, etc.

[0065] For example, the central axis 20 can be a hollow axis.

[0066] like Figure 1 and Figure 2As shown, in the pipeline equivalent test device provided by the exemplary embodiment of the present invention, when the counterweight 10 includes a plurality of mass rings 11, in two adjacent mass rings 11, a first groove 111 is formed on the outer circumferential surface of one mass ring 11, the first groove 111 extends from one end face of the mass ring 11 to the other end face, and a second groove 112 is formed on the inner circumferential surface of the other mass ring 11 that mates with the first groove 111; the first groove 111 and the corresponding second groove 112 form an assembly hole that penetrates the counterweight 10 axially.

[0067] The equivalent test apparatus also includes a fixing component 60 that mates with the assembly hole, the fixing component 60 being used to fix two adjacent mass rings 11.

[0068] For example, a first groove 111 is formed on the outer circumferential surface of the mass ring 11 fitted on the central shaft 20. Specifically, the phase difference between the first groove 111 and the three screw holes 113 in the circumferential direction can be 90°. A second layer mass ring 11 fitted on the outer circumferential surface of the mass ring 11 has a second groove 112 on its inner circumferential surface that mates with the first groove 111. The first groove 111 and the corresponding second groove 112 form an axially penetrating mounting hole through the counterweight 10. The inner and outer layers of mass rings 11 are fixedly connected by the engagement of the fixing component 60 with the mounting hole, thereby facilitating the adjustment and fixation of the mass of the counterweight 10.

[0069] A first groove 111 can be formed on the outer circumferential surface of the second layer mass ring 11, which can cooperate with the second groove 112 of the third layer mass ring 11 sleeved on the second layer mass ring 11, so that the counterweight part 10 can add more mass rings 11. That is, in addition to the mass ring 11 sleeved on the central shaft 20 having a first groove 111, other mass rings 11 in the same counterweight part 10 can simultaneously have a second groove 112 on the inner circumferential surface and a first groove 111 on the outer circumferential surface, so as to facilitate mass adjustment and fixation.

[0070] Figure 6 This is an isometric structural schematic diagram of a wedge block according to an embodiment of the present invention. Figures 1-2 , Figure 6 As shown, the fixing component 60 includes a fixing bolt 62 and two wedge blocks 61 with through holes 612. The size of the larger end of the wedge block 61 is larger than the size of the assembly hole. The two wedge blocks 61 are pressed into the assembly hole from both sides by the fixing bolt 62.

[0071] The assembly hole formed by the first groove 111 and the second groove 112 can be either a cubic hole or a cuboid hole. The following example uses a cubic hole as an illustration. The wedge block 61 has a large end and a small end. The size of the wedge block 61 gradually decreases from the large end to the small end, with the large end being larger than the size of the assembly hole, while the small end can fit into the assembly hole. The small ends of the two wedge blocks 61 are inserted into the assembly hole from both ends. Then, a fixing bolt 62 is used to pass through the through holes 612 of the two wedge blocks 61 and engage with a nut. After applying a preload to the two wedge blocks 61, the two mass rings 11 of the inner and outer layers are fixed through the wedge-shaped surfaces. Since the mass of the fixing component 60 is relatively small compared to the mass of the counterweight 10, it can be ignored in the equivalent process.

[0072] For example, the wedge block 61 may have two or one wedge surface 611. When the wedge block 61 has two wedge surfaces 611, they are respectively disposed on opposite sides of the wedge block 61, such as... Figure 6 As shown.

[0073] When the mass ring 11 has both a first groove 111 and a second groove 112, the phase difference between the first groove 111 and the second groove 112 on the same mass ring 11 in the circumferential direction is 180°. Alternatively, it can be other angles such as 30°, 45°, 60°, 75°, 120°, etc., so that the radial thickness of the mass ring 11 can be thinner, that is, the mass of each mass ring 11 can be smaller. When the counterweight 10 adjusts the mass, the dispersion is smaller and the equivalent result is more accurate.

