Material stretching-compression-torsion hydraulic comprehensive test equipment

Abstract

The invention relates to the technical field of material detection equipment, in particular to material stretching-compression-torsion hydraulic comprehensive test equipment. According to the scheme, the lifting linear driving mechanism is vertically and fixedly arranged in the rack, the two ends of the piston rod extend out of the cylinder body and can synchronously achieve lifting and rotating motion, the structure is compact, power transmission is direct, and precision loss of multi-assembly linkage is avoided; the swing cylinder is slidably assembled in the rack, fixedly connected with the bottom end of the piston rod and capable of synchronously ascending and descending along with the piston rod, stable transmission of torsion driving force is guaranteed, the rotation angle of the piston rod is accurately controlled, and the synchronous control precision of stretching / compression and torsion actions is improved. The upper chuck and the lower chuck are correspondingly arranged, adaptive clamping can be achieved according to the profile characteristics of steel plates and round steel, the problem that the adaptability of a universal equipment clamping assembly and a power transmission structure is insufficient is solved, and the requirement for accurate testing of specific profiles in the new material development stage is met.

Description

Technical Field

[0001] This invention relates to the field of material testing equipment technology, and in particular to a hydraulic integrated testing device for tensile-compression-torsion of materials. Background Technology

[0002] In fields such as engineering construction and machinery manufacturing, metal materials such as steel plates and round bars are widely used. The comprehensive mechanical properties of these materials directly determine the structural stability, load-bearing capacity, and service life of the final product. Therefore, after the successful development of new materials and before their large-scale production, conducting comprehensive and accurate testing and evaluation of their core mechanical indicators, such as tensile properties, compressive properties, and torsional properties, is a crucial step in ensuring product quality and mitigating engineering risks.

[0003] Currently, the industry generally adopts a single-item testing model for the mechanical property testing of materials such as steel plates and round bars. This involves using dedicated tensile testing equipment, compression testing equipment, and torsion testing equipment to independently test material samples, and then indirectly evaluating the comprehensive mechanical properties of the material based on the results of each individual test. Among the existing single-item testing equipment, tensile testing equipment mostly achieves axial tension on the material by driving the clamping assembly to rise and fall, obtaining parameters such as tensile strength and elongation; compression testing equipment applies axial pressure to determine indicators such as compressive strength and yield strength; and torsion testing equipment relies on a rotary drive mechanism to twist the material sample, obtaining parameters such as torsional strength and torsion angle.

[0004] However, the existing testing methods described above have significant technical shortcomings and are insufficient to meet the needs of accurate evaluation of the comprehensive mechanical properties of new materials. On the one hand, under the single-item testing mode, material samples need to be tested separately on different devices. The testing process requires multiple clamping and positioning operations, which is not only cumbersome and inefficient, but also prone to reduced correlation between individual test data due to clamping errors and positioning deviations. This makes it impossible to truly reflect the mechanical response of the material when it is simultaneously subjected to tensile, compressive, and torsional forces under actual working conditions. On the other hand, the comprehensive mechanical properties of materials are not a simple summation of individual properties. Single-item testing cannot capture the coupling effects between different stress forms. The comprehensive performance evaluated based on independent test results deviates significantly from the actual service performance of the material, which may lead to misjudgment of conformity. If a new material is mistakenly judged to meet the comprehensive performance standards and put into production, it may create hidden dangers of product failure and engineering accidents. On the other hand, overly conservative evaluation will limit the promotion and application of high-quality new materials and increase research and development and production costs.

[0005] In existing technologies, some testing equipment attempts to achieve integrated testing of multiple performance characteristics. For example, patent application CN118777068A discloses an engineering material performance testing device that, through the cooperation of a fixed clamping assembly, a movable clamping assembly, and a lifting assembly, can perform tensile, compressive, torsional, and corrosion performance tests on materials. However, the structural design of this type of equipment focuses more on the comprehensive testing of general engineering materials. Its clamping components and power transmission structure lack adaptability to specific profiles such as steel plates and round bars. Furthermore, it still falls short of meeting the stringent requirements for precise testing in the development stage of new materials in terms of the synchronous control accuracy of tensile and torsional combined forces and the correlation of mechanical parameter testing.

[0006] In summary, existing single-item testing equipment and general-purpose integrated testing equipment are unable to efficiently and accurately complete the comprehensive mechanical property testing tasks during the development stage of new materials such as steel plates and round bars, making it difficult to provide reliable data support for the qualification assessment and optimization of new materials. Therefore, developing a comprehensive testing device that is compatible with steel plates, round bars, and other profiles, can simultaneously perform integrated testing of tensile, compressive, and torsional properties, and has high testing accuracy and strong data correlation has become an urgent technical problem to be solved in the field of materials testing. Summary of the Invention

[0007] To address the above problems, this invention provides a hydraulic integrated testing device for material tensile-compression-torsion, which can simultaneously perform integrated testing of tensile, compressive, and torsional properties, with high testing accuracy and strong data correlation.

[0008] The technical solution of this invention is: A hydraulic integrated testing device for tensile-compression-torsion of materials, comprising: The lifting linear drive mechanism is vertically fixed inside the frame; the lifting linear drive mechanism is a double-outlet rod type drive component, with both ends of its hydrostatic piston rod extending out of the cylinder body, and the piston rod can move up and down along the cylinder body axis and can rotate around its own axis. The lower chuck is fixedly connected to the top of the piston rod of the lifting linear drive mechanism, and moves up and down and rotates synchronously with the piston rod. The swing cylinder is slidably disposed within the frame and can slide vertically up and down; the output shaft of the swing cylinder is fixedly connected to the bottom end of the piston rod of the lifting linear drive mechanism. By rotating the output shaft of the swing cylinder, the piston rod of the lifting linear drive mechanism is driven to rotate around its own axis, thereby controlling the rotation angle of the lower clamp. The upper clamp is fixed above the lower clamp and is arranged correspondingly to the lower clamp. It is used to jointly clamp the material to be tested in order to achieve comprehensive testing of the material's tensile and torsional properties.

[0009] Specifically, the lifting linear drive mechanism is one of a double-rod hydraulic cylinder, a double-rod pneumatic cylinder, or a double-rod electric cylinder.

[0010] Specifically, the swing cylinder slides up and down within the frame via a cylinder body connecting seat.

[0011] Specifically, the cylinder block connecting seat includes at least one pair of connecting plates; The end of the connecting plate is provided with a pair of rotatably connected rolling bearings; The inner side of the frame is provided with a guide rail located between and adapted to the pair of rolling bearings.

[0012] Specifically, the rack includes: The side panels are provided in pairs, arranged symmetrically vertically; The top plate is fixedly mounted on the top surface of the pair of side plates.

[0013] Specifically, the top of the frame is provided with an upper crossbeam that is adjustable and fixedly connected vertically; The upper clamp is connected to the bottom of the upper crossbeam via a test assembly.

[0014] Specifically, the lower chuck includes: The chuck body has a piston chamber and a clamping port at the top that communicates with the piston chamber; the clamping port has a cross-section that is smaller at the top and larger at the bottom. A pair of clamping wedges are provided, which are adapted to the clamping opening and are symmetrically slidably assembled in the clamping opening. The opposite end faces of the pair of clamping wedges constitute the sample clamping surface. The chuck piston is slidably disposed in the clamping cavity. Its tail end is fixedly connected to the top end of the piston rod of the lifting linear drive mechanism, and its front end is correspondingly connected to a pair of clamping wedges. The distance between the pair of clamping wedges is adjusted by the relative sliding of the chuck body and the chuck piston to achieve the clamping and releasing of the material. The fitting springs are provided in at least one pair. One end of each fitting spring is connected to the clamping wedge on the corresponding side, and the other end is connected to the chuck piston. They are inclined so that the corresponding fitting spring is pulled outward so that the fitting spring is always in contact with the top inclined surface of the chuck body.

[0015] Specifically, the top surface of the chuck piston is provided with a clamping groove that is adapted to the clamping wedge.

[0016] Specifically, the clamping opening is provided with a guide plate that is fixedly connected to the main body of the clamp; the guide plate is provided with an oblique groove that is adapted to the sliding direction of the clamping wedge; The clamping wedge is provided with a wedge pin fixedly connected thereto. The wedge pin extends out from the inclined slide groove and is used to connect to one end of the fitting spring. The other end of the fitting spring is connected to the chuck piston.

[0017] Specifically, the outer circumferential surface of the chuck piston is provided with a partition extending in the circumferential direction; The piston chamber is provided with a control chamber adapted to the partition; by introducing oil into the upper or lower part of the partition, the chuck body is driven to slide up and down on the chuck piston, thereby driving a pair of clamping wedges to slide synchronously and adjusting the distance between the pair of clamping wedges.

[0018] This invention addresses the core problems in the prior art, such as deficiencies in single-item testing modes, insufficient adaptability to general integrated equipment, and poor testing accuracy, through an integrated structural design and precise power control mechanism. The specific solutions are as follows: I. Overcome the fragmentation of single-item testing mode and achieve synchronous testing of composite forces.

[0019] Existing single-item tests require multiple setups on multiple devices, which can easily introduce errors and fail to capture the coupled effects of tensile, compressive, and torsional forces, leading to distorted comprehensive performance evaluations. This solution integrates a lifting linear drive mechanism, a swing cylinder, and upper and lower clamps to create an integrated testing platform. The corresponding upper and lower clamps allow for stable clamping of material samples such as steel plates and round bars in a single operation, eliminating the need for multiple clamping and positioning steps and fundamentally removing clamping errors and reduced data correlation. The double-outlet piston rod of the lifting linear drive mechanism enables axial lifting, providing tensile or compressive loads to the material. Simultaneously, the swing cylinder drives the piston rod to rotate around its own axis via an output shaft, applying torsional loads synchronously. This achieves simultaneous testing of tensile / compressive and torsional combined forces, accurately simulating the stress state of materials under actual working conditions and effectively capturing the coupled effects of different force forms. This solves the problem that single-item tests cannot reflect the true service performance of materials.

[0020] 2. Optimize power transmission and structural adaptability to meet specific profile testing requirements.

[0021] Existing general-purpose integrated equipment lacks adaptability to specific profiles such as steel plates, and suffers from low precision in synchronous control of composite forces. This design addresses this issue by vertically fixing the lifting linear drive mechanism within the frame. The piston rod extends from both ends of the cylinder and can simultaneously achieve lifting and rotational movements. Its compact structure and direct power transmission avoid the precision loss associated with multi-component linkage. The swing cylinder is slidably mounted within the frame and fixedly connected to the bottom of the piston rod, allowing it to rise and fall synchronously with the piston rod. This ensures stable transmission of torsional driving force, precisely controls the piston rod's rotation angle, and improves the synchronous control precision of tension / compression and torsional movements. Corresponding upper and lower clamps are designed to adapt to the characteristics of steel plates and round bars, solving the problem of insufficient adaptability of clamping components and power transmission structures in general-purpose equipment. This meets the precise testing requirements for specific profiles during the development of new materials. Attached Figure Description

[0022] Figure 1 This is a three-dimensional structural schematic diagram of the present invention; Figure 2 This is a cross-sectional structural diagram of the present invention; Figure 3 This is a schematic diagram of the three-dimensional structure of the lower chuck; Figure 4 This is a schematic diagram of the three-dimensional structure of the lower chuck in its disassembled state; Figure 5 This is a cross-sectional structural diagram of the lower chuck. Figure 6 This is a schematic diagram of the two cross-sectional structures of the lower clamp. Figure 7 This is a schematic diagram of the cross-sectional structure of the clamping wedge and the chuck piston; Figure 8 This is a three-dimensional structural diagram of the connection between the lifting linear drive mechanism and the swing cylinder; Figure 9 This is a three-dimensional structural diagram of the lifting linear drive mechanism and the swing cylinder in their disassembled state; Figure 10 This is a cross-sectional three-dimensional structural diagram of the hydrostatic cylinder block; Figure 11 This is a schematic diagram of the cross-sectional structure of the hydrostatic cylinder body and the hydrostatic piston rod; Figure 12 This is a cross-sectional view of the upper hydrostatic cylinder liner; Figure 13 This is a schematic diagram of the three-dimensional structure of the swing cylinder in its disassembled state; Figure 14 This is a schematic diagram of the cross-sectional structure of the swing cylinder; Figure 15 This is a schematic diagram of the swing cylinder structure; Figure 16 This is a cross-sectional view of the stator and rotor in their respective states; Figure 17 These are two sectional views showing the stator and rotor in their respective states. In the diagram, 100 is the lifting linear drive mechanism, 110 is the hydrostatic cylinder body, 120 is the hydrostatic piston rod, 130 is the upper hydrostatic cylinder liner, 131 is the pressure cavity, and 132 is the throttle port. 200 is the frame, 210 is the side plate, 220 is the top plate, 230 is the upper crossbeam, and 231 is the crossbeam lifting cylinder. 300 is the lower chuck, 310 is the chuck body, 320 is the clamping wedge, 330 is the chuck piston, 331 is the separator, 340 is the contact spring, and 350 is the guide plate. 400 is the swing cylinder, 401 is the upper end cover, 402 is the stator, 403 is the right end cover, 404 is the needle roller bearing, 405 is the rotor, 406 is the coupling, and 407 is the angular displacement sensor. 410 is the swing cylinder connecting seat, 411 is the connecting plate, 412 is the rolling bearing, and 413 is the guide rail. 420 is a displacement sensor. 500 is the upper clamp, and 510 is the tension and torsion tester. Detailed Implementation

[0023] Embodiments of the present invention are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention, and should not be construed as limiting the present invention.

[0024] In the description of this invention, it should be understood that the terms "upper," "lower," "left," "right," "vertical," and "horizontal," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing the invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of the invention. In the description of this invention, unless otherwise stated, "a plurality of" means two or more.

[0025] In the description of this invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "linking" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this invention based on the specific circumstances.

[0026] The following is for reference. Figure 1-17 Description of embodiments according to the present invention; A hydraulic integrated testing device for tensile-compression-torsion of materials, comprising: The lifting linear drive mechanism 100 is vertically fixed inside the frame 200; the lifting linear drive mechanism 100 is a double-outlet rod type drive component, both ends of its hydrostatic piston rod extend out of the cylinder body, and the piston rod can move up and down along the axis of the cylinder body and can rotate around its own axis. The lower chuck 300 is fixedly connected to the top end of the piston rod of the lifting linear drive mechanism 100, and synchronously achieves lifting and rotational movements with the piston rod; The swing cylinder 400 is slidably disposed within the frame 200 and can slide vertically up and down; the output shaft of the swing cylinder 400 is fixedly connected to the bottom end of the piston rod of the lifting linear drive mechanism 100. By rotating the output shaft of the swing cylinder 400, the piston rod of the lifting linear drive mechanism 100 is driven to rotate around its own axis, thereby controlling the rotation angle of the lower chuck 300. The upper chuck 500 is fixed above the lower chuck 300 and is arranged correspondingly to the lower chuck 300. It is used to jointly clamp the material to be tested so as to realize the comprehensive testing of the material's tensile and torsional properties.

[0027] Specifically, the lifting linear drive mechanism 100 is one of a double-rod hydraulic cylinder, a double-rod pneumatic cylinder, or a double-rod electric cylinder.

[0028] In order to test the accuracy of the tensile, compressive and torsional forces of the sample in each dynamic stage, it is required that the lifting and lowering action of the hydraulic cylinder be very flexible and have low resistance when controlling the sample during tensile, compressive and torsional phases. Therefore, this case prefers a double-rod hydraulic cylinder (or hydrostatic support cylinder).

[0029] The hydrostatic support cylinder includes a hydrostatic cylinder body 110 and a hydrostatic piston rod 120. The double-outlet drive component 120 has a cross-shaped cross section. The hydrostatic piston rod 120 is confined within the hydrostatic cylinder body 110 and moves up and down through an upper hydrostatic cylinder liner 130 and a lower hydrostatic cylinder liner located at the port of the hydrostatic cylinder body 110. To reduce the resistance caused by misalignment of the hydrostatic piston rod 120 within the hydrostatic cylinder body 110, the piston and piston rod portions of the hydrostatic cylinder body 110 are machined as a single unit to ensure concentricity.

[0030] To reduce the friction between the piston part of the hydrostatic piston rod 120 and the hydrostatic cylinder 110 during relative motion, the piston of this drive component adopts a gap seal without seals as the main sealing structure. By precisely controlling the fitting gap between the piston and the hydrostatic cylinder 110, the gap is minimized and stabilized. At the same time, a high-polymer wear-resistant and friction-reducing coating is plated on the surface of the piston part, such as a polytetrafluoroethylene (PTFE)-bronze powder composite coating or a PTFE-molybdenum disulfide-carbon fiber composite coating. Alternatively, depending on the working conditions of high temperature, high pressure or corrosive media, suitable materials such as polyimide (PI)-graphite-PTFE composite coating or polyetheretherketone (PEEK) coating can be selected.

[0031] After the coating process is completed, subsequent finishing processes are performed to precisely ensure the fit clearance between the piston and the cylinder, ensuring that the cylinder output force meets the design requirements. In this design, the hydrostatic piston rod 120 has multiple parallel triangular grooves at the piston position. The high-pressure oil flowing through the piston drives the piston to complete the lifting and lowering action. On the other hand, because there is a fit clearance between the piston and the hydrostatic cylinder 110, the high-pressure oil flows through this clearance to the other end of the piston. The oil entering the triangular grooves creates flow resistance, which allows the piston of the hydrostatic piston rod 120 to float and remain centered in the hydrostatic cylinder 110. Simultaneously, the oil flowing through the triangular grooves forms a stable oil film between the mating surfaces of the piston and the hydrostatic cylinder 110, providing reliable lubrication for their relative moving surfaces and further reducing friction loss.

[0032] The inner wall of the upper hydrostatic cylinder liner 130 is coated with a high-polymer wear-resistant and friction-reducing coating. The coating material is a high-polymer composite material with a low coefficient of friction and high wear resistance, effectively reducing frictional loss during relative movement between the cylinder liner and mating parts. The inner side of the upper hydrostatic cylinder liner 130 is provided with multiple pressure cavities 131, such as... Figure 12 As shown, the hydraulic pressure generating chamber provides a stable pressure source for hydraulic drive. The piston rod surface of the hydrostatic piston rod 120 is treated with hard chrome plating and then precision machined. This significantly improves the wear resistance and scratch resistance of the piston rod surface, and also ensures the designed fit clearance between the piston rod and the upper hydrostatic cylinder liner 130, ensuring the fit accuracy and sealing effect of the moving parts.

[0033] In this case, the static pressure cylinder liner 130 can be directly used as part of the frame 200 and rigidly connected to the side plate 210 of the frame 200. The overall structure is compact, which greatly reduces the cumulative error in the assembly process and improves the overall installation accuracy and operational stability of the equipment. The crossbeam lifting button and crossbeam locking button are humanizedly set at the front end of the equipment, and the operating position is in line with the actual use needs, realizing the convenience and efficiency of operation.

[0034] The hydraulic operation and hydrostatic support principle of this hydrostatic support hydraulic lifting cylinder are as follows: External pressure oil enters the internal pressure cavity 131 of the upper hydrostatic cylinder liner 130 through four throttle ports 132. The hydraulic force generated by the oil in the pressure cavity 131 acts on the outer circumference of the hydrostatic piston rod 120, stabilizing the piston rod at the center of the upper hydrostatic cylinder liner 130. Subsequently, the oil flows to the other end along the fit clearance between the upper hydrostatic cylinder liner 130 and the piston rod. During the flow, a uniform and stable hydrostatic oil film is formed between the mating surfaces, providing reliable lubrication and friction reduction for the moving parts. The oil flow mode and hydrostatic support principle of the lower hydrostatic cylinder liner and the lower end of the piston rod are completely consistent with the structure of the upper hydrostatic cylinder liner.

[0035] In summary, this hydrostatic support hydraulic lifting cylinder adopts a sealless gap sealing structure. Through precision machining, the fitting gap is minimized and stability is controlled. Combined with the double-end hydrostatic support design of the upper and lower hydrostatic cylinder liners, the cylinder's up and down lifting movement is more flexible and smooth, effectively reducing resistance loss during the movement process. At the same time, relying on the continuous lubrication of the hydrostatic oil film, the operational reliability and service life of the moving parts are further improved.

[0036] The lower end of the hydrostatic piston rod 120 of the lifting linear drive mechanism 100 is fixedly connected to the output shaft of the swing cylinder 400. The swing cylinder 400 is mounted on the cylinder body connecting seat 410 (or swing cylinder connecting seat). The swing cylinder 400 and the swing cylinder connecting seat 410 rise or fall together through the hydrostatic piston rod 120. The swing cylinder connecting seat 410 moves up and down on the guide rail 413 through the rolling bearing 412.

[0037] To test the torsional requirements of the prototype, a swing cylinder was designed at the lower end of the piston rod of the hydrostatic support hydraulic lifting cylinder.

[0038] The swing cylinder 400 slides up and down within the frame 200 via the cylinder body connecting seat 410.

[0039] The cylinder block connecting seat 410 includes at least one pair of connecting plates 411, and two pairs of connecting plates 411 are used in this case; The end of the connecting plate 411 is provided with a pair of rotatably connected rolling bearings 412; The inner side of the frame 200 is provided with a guide rail 413 located between and adapted to a pair of rolling bearings 412.

[0040] Further description of connecting plate 411: One end of the connecting plate 411 is connected to the swing cylinder 400. This end has an arc-shaped structure and is a wide end, with its width gradually decreasing along the extension direction toward the rolling bearing 412. The other end is fixedly connected to the crossbeam plate for mounting the rolling bearing 412. This end is a narrow end and has a planar port structure. It is fixedly connected to the crossbeam plate, and a pair of rolling bearings 412 are rotatably mounted on the crossbeam plate.

[0041] The connecting plate 411, with its wide-end arc shape, narrow-end flat surface, and smoothly decreasing width, effectively disperses the torque output by the swing cylinder 400, avoids stress concentration, and improves the structure's fatigue resistance and force transmission efficiency. On the other hand, the arc-shaped structure conforms to the arc-shaped motion trajectory of the swing cylinder, and the bottom surface of the connecting plate 411 is in contact with and fixed to the surface of the crossbeam plate, which not only ensures connection stability and motion accuracy but also avoids motion and spatial interference. At the same time, it achieves a compact layout of the swing mechanism, simplifies processing and assembly, and adapts to the actual operating requirements of the equipment.

[0042] When a gap appears between the rolling bearing 412 and the guide rail 413, it can cause various problems related to testing accuracy, equipment operation, and structural safety, such as: 1) The gap will cause the torque output of the swing cylinder to be delayed and fluctuate, and the torque value will be inconsistent and cannot be stably transmitted to the sample. This will cause the measured key data such as torsional stiffness and torsional strength to deviate from the true value, and the test results will lose their reference value.

[0043] 2) Comprehensive testing requires simultaneous control of tensile-compression and torsion actions. The gap will increase the deviation of the straightness of the rolling bearing sliding along the guide rail. When the sample is under force, an additional eccentric displacement will be generated at the same time, making it impossible to achieve the preset stress state, thus affecting the accuracy of the test data under composite working conditions.

[0044] 3) The motion jamming and free rotation caused by the gap will lead to disordered feedback signals from the equipment sensors (force sensor, angle sensor), resulting in force value jumps and angle measurement lags. It is impossible to accurately capture the real-time response of the sample after being subjected to force, making it difficult to complete high-precision testing tasks.

[0045] To this end, this design pre-designs a connecting plate 411 with a gradually wide structure to provide a suitable basic structure for gap adjustment. The wide end connects to the swing cylinder 400, conforming to the arc-shaped motion trajectory of the swing cylinder to avoid spatial interference; the narrow end is used to assemble the eccentric rod assembly to ensure connection stability and force transmission efficiency.

[0046] Rolling bearing 412 is fitted onto the eccentric section of the eccentric rod. The inner ring of the bearing is interference-fitted with the eccentric section of the eccentric rod, while the outer ring slides against the side wall of guide rail 413. The eccentricity can be flexibly adjusted according to the swing angle of the swing cylinder, the guide rail spacing, and torque transmission requirements, balancing force and angle conversion efficiency with motion interference avoidance. The eccentric rod can make the bearing always fit the guide rail through radial offset, and the torque is rigidly transmitted through the eccentric rod to avoid the force from spinning freely. This meets the stringent requirements of the sample torsion test for the stability of force transmission, ensures the accuracy of the swing cylinder swing angle, and avoids test data distortion caused by gaps.

[0047] Further description of displacement sensor 420: The fixed end of the displacement sensor 420 is installed on the static pressure cylinder 110 of the lifting linear drive mechanism 100, and the movable end is installed on the connecting plate 411. The static pressure piston rod 120 of the lifting linear drive mechanism 100 moves up and down in the static pressure cylinder 110 under the push of the oil. The displacement sensor 420 measures the stroke of the lifting cylinder.

[0048] Further description of the structure of the 400 swing cylinder: The main structure of the swing cylinder 400 includes core components such as an upper end cover 401, a stator 402, a right end cover 403, a needle roller bearing 404, a rotor 405, a coupling 406, an angular displacement sensor 407, an upper support plate, and a lower support plate. The upper end cover 401 and the right end cover 403 are fastened together by screws, and the stator 402 is precisely clamped between the upper end cover 401 and the right end cover 403 to form a stable cylinder body basic structure.

[0049] The radial mating surfaces of stator 402 and rotor 405 employ a seal-free gap seal design. Specifically, this sealing method is used on both the outer and inner radial mating surfaces of stator 402 and rotor 405. This design imposes requirements on the radial clearance of the mating surfaces to be small and highly stable. To address this, a high-polymer wear-resistant and friction-reducing coating is applied to the inner surface of stator 402 and the outer surface of rotor 405. The low-friction characteristics of the coating reduce radial relative motion resistance, while its high wear resistance ensures the long-term stability of the gap seal.

[0050] The rotor 405 adopts an axial clearance sealing design without seals between its two end faces and the upper and lower support plates. The axial fit clearance is required to meet the technical requirements of small clearance, high precision and stability. Correspondingly, the surfaces of the upper and lower support plates that mate with the end faces of the rotor 405 are coated with the same type of polymer wear-resistant and friction-reducing coating, which effectively reduces friction loss from axial relative movement and avoids gap deviation caused by end face contact wear.

[0051] To ensure that the radial clearance between stator 402 and rotor 405 and the axial clearance between rotor 405 and upper and lower support plates meet the design requirements, stator 402 and rotor 405 are both processed by integral wire cutting process. The high-precision machining method ensures the form and position tolerances and dimensional accuracy of the parts, and ensures the miniaturization and stability of the clearances of each mating surface from the machining end, providing a foundation for the reliable realization of sealless gap sealing.

[0052] The needle roller bearing 404 is sleeved on the outside of the rotor 405, providing stable rotational support for the rotor 405 and ensuring that the rotor 405 can achieve high-speed and smooth operation. By replacing sliding friction with rolling friction, it significantly reduces frictional resistance during movement and improves the flexibility and smoothness of the swing cylinder 400's operation. The angular displacement sensor 407 is connected to the rotor 405 via the coupling 406, accurately detecting and outputting the real-time rotational displacement of the rotor 405, thus achieving accurate monitoring of angular displacement.

[0053] The operating principle of this swing cylinder 400 is as follows: Figure 16 As shown: Pressurized oil enters cylinder cavity A through the pre-set inlet of stator 402. Because rotor 405 has radially opened through-holes, the pressurized oil can connect cavity A and cavity B at the mating point of stator 402 and rotor 405, allowing both cavities to be filled with pressurized oil and forming hydraulic driving force, thus pushing rotor 405 along... Figure 16 Rotation occurs in the direction of the arrow; conversely, switching the direction of the inlet and outlet of the pressurized oil changes the direction of the hydraulic driving force, thus achieving reverse rotation of rotor 405. During the operation of rotor 405, its real-time angular displacement is synchronously detected and continuously output by angular displacement sensor 407, ensuring precise control of the rotational motion.

[0054] The structure of rack 200 is further described, including: Side panels 210 are provided in pairs, arranged symmetrically vertically; The top plate 220 is fixedly installed on the top surface of the pair of side plates 210. The top surface of the top plate in this case is a plane. The bottom of the pair of side plates 210 is connected and reinforced by multiple connecting plates.

[0055] The top of the frame 200 is provided with an upper crossbeam 230 that is adjustable and fixedly connected vertically; The upper chuck 500 is connected to the bottom of the upper crossbeam 230 via a testing assembly. The upper crossbeam 230 is fixedly mounted on the top of the frame via a pair of columns. In this case, the upper crossbeam 230 is fixedly connected to the pair of columns via multiple connectors, which facilitates the vertical adjustment of the height of the upper crossbeam 230 in the axial direction of the columns. The testing assembly includes a tension-torsion tester 510. The tension-torsion tester 510 is located between the upper crossbeam 230 and the upper chuck 500. The tension-torsion tester 510 is fixedly connected to the upper chuck 500 via threads. It is used to detect the torque value generated by the sample during torsion in real time, to detect the clamping pressure on the sample in real time, and the axial force fed back by the sample during tension / compression. The tension-torsion tester 510 in this case is an existing integrated product.

[0056] The upper crossbeam 230 is made of high-strength aluminum alloy, which effectively reduces its weight while ensuring structural strength; the column is made of low-carbon steel. The friction pair composed of aluminum alloy and low-carbon steel has a large static friction coefficient, which can ensure that the upper crossbeam can remain locked after lifting and lowering, thus ensuring the reliability of locking.

[0057] Further optimization of the upper crossbeam 230: While the upper crossbeam 230 is mounted on a pair of uprights, the height of the upper crossbeam 230 is adjusted by a pair of crossbeam lifting cylinders 231. After adjustment, the upper crossbeam 230 is locked onto the pair of uprights.

[0058] Specifically, the cylinder body of the crossbeam lifting cylinder 231 is fixedly installed on the outside of the side plate 210, and its piston rod is hinged to the upper crossbeam 4. Under the push of the oil, the piston rod moves up and down, thereby driving the upper crossbeam 230 to move up and down along the axial direction of the column, thereby driving the inclined wedge force-increasing hydraulic upper chuck 500 to move up and down, so as to meet the height requirements of different sample pieces.

[0059] Test specimens are typically dumbbell-shaped plates or cylinders with smooth surfaces. Sufficient clamping force is required to hold the specimens securely. Therefore, a wedge-shaped hydraulic upper and lower clamp was designed.

[0060] The lower chuck 300 structure specifically includes: The chuck body 310 has a piston chamber and a clamping port at the top that communicates with the piston chamber. The clamping port has a cross-section that is smaller at the top and larger at the bottom, which provides a guiding foundation for the sliding and force-increasing clamping of the clamping wedge 320. A pair of clamping wedges 320 are provided, which are adapted to the clamping opening and are symmetrically slidably assembled in the clamping opening. The opposite end faces of the pair of clamping wedges 320 form the sample clamping surface, which is adapted to the clamping requirements of steel plates and other profiles, and improves the friction of clamping the sample. The clamping surface has a sawtooth structure. The chuck piston 330 is slidably disposed in the clamping cavity. Its tail end is fixedly connected to the top end of the piston rod of the lifting linear drive mechanism 100, and its front end is correspondingly connected to a pair of clamping wedges 320. By sliding the chuck body 310 relative to the chuck piston 330, the pair of clamping wedges 320 are driven to slide synchronously along the gradient structure of the clamping opening, thereby adjusting the distance between the pair of clamping wedges 320 to achieve the clamping and releasing of the material. At least one pair of contact springs 340 are provided. One end of each contact spring 340 is connected to the clamping wedge 320 on the corresponding side, and the other end is connected to the chuck piston 330. They are inclined so that the corresponding contact spring 340 is pulled outward to keep it in contact with the top inclined surface of the chuck body 310. With the elastic force of the contact springs 340, the clamping wedge 320 and the front end face of the chuck piston 330 are always tightly fitted, ensuring the stability of power transmission and the synchronization of clamping action.

[0061] The top surface of the chuck piston 330 is provided with a clamping groove that is adapted to the clamping wedge 320. The vertical bottom surfaces of a pair of clamping wedges 320 are fitted into the clamping grooves of the chuck piston 300, and the outer inclined surfaces of the pair of clamping wedges are fitted to the 25-degree inner inclined surface of the clamping opening. As the chuck piston 330 moves up and down, the opening and closing actions are synchronously realized along the inclined surface.

[0062] The clamping opening is provided with a guide plate 350 that is fixedly connected to the chuck body 310; the guide plate 350 is provided with an inclined groove that is adapted to the sliding direction of the clamping wedge 320; The clamping wedge 320 is provided with a wedge pin fixedly connected thereto. The wedge pin extends out from the inclined slide groove and is used to connect to one end of the fitting spring 340. The other end of the spring 340 is connected to the chuck piston 330.

[0063] In this invention, guide plates 350 are provided on both sides of the clamping wedge 320. With the help of the elastic force of the contact spring 340, the clamping wedge 320 is always tightly fitted with the front end face of the chuck piston 330. At the same time, with the guiding effect of the guide plate 350, the sliding trajectory of the clamping wedge 320 is ensured, further improving the stability of power transmission and the synchronization of clamping action.

[0064] The outer circular surface of the chuck piston 330 is provided with a partition 331 extending in the circumferential direction; in this case, the partition 331 has a ring structure. The piston chamber is provided with a control chamber adapted to the partition 331; by injecting oil into the upper or lower part of the partition 331, the chuck body 310 is driven to slide up and down on the chuck piston 330, thereby driving a pair of clamping wedges 320 to slide synchronously, adjusting the distance between the pair of clamping wedges 320, and finally realizing the function of clamping or releasing the material.

[0065] The lower chuck 300, as the core clamping and power transmission component, directly determines the material clamping stability, force transmission accuracy, and composite testