A torque plate and an impact test bench having the same

Abstract

This utility model relates to a bidirectional torque plate for an impact testing bench, comprising a torque plate body detachably mounted on a torque limiter under test. The torque plate body has lever arms extending radially to both sides, with each lever arm's end forming a torque-acting end mechanically connected to a force sensor. When the torque limiter under test is subjected to an impact load, the torque plate body tends to rotate clockwise or counterclockwise. When one lever arm applies pressure to the corresponding force sensor through its torque-acting end, the other lever arm applies tension to the corresponding force sensor through its torque-acting end, thus achieving bidirectional measurement of tensile and compressive forces. This utility model improves detection accuracy by canceling out the self-weight of symmetrical torque couples, effectively achieving precise control of the torque transmission path under impact load, thereby enhancing the stability and reliability of torque measurement data.

Description

Technical Field

[0001] This utility model relates to the field of testing device technology, and in particular to a bidirectional torque plate and an impact test bench having the torque plate. Background Technology

[0002] In fields such as mining machinery and aerospace, transmission systems often face sudden impact loads, requiring torque limiting devices for overload protection. This necessitates impact torque testing equipment to determine their dynamic operating capabilities. Currently, traditional torque testing platforms mostly employ a single-sided lever arm or rigid coupling structure, using a motor to drive the tested component to rotate and sensors to directly collect torque data. While this design can achieve basic torque detection, in simulating high-speed impacts or sudden jamming conditions, the single-sided lever arm is prone to measurement deviations due to uneven torque transmission, and it cannot eliminate the mechanical stress concentration problem caused by off-center loading. Furthermore, existing torque plate structures are fixed, making it difficult to adapt to torque limiters of different sizes or installation angles. Changing test components requires overall adjustment of the test bench, resulting in low testing efficiency.

[0003] On the other hand, existing technologies often rely on complex transmission components to connect torque plates to the test piece, resulting in cumbersome installation processes and a lack of rapid positioning structures, which can easily introduce assembly errors. While some solutions increase torque capacity by adding motor power or large brakes, this leads to bulky equipment and a surge in energy consumption, making it difficult to meet the needs of compact testing scenarios. Furthermore, the lever arm structure of traditional torque plates is mostly designed with a uniform cross-section, which is prone to impact fracture due to stress concentration under dynamic impact, or damage from plastic deformation and fatigue fracture due to repeated impacts, affecting test reliability.

[0004] CN114295266A discloses a dynamic impact torque simulation test bench, which uses a combination of a flywheel and a hydraulic clutch to utilize rotational inertia to represent the output of a large electric motor. The test bench's fixture plate 16 features a single-sided limiting design, meaning one end is locked and the other contacts the sensor. However, this single-sided design causes torque fluctuations at the sensor location due to the impact load generated by the rotational inertia when the clutch suddenly engages. Furthermore, repeated use can easily deform the single-arm fixture plate 16, and the asymmetrical design makes it more prone to installation tolerances. The cumulative error resulting from this affects the test torque and consequently the measurement accuracy. In addition, this technical solution relies on pressure sensors and encoders, only supporting unidirectional torque detection, making it difficult to adapt to more complex testing requirements.

[0005] Therefore, there is an urgent need for a testing device that can take into account dynamic impact simulation, bidirectional torque measurement, and rapid adaptability, in order to solve the problems of torque transmission deviation, structural redundancy, and insufficient adaptability to working conditions in the existing technology, and to provide technical support for the reliability verification of torque limiting devices.

[0006] Furthermore, on the one hand, there are differences in understanding among those skilled in the art; on the other hand, the applicant studied a large number of documents and patents when making this utility model, but due to space limitations, not all details and contents were listed in detail. However, this does not mean that this utility model does not have the features of these prior art. On the contrary, this utility model has all the features of the prior art, and the applicant reserves the right to add relevant prior art to the background art. Utility Model Content

[0007] In view of the shortcomings of the prior art, this application proposes a bidirectional moment plate for impact test bench, and in particular a moment plate with a bilateral symmetrical lever arm, which aims to solve one or more technical problems in the prior art.

[0008] This utility model relates to a bidirectional torque plate, comprising a torque plate body detachably mounted on a torque limiter under test. The torque plate body has lever arms extending radially to both sides, each lever arm ending in a torque-acting end mechanically connected to a force sensor. When the torque limiter under test is subjected to an impact load, the torque plate body exhibits a clockwise or counterclockwise rotation tendency. Specifically, when one lever arm applies pressure to the corresponding force sensor through its torque-acting end, the other lever arm applies tension to the corresponding force sensor through its torque-acting end, thus achieving bidirectional measurement of tensile and compressive forces. The rotation tendency here should be broadly understood, because at a microscopic level, the torque plate body certainly experiences a small displacement under a large impact load, thereby generating a force on the force sensor. However, those skilled in the art will understand that the clockwise or counterclockwise rotation tendency described in this utility model includes this small displacement.

[0009] This utility model's torque plate body employs a combined pressure and tension measurement method, achieving simultaneous bidirectional torque monitoring. This overcomes the systematic errors caused by installation tolerances and aging testing equipment inherent in traditional torque measurement devices such as impact test benches. This is because when an impact load is applied to the torque plate body, the tension and pressure forces borne by the equal-arm double arms should be a pair of equal and opposite resultant forces (for non-equal arms or double-arm angles not exceeding 180°, the proportional relationship between tension and pressure can be clearly determined due to known geometric relationships). Therefore, when the difference or ratio between tension and pressure exceeds a preset range, it can be inferred that certain transmission components of the impact test bench or the torque limiter under test have installation tolerances exceeding expectations, or that the torque plate or transmission shaft of the impact test bench is deformed. This provides a simple and effective solution for accurate torque measurement under impact loads. The torque plate body integrally forms the lever arm, creating a unified force transmission path and ensuring high-fidelity torque data transmission. The double-sided distributed lever arm structure gives the device self-balancing characteristics and can also counteract external interference torques in non-measuring directions, improving measurement stability under complex working conditions. Meanwhile, this structure does not rely on complex transmission mechanisms or electrical compensation systems, which simplifies the mechanical layout and enhances the environmental adaptability of the equipment. It is especially suitable for the real-time monitoring of dynamic torque under high impact and large load alternating conditions. In particular, under environmental vibration interference, the double-arm lever helps to easily eliminate unqualified data from repeated measurements.

[0010] According to a preferred embodiment, the torque plate body has its inner annular hole formed in such a way that the inner annular hole is located at the root of the two lever arms, and its center forms the rotation center of the two lever arms and coincides with the rotation axis of the torque plate body. The first drive shaft for transmitting the test load extends through the inner annular hole via the torque limiter under test. The drive shaft and the inner annular hole maintain a distance from each other, ensuring rotational freedom while effectively avoiding eccentric moments through the coincident axis design, ensuring that the impact load is accurately transmitted to the torque plate body along a preset annular path. Furthermore, after passing through the torque limiter under test and extending through the inner annular hole, the first drive shaft remains within a bearing housing, which is spaced apart from the torque plate body, providing stable axial constraint for the drive shaft.

[0011] According to a preferred embodiment, the torque plate body has a plurality of bolt holes arranged in a ring around the outer periphery of the inner ring hole. The spatial arrangement of the bolt holes forms a positioning fit with the pre-set positioning holes of the torque limiter under test. These bolt holes collectively form an installation ring that serves as a "ring-shaped force path for transmitting the test load from the torque limiter under test to the torque plate body." The axial constraint method of the bolt connection ensures the fixation of the torque plate body under impact loads and, through its detachable design, meets the flexibility requirements for equipment maintenance and adaptation to different models of torque limiters. The evenly distributed ring-shaped bolt hole layout creates a symmetrical distribution of constraint forces, effectively suppressing the asymmetrical stress concentration problem caused by installation misalignment and ensuring that the rotation center of the torque plate body is strictly aligned with the axis of the torque limiter.

[0012] According to a preferred embodiment, a stop ring surrounding an inner annular hole is provided on the distal end face of the torque plate body. The stop ring and the corresponding mating structure of the torque limiter under test form a shape-fit connection for mutual installation positioning of the torque limiter under test and the stop ring. Before the bolts are tightened, the annular groove structures of the two form a temporary constraint through mechanical interlocking, which can effectively eliminate axial offset and angular deviation during assembly, ensuring that the rotation center of the torque plate body and the axis of the torque limiter are quickly and accurately aligned. This structure completes the radial degree of freedom constraint before the bolts are pre-tightened, significantly reducing the positioning error caused by manual adjustment during installation, and at the same time, the uniformly distributed support of the annular contact surface offsets the asymmetrical assembly stress.

[0013] According to a preferred embodiment, the stop ring is located in the radial region between the mounting ring formed by the bolt holes and the inner ring hole, wherein the radial distance between the stop ring and the opening of the inner ring hole (especially the radial inner wall) is smaller than the radial distance between the stop ring and the mounting ring. The placement of the stop ring close to the inner ring hole preferentially strengthens the local stiffness of the force transmission core area, disperses circumferential stress, and avoids fatigue cracks caused by stress concentration at the bolt hole edges. This design maintains the high-precision positioning function of the stop ring and the countersink while giving the torque plate body radial bending toughness, ensuring the stability of dynamic torque measurement and improving the service life of the device under alternating impact loads.

[0014] According to a preferred embodiment, the bolt holes can be either through-holes or blind holes on one side. These bolt holes transmit the rotational test load, transmitted from the first drive shaft to the torque limiter under test, along the mounting ring to the torque plate body. Depending on the direction of the rotational test load transmitted from the first drive shaft, the torque plate body can exhibit a clockwise or counterclockwise rotation tendency. By providing both through-hole and blind hole structures, assembly requirements for different installation scenarios can be accommodated. When space is limited on the test bench, the blind hole structure prevents bolts from penetrating the entire torque plate body, reducing axial space occupation.

[0015] According to a preferred embodiment, the two lever arms extending radially to both sides form an angle of 90° to 180° with each other, and / or the two lever arms have the same lever arm length or have lever arm lengths in a predetermined proportional relationship. When the angle between the two lever arms is 180° (symmetrical distribution), complete balance measurement of bidirectional torque can be achieved, suitable for scenarios requiring high-precision symmetrical detection; when the angle is adjusted to 90° (orthogonal distribution), the radial space occupation of the device can be significantly reduced, adapting to the layout requirements of compact test benches (see Appendix). Figure 9 Furthermore, by setting the lever arm length ratio (e.g., 1:2), the measurement sensitivity of unilateral impact loads can be specifically optimized. For example, when the right lever arm is extended to twice its length, its torque amplification effect can improve the accuracy of capturing the impact energy on the right side, while maintaining system stability through the reference action of the left lever arm (see the description of asymmetric lever arms in Example 1). The preferred equal-length lever arm (1:1) design cancels out the interference torque in the non-measurement direction through self-balancing characteristics, significantly improving the measurement stability under dynamic impact.

[0016] According to a preferred embodiment, the mounting ring, inner ring hole, and stop ring of the torque plate body form concentric circles with a common center, wherein the center constitutes the rotation center of the two lever arms. The triple concentric circle structure (mounting ring, inner ring hole, and stop ring) ensures strict alignment between the torque plate body and the rotation axis of the torque limiter under test by sharing a common center, helping to easily control assembly eccentricity errors to a very small range. Furthermore, the concentric circle design allows impact loads to be evenly transmitted along the annular path, avoiding stress concentration at the bolt hole edges and significantly reducing local stress peaks. Additionally, the stop ring and the groove structure of the torque limiter under test achieve pre-positioning through shape matching, significantly improving the alignment efficiency of the bolt hole and the positioning hole, while eliminating angular deviations through the uniform support of the annular contact surface.

[0017] According to a preferred embodiment, the torque-acting end is provided with a mating hole, and the force sensor is mechanically connected to the torque plate body via a hinge to the mating hole. Through the combined design of the mating hole and the hinge structure, the force sensor can adaptively adjust its connection posture within a certain angular range.

[0018] According to a preferred embodiment, the torque-acting end is a plate-shaped structure integrally connected to the torque plate body. The continuity between the integrally formed plate-shaped torque-acting end and the body structure ensures higher structural integrity of the load transmission path, thereby significantly improving the fatigue resistance of the interface between the lever arm end and the force sensor.

[0019] This utility model also relates to an impact test bench, which is equipped with the aforementioned torque plate, including a base and a first drive shaft, a second drive shaft and a clutch located above the base. The clutch is disposed between the second drive shaft and the first drive shaft. When the clutch is engaged, the second drive shaft transmits torque to the first drive shaft.

[0020] The clutch engagement switching enables the second drive shaft to transmit controllable torque to the first drive shaft. Combined with the bidirectional lever arm structure of the torque plate, it facilitates the capture of the dynamic response characteristics of the torque limiter under both forward and reverse impacts. The dual-shaft layout supported by the base optimizes the straightness of the power transmission path, reducing torque loss and vibration interference caused by shaft misalignment. Simultaneously, the axial alignment design of the clutch and drive shaft ensures that the impact load is stably transmitted to the torque plate along a preset path. The integrated structure gives the test bench both high load impact capability and dynamic measurement accuracy. The modular torque plate mounting mechanism supports the overall disassembly and assembly of the torque limiter under test, connecting components, and symmetrical torque plates, enabling rapid replacement and significantly improving testing efficiency.

[0021] According to a preferred embodiment, the base is provided with a linear slide rail whose axial extension direction is the same as that of the central axis of the second drive shaft or the first drive shaft. The force sensor is slidably mounted on the slide rail. The force sensor can be adjusted by axial displacement along the slide rail to ensure that the detection end of the force sensor and the torque action end are in positional correspondence, thereby adapting to torque limiters of different axial thicknesses.

[0022] The sliding adjustment mechanism allows the detection end to quickly match the spatial position of the torque application end according to the thickness variation of different torque limiters, maintaining the linearity of the pressure or tension transmission path and improving the test bench's compatibility with different specifications of torque limiters through axial degree of freedom. The guiding characteristics and position locking function of the slide rail effectively suppress the vibration displacement of the sensor bracket during dynamic impact testing, ensuring the stability of the measurement contact point under high load conditions. Attached Figure Description

[0023] Figure 1 This is a schematic diagram of the overall structure of a preferred bidirectional torque plate of this utility model installed on a test bench from a first-view perspective.

[0024] Figure 2 This is a schematic diagram of the overall structure of a preferred bidirectional torque plate of this utility model installed on a test bench from a second perspective.

[0025] Figure 3 This is a schematic diagram of the overall structure of the test bench of this utility model, wherein the bidirectional torque plate is omitted in order to facilitate observation of the torque limiter to be tested that is blocked by it;

[0026] Figure 4This is a schematic diagram of the frontal view of a preferred bidirectional torque plate of this utility model after it has been removed from the test bench and is viewed along the drive shaft.

[0027] Figure 5 This is a schematic diagram of the frontal view of a preferred bidirectional torque plate of this utility model installed on a test bench, observed along the transmission shaft.

[0028] Figure 6 This is a schematic diagram of the near-end view of a preferred torque plate body according to this utility model;

[0029] Figure 7 This is a schematic diagram of the far end view of a preferred torque plate body of this utility model;

[0030] Figure 8 This is a schematic diagram of the near-end face of a torque plate body with different selectable lever arm lengths according to this utility model.

[0031] Figure 9 This is a schematic diagram of the near-end face of a torque plate body with mutually perpendicular lever arms, which is an optional feature of this utility model.

[0032] List of reference numerals

[0033] 100: Base; 230: Second drive shaft; 240: Clutch; 250: Torque limiter to be tested; 251: Sinking platform; 260: First drive shaft; 270: Bearing housing; 300: Torque plate body; 300a: Near end face of torque plate; 300b: Far end face of torque plate; 301: First reference line; 302: Second reference line; 303: Third reference line; 304: Vertex of torque plate; 305: 306: First oblique cross line; 310: Lever arm; 311: Edge; 320: Inner ring hole; 321: Inner ring feature point; 322: Center; 330: Stop ring; 340: Bolt hole; 341: Mounting ring; 350: Torque application end; 350a: Top edge; 351: Mating hole; 352: Connection point; 353: End midpoint; 400: Force sensor; 410: Slide rail. Detailed Implementation

[0034] The present invention will now be described in detail with reference to the accompanying drawings.

[0035] Location definition: combined with Figure 1 When viewed along the axis of the first drive shaft 260 or the second drive shaft 230, the end closest to the torque plate body 300 is the proximal end, and the other end is the distal end. Figure 6 The image shown is the near end face 300a of the moment plate body 300 facing the near end; Figure 7 The image shows the far end face 300b of the torque plate body 300 facing the far end.

[0036] Example 1

[0037] This embodiment relates to a bidirectional moment plate for an impact testing bench, the main body of which is a plate-shaped moment plate body 300. Figure 1 and Figure 2 The installation position of the moment plate body 300 in the impact test bench is shown. The moment plate body 300 has two end faces, of which the face facing the proximal end is the moment plate proximal end face 300a (e.g., Figure 6 As shown), the side facing the far end is the far end face 300b of the moment plate (as shown). Figure 7 (As shown). Combined Figure 2 The distal end face 300b of the torque plate body 300 is connected to the torque limiter 250 to be tested, which is mounted on the impact test bench, so that the torque plate body 300 can receive the torque transmitted by the torque limiter 250. Figure 1 As shown, the torque limiter 250 under test is mechanically connected to a clutch 240 for controlling torque output via a first drive shaft 260 arranged along its axis. The input end of the clutch 240 is connected to a drive motor and an inertial flywheel (see...). Figure 2 When the clutch 240 is engaged, the impact torque at its output end is transmitted to the torque plate body 300 via the torque limiter 250, causing the torque plate body 300 to rotate. The actual transmitted force can then be measured using force sensors 400 located at both ends of the torque plate body 300. The rotation of the torque plate body 300 is not a macroscopically visible movement, but rather a minute angular displacement caused by the impact torque.

[0038] like Figure 2 As shown, the motor drives the inertial flywheel to rotate and can transmit the load to the first drive shaft 260 via the clutch 240. Since the first drive shaft 260 is fixed to the torque limiter 250 under test, the torque limiter 250 under test will absorb all the impact load, which is the rotational load from the first drive shaft 260. The first drive shaft 260 passes through the torque limiter 250 under test and is fixed to the bearing housing 270 on its other side (see...). Figure 3 ).

[0039] In such Figure 6 In the embodiment of the torque plate body 300 with a fully symmetrical design, the center of the torque plate body 300 has an inner annular hole 320 that extends through the entire thickness. The center 322 of the inner annular hole 320 is approximately coincident with the rotation axis of the torque plate body 300. Centered on the center 322 of the inner annular hole 320, the torque plate body 300 can extend two lever arms 310 radially to both sides, such as... Figure 1 and Figure 9As shown. The outer wall of the inner ring hole 320 also forms the root of the two lever arms 310, and a torque-acting end 350, which is mechanically connected to the force sensor 400, is formed at the other end of the two lever arms 310 opposite to the inner ring hole 320. The torque-acting end 350 can be, for example, a plate-like structure integrally connected to the torque plate body 300.

[0040] like Figure 6 As shown, with the lever arms 310 on both sides of the torque plate body 300 designed to be fully symmetrical, an imaginary first reference line 301 extends from the center 322 of the inner ring hole 320 along the length of the lever arm 310. This first reference line 301 passes through the midpoint 353 of the end of the torque application end 350. The torque plate body 300 also forms an imaginary third reference line 303 by passing radially through the two torque plate vertices 304 (the positions with the largest cross-sectional width of the torque plate body 300). Figure 6 In the fully symmetrical design shown, the third reference line 303 also forms the boundary line between the two lever arms 310, which extend to both sides with the third reference line 303 as the boundary. Thus, when a rotational tendency is generated under the action of impact load, the torque-acting ends 350 at their ends apply forces of equal magnitude but opposite direction toward the sensor.

[0041] See Figure 6 The third baseline 303 intersects the outline of the inner ring hole 320 to form two inner ring feature points 321, passing through the end midpoint 353 and intersecting with either of the inner ring feature points 321. Figure 6 The selected inner ring feature point 321 can form an imaginary first oblique crossing line 305. An angle α is formed between the first reference line 301 and the first oblique crossing line 305. The first oblique crossing line 305 defines the load transfer direction of the lever arm 310, and its angle α affects the stress distribution at the root of the lever arm 310. This angle α ranges from 0 to 30°, preferably from 5 to 20°, and more preferably from 10 to 15°. Figure 6 When the lever arms 310 on both sides of the torque plate body 300 are designed to be fully symmetrical, the edges 311 on both sides of the lever arms 310 intersect with the two top edges 350a of the torque action end 350 to form two connection points 352. Figure 6 An imaginary second reference line 302, parallel to the first reference line 301, extends along the length of the lever arm 310 from the connection point 352 located above the first reference line 301. The second reference line 302 is also orthogonal to the third reference line 303. Figure 6As shown, an imaginary second oblique span 306 is formed between the aforementioned connection point 352 and the moment plate vertex 304, which is also located above the first reference line 301. An angle β is formed between the second oblique span 306 and the second reference line 302. The angle β defines the load direction of the second oblique span 306, and the angle β ranges from 0 to 30°, preferably from 5 to 20°, and more preferably from 10 to 15°. Preferably, the included angles α and β can be configured to have the same angle value, so that the equivalent cross-sectional area of ​​the lever arm 310 is consistent, thereby optimizing the stress uniformity under bidirectional impact loads and reducing the risk of local fatigue damage.

[0042] like Figure 7 As shown, a stop ring 330 surrounding the inner ring hole 320 is provided on the distal end face 300b of the torque plate body 300. This stop ring 330 can be used to position itself relative to the torque limiter 250 under test. For example, when the torque plate body 300 is assembled with the torque limiter 250 under test, in order to align the torque plate body 300 and the torque limiter 250 under test, the stop ring 330 and the corresponding mating structure of the torque limiter 250 under test can be mated together in a form-fit manner.

[0043] According to a preferred embodiment, such as Figure 7 As shown, the stop ring 330 can be configured as an annular protrusion structure protruding from the far end face of the moment plate body 300, and the settling platform 251 (see...) Figure 4 The corresponding structure is processed into a matching annular recessed groove, and the two form a mechanical constraint through the concave-convex fit. Furthermore, the annular protrusion of the stop ring 330 relative to the distal end face of the moment plate body 300 serves both to radially position the moment plate body 300 and to form reinforcing ribs at the roots of the two lever arms 310 along the annular force path. Those skilled in the art will understand that the stop ring 330 and the countersink 251 can adopt other concave-convex joint methods to form a geometric fit connection, such as a keyway fit structure, a spline connection structure, a polygonal fit structure, a trapezoidal boss-groove fit, a wave-shaped gear fit structure, a wedge fit structure, or a ball-and-socket fit structure; these all fall within the protection scope of this utility model. Other non-advantageous embodiments, such as changing the concave-convex joint method of the stop ring 330 and the countersink 251 to a form where "the stop ring 330 is concave and the countersink 251 is convex," although not beneficial to structural stability, also fall within the protection scope of this utility model.

[0044] According to a preferred embodiment, such as Figure 7 As shown, the inner ring hole 320 that runs through the center of the torque plate body 300 has several bolt holes 340 distributed in a ring around its periphery, thus forming a ring-shaped force path for the torque plate body 300. The center points of each bolt hole 340 are located on the same circumference to form an installation ring 341 that serves as the ring-shaped force path, allowing the torque to be transmitted along the lever arm 310 to its end.

[0045] Preferably, the central axis of each bolt hole 340 is perpendicular to the distal end face 300b of the torque plate body 300, and its position corresponds to the preset positioning hole of the torque limiter 250 under test. The bolt holes 340 are implemented by means of through bolt holes. Those skilled in the art will know that a single-sided blind hole (not shown in the figure) can also be used. When a blind hole structure is used, its depth can be configured, for example, to be 50-80% of the thickness of the torque plate body 300, and it is axially constrained to the positioning hole of the torque limiter 250 under test by countersunk bolts. When the torque plate body 300 and the torque limiter 250 under test are assembled, the bolt holes 340 and the positioning holes are connected by bolts to achieve axial constraint, so that the torque plate body 300 can be detachably placed on the near end face of the torque limiter 250 under test, avoiding relative displacement with the torque limiter 250 under test.

[0046] like Figure 7 As shown, the bolt hole 340 forming the annular force path is opened along the outer side of the annular stop ring 330. The radial distance between the stop ring 330 and the inner annular hole 320 is less than the radial distance between the stop ring 330 and the mounting ring 341.

[0047] Preferably, the force sensor 400 connected to the torque-acting end 350 at the end of the lever arm 310 can be a bidirectional force sensor capable of measuring both pressure and tension. When the torque limiter 250 under test is subjected to torque, the torque plate body 300 tends to rotate clockwise or counterclockwise, or rotates slightly clockwise or counterclockwise. The force sensors 400 corresponding to each of the two lever arms 310 can measure the pressure or tension generated by the corresponding torque-acting end 350. Figure 5 For example, when the torque plate body 300 rotates clockwise due to a momentary impact on the torque limiter 250 under test, the right lever arm 310 will move closer to its corresponding force sensor 400, causing the force sensor 400 to be under pressure; the left lever arm 310 will move away from its corresponding force sensor 400, causing the force sensor 400 to be under tension. Correspondingly, when the torque plate body 300 rotates counterclockwise due to a momentary impact on the torque limiter 250 under test, the right lever arm 310 will move away from its corresponding force sensor 400, causing the force sensor 400 to be under tension; the left lever arm 310 will move closer to its corresponding force sensor 400, causing the force sensor 400 to be under pressure. The torque plate body 300, with its double-arm structure and bidirectional force sensors configured in conjunction with each arm, can realize bidirectional torque measurement. In particular, when the axial lengths of the two arms 310 are equal, this symmetrically distributed arm structure can achieve self-weight cancellation of symmetrical couples, improve detection accuracy, and effectively optimize the torque transmission path under impact load.

[0048] According to a preferred embodiment, the axial lengths of the two lever arms 310 can be combined in different ways to suit different types of impact loads. For example, when both lever arms 310 are designed with a symmetrical length L, this equal-length structure is suitable for working conditions requiring the balancing of bidirectional impacts. Figure 8 The torque plate body 300 shown has two lever arms 310 of different lengths, left and right. If the left lever arm 310 maintains a length of L while the right one extends to 2L, forming an asymmetrical layout with heavy load on the right side, it can adapt to scenarios where the impact energy on one side is significantly higher. When the left lever arm 310 is extended to 2L and the right one is shortened to L, this arrangement allows the torque plate body 300 to be designed as an asymmetrical structure. By adjusting the length ratio of the two lever arms 310, the gravitational moments of the left and right parts relative to the axis of rotation can be kept balanced. This structure can flexibly adapt to the impact conditions dominated by one side, meeting the impact load testing requirements of different directions and energy levels, and also adapting to the special space constraints of the tested product. By precisely adjusting the lever arm ratio, accurate matching for different dynamic impact load testing scenarios can be achieved.

[0049] like Figure 9 As shown, the two lever arms 310 can be configured in a non-180-degree angle manner. When the test space is limited, the lever arms 310 can be orthogonally arranged to reduce the radial expansion size, while maintaining the mechanical connection between the torque end 350 and the force sensor 400.

[0050] Example 2

[0051] This embodiment is a further explanation of the foregoing embodiment, and repeated content will not be repeated.

[0052] This embodiment relates to an impact test bench equipped with the torque plate described in the foregoing embodiment, such as Figure 1 As shown, it includes a base 100 and a first drive shaft 260, a second drive shaft 230, and a clutch 240 located on the base 100.

[0053] The base 100 serves as the supporting foundation for the entire impact test bench. It adopts a rectangular steel plate welded frame structure, with anchor bolt mounting holes at the four corners of the bottom, and the top surface is machined to form a flat reference surface. Figure 1 , Figure 2As shown, the second drive shaft 230 can form a belt drive connection with the motor via a drive belt. A pair of bearing seats 270 at both ends of the second drive shaft 230 provide stable axial constraint. The first drive shaft 260 and the second drive shaft 230 are coaxially connected via a clutch 240. The first drive shaft 260 extends proximally along its axis and passes through the central hole of the torque limiter 250 under test. The torque limiter 250 under test is connected to the first drive shaft 260 in the axial central region, forming a mechanical transmission chain capable of transmitting torque. For example, under a large impact load, the first drive shaft 260 may also rotate relative to the torque limiter 250 under test by a certain angle.

[0054] like Figure 2 As shown, the base 100 is provided with at least one linear slide rail 410 for mounting a force sensor 400, the extension direction of which is the same as the extension direction of the central axis of the second drive shaft 230 or the first drive shaft 260. The force sensor 400 is slidably mounted on the slide rail 410. Those skilled in the art will understand that the force sensor 400 can be adjusted by axial displacement along the slide rail 410 to ensure that the detection end of the force sensor 400 and the torque application end 350 maintain a corresponding position, thereby adapting to torque limiters 250 with different axial thicknesses. Although two slide rails 410 are shown in the figure, only one slide rail 410 is used to fit... Figure 9 The horizontally arranged lever arm 310 of the torque plate body 300 shown is also feasible.

[0055] In this embodiment, as Figure 6 and Figure 8 As shown, the torque plate body 300 can have at least one mating hole 351, especially two mating holes 351 arranged vertically, at the end of the lever arm 310. With two mating holes 351 arranged vertically, the force generated by the rotational tendency can be precisely and perpendicularly applied to the bidirectional sensor. Thus, the torque plate body 300 can apply pressure to the sensor and also generate tension due to the reverse action, thereby solving the limitations of traditional single-sided pressure detection with higher accuracy.

[0056] The arrangement of several mating holes 351 can accommodate sensors with different operating heights and installation heights, ensuring that the point of action of the lever arm and the center of the inner ring hole 320 are on the same horizontal axis. Of course, in order to meet the accuracy requirements of actual testing needs, a liftable sensor or sensor bracket can also be used to achieve higher measurement accuracy.

[0057] It should be noted that the above specific embodiments are exemplary. Those skilled in the art can devise various solutions inspired by the disclosure of this utility model, and these solutions all fall within the scope of this utility model and its protection scope. Those skilled in the art should understand that this utility model specification and its drawings are illustrative and do not constitute a limitation on the claims. The protection scope of this utility model is defined by the claims and their equivalents. Throughout the text, features introduced by "preferred" are merely optional and should not be construed as mandatory. Therefore, the applicant reserves the right to abandon or delete relevant preferred features at any time.

Claims

1. A torque plate, comprising a torque plate body (300), characterized in that, The torque plate body (300) is detachably installed on the torque limiter (250) to be tested. It has lever arms (310) extending radially to both sides, and the ends of each lever arm form torque action ends (350) that are mechanically connected to the force sensor (400). When the torque limiter (250) under test is subjected to a test load, the torque plate body (300) tends to rotate clockwise or counterclockwise. When one of the lever arms (310) applies pressure to the corresponding force sensor (400) through its end torque action end (350), the other lever arm (310) applies tension to the corresponding force sensor (400) through its end torque action end (350), so as to realize bidirectional measurement of tension and compression forces.

2. The torque plate of claim 1, wherein, The torque plate body (300) is formed with an inner ring hole (320) in such a way that the inner ring hole (320) is located at the root of the two lever arms (310), the center (322) of the inner ring hole (320) constitutes the rotation center of the two lever arms (310) and coincides with the rotation axis of the torque plate body (300), wherein the first drive shaft (260) for transmitting the test load extends through the inner ring hole (320) via the torque limiter under test (250).

3. The torque plate of claim 2, wherein, The torque plate body (300) has a plurality of bolt holes (340) arranged in a ring around the outer periphery of the inner ring hole (320). The spatial arrangement of the bolt holes (340) forms a positioning fit with the positioning hole of the torque limiter (250) under test. These bolt holes (340) together form an mounting ring (341) that serves as a "ring force path for transmitting the test load from the torque limiter (250) under test to the torque plate body (300)".

4. The torque plate of claim 3, wherein, The torque plate body (300) has a stop ring (330) on its far end face (300b) that surrounds the inner ring hole (320). The stop ring (330) and the corresponding mating structure of the torque limiter (250) to be tested form a shape fit connection for mutual installation and positioning of the torque limiter (250) to be tested and the stop ring (330).

5. The torque plate of claim 4, wherein, The stop ring (330) is located in the radial region between the mounting ring (341) formed by the bolt holes (340) and the inner ring hole (320). The radial distance between the stop ring (330) and the radial inner wall of the inner ring hole (320) is smaller than the radial distance between the stop ring (330) and the mounting ring (341).

6. The torque plate of claim 3, wherein, The bolt holes (340) are either through bolt holes or blind holes on one side. These bolt holes (340) are used to transmit the rotational test load transmitted from the first drive shaft (260) to the torque limiter (250) under test along the mounting ring (341) to the torque plate body (300). The torque plate body (300) tends to rotate clockwise or counterclockwise depending on the direction of the rotational test load transmitted from the first drive shaft (260).

7. The torque plate according to one of claims 1 to 6, characterized in that The two lever arms (310) extending radially to both sides form an angle of 90° to 180° between each other, and / or the two lever arms (310) have the same lever arm length or they have lever arm lengths in a predetermined proportional relationship.

8. The torque plate of claim 4, wherein, The mounting ring (341), the inner ring hole (320), and the stop ring (330) of the torque plate body (300) form concentric circles and have a common center (322), wherein the center (322) constitutes the rotation center of the two lever arms (310).

9. An impact test rig having a torque plate as claimed in any one of claims 1 to 8, characterised in that, The device includes a base (100) and a first drive shaft (260), a second drive shaft (230), and a clutch (240) located above the base (100). The clutch (240) is disposed between the second drive shaft (230) and the first drive shaft (260). When the clutch (240) is engaged, the second drive shaft (230) transmits the test torque to the first drive shaft (260) to transmit the test torque to the torque plate body (300) of the torque plate via the torque limiter under test (250).

10. The impact testing bench according to claim 9, characterized in that, The base (100) is provided with a linear slide rail (410) whose axial extension direction is the same as that of the central axis of the second drive shaft (230) or the first drive shaft (260). A force sensor (400) for bearing the force from the torque plate body (300) is slidably mounted on the slide rail (410). The force sensor (400) can be adjusted by axial displacement along the slide rail (410) so that the detection end of the force sensor (400) and the torque action end (350) of the torque plate body (300) are positioned relative to each other, thereby adapting to torque limiters (250) with different axial thicknesses.

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