[0074] Considering the ease of disassembly and assembly between the pipeline equivalent test device and its accessories, such as Figure 5 As shown, the sleeve 30 also has an internally threaded cavity section 32 adjacent to the rotating cavity section 31. When the internally threaded cavity section 32 is connected to the interface, the interface fixes the base plate 43 in the rotating cavity section 31.

[0075] The internal threaded cavity section 32 engages with the external thread of the accessory interface to form a detachable connection. The axial length of the internal threaded cavity section 32 of the sleeve 30 is less than or equal to the axial length of the external thread of the accessory interface, ensuring that when the two are tightened, the end face of the accessory interface can have a preload applied to the base plate 43 to fix it in the rotating cavity section 31.

[0076] Figure 7 This is a schematic diagram illustrating the derivation of the polar rotational inertia of the pipeline equivalent test apparatus according to an embodiment of the present invention. Figure 7 As shown, the inner diameter of the mass ring 11 is set to R1, the outer diameter to R2, the length to L2, the density to ρ, the volume to V2, the mass to m2, and the polar moment of inertia to J. z .

[0077] Volume: V² = πL²(R²)2 -R1 2 ),

[0078] Mass: m2 = ρV2 = ρπL2(R2) 2 -R1 2 ), Formula 1;

[0079] Given a (micro-element) cylinder with an axial width of L2 and an inner-outer diameter difference of dr for mass ring 11, we obtain dm = ρdV = ρ2πrL2dr.

[0080] Polar moment of inertia of mass ring 11:

[0081]

[0082] It should be noted that the axis of rotation of the extreme moment of inertia of the mass ring 11 is the axis of the central axis 20.

[0083] Figure 8 This is a schematic diagram illustrating the derivation of the diameter rotational inertia of the pipeline equivalent test apparatus according to an embodiment of the present invention. Figure 8 As shown, the axial distance from one end face of the mass ring 11 to the end face of the central axis 20 near the base 40 is set as L1, and the axial distance from the other end face of the mass ring 11 to the end face of the central axis 20 near the base 40 is set as L2, where L2 > L1.

[0084] Establish a coordinate system o-xyz with the center of the circle on the end face of the central axis 20 near the base 40 as the origin, and establish a coordinate system o'-x'y'z with the center of the circle on the end face of the mass ring 11 near the base 40 as the origin. Take a small element dm on the cylinder, the distance from dm to the y-axis is r', the distance from the projection point of dm on the xoy plane to the origin is r, the x-coordinate of dm in the o-xyz coordinate system is x, the y-coordinate is y, and the z-coordinate is z. Therefore, we have: r 2 =x 2 +y 2 x = rcosθ, r′ 2 =x 2 +z 2 J y Let m be the moment of inertia of the diameter, ρ be the mass, and ρ be the density.

[0085]

[0086] in

[0087]

[0088] Therefore, the moment of inertia of the diameter of mass ring 11 is:

[0089]

[0090] It should be noted that the axis of rotation of the diameter moment of inertia is a straight line along the radial direction passing through the center of the circle on the end face of the central axis 20 near the base 40.

[0091] As can be seen from the above, the outer diameter R2 and axial width L of the mass ring 11 can be obtained by Equation 1 and Equation 2. By adjusting the number of counterweights 10 and the number of mass rings 11 in the counterweights 10, the equivalent mass and polar rotational inertia of the pipeline can be achieved. Then, by adjusting the axial position of the counterweights 10 on the central axis 20 according to Equation 3, the equivalent diameter rotational inertia can be achieved.

[0092] It should be noted that, in terms of the mass, polar moment of inertia, and diametrical moment of inertia of the pipelines connected to the external accessories of the engine, the mass, polar moment of inertia, and diametrical moment of inertia are linearly additive.

[0093] An exemplary embodiment of the present invention also provides a pipeline equivalent test method, which is applied to the equivalent test apparatus of the above embodiments.

[0094] The target modes of the assembly accessories were tested under actual assembly conditions.

[0095] A preset model of the attachment under actual assembly conditions on the vibration table is established. Then, a parameterized model of the pipeline equivalent test device is added to the preset model. The corresponding initial values ​​of parameters are calculated using finite element method, such as the spatial position between the central shaft 20 and the sleeve 30, the number of counterweights 10, the number of mass rings 11 of each counterweight 10, and the axial position of the counterweights 10 on the central shaft 20.

[0096] Furthermore, the spatial position between the central shaft 20 and the sleeve 30, the number of counterweights 10, the number of mass rings 11 of each counterweight 10, and the axial position of the counterweights 10 on the central shaft 20 are adjusted until the target mode of the accessory under actual assembly conditions is reproduced.

[0097] ε=(ω1-ω 1′ ) 2 +(ω2-ω 2′ ) 2 +…+(ω n -ω n′ ) 2

[0098] Where ω i Let ω be the modal frequency of the i-th mode under actual assembly conditions. 1′ To determine the modal frequency of the i-th order mode obtained from finite element simulation after adjusting the parameters, the parameters are continuously adjusted to minimize ε. For example, by continuously adjusting the parameters, if the error of the modal frequency of each of the first three orders is within 15%, it can be identified as the target mode.

[0099] The technical advantages of the above-mentioned pipeline equivalent test method compared to the prior art are the same as those of the above-mentioned pipeline equivalent test device, and will not be repeated here.

[0100] Those skilled in the art should understand that the above embodiments are merely for illustrating the present invention and are not intended to limit the scope of the invention. Those skilled in the art can make other changes or modifications based on the above disclosure, and these changes or modifications still fall within the scope of the present invention.

Claims

1. A pipeline equivalent test device, characterized in that, The pipeline is an interface connected to the outside of the engine as an accessory. The test device includes a sleeve, a base, a central shaft with one end hinged to the base, and at least one annular counterweight sleeved on the central shaft; wherein the central shaft on the base can be adjusted at least 180°. The base is rotatably mounted on the sleeve and can rotate 360°. The sleeve is used to connect the base to the interface of the accessory. The counterweight includes at least one mass ring, one of which is sleeved on the central shaft; wherein the number of the counterweight and the number of mass rings in each counterweight are adjustable, and the axial position of the counterweight on the central shaft is adjustable.

2. The equivalent test apparatus according to claim 1, characterized in that, The sleeve has a rotating cavity section and an opening formed on the end face of the sleeve, the opening communicating with the rotating cavity section; The base has a substrate and a protrusion provided on the substrate.

3. The equivalent test apparatus according to claim 2, characterized in that, The mass ring fitted on the central shaft is detachably connected to the central shaft.

4. The equivalent test apparatus according to claim 3, characterized in that, The mass ring sleeved on the central shaft has at least one screw hole, which extends from the outer circumferential surface of the mass ring to the inner circumferential surface of the mass ring; The test apparatus also includes screws that mate with the screw holes.

5. The equivalent test apparatus according to claim 4, characterized in that, The wedge block has wedge-shaped surfaces on both opposite sides.

6. The equivalent test apparatus according to claim 5, characterized in that, When the mass ring has both a first groove and a second groove, the first groove and the second groove on the same mass ring have a circumferential phase difference of 180°.

7. The equivalent test apparatus according to claim 6, characterized in that, The sleeve also has an internally threaded cavity section adjacent to the rotating cavity section. When the internally threaded cavity section is connected to the interface, the interface fixes the substrate in the rotating cavity section.

8. The equivalent test apparatus according to claim 6, characterized in that, When there are multiple counterweights, the distance between two adjacent counterweights along the axial direction of the central axis is greater than or equal to zero.

9. A pipeline equivalent test method, characterized in that, The equivalent test apparatus according to any one of claims 1-8 is used to conduct the pipeline equivalent test.

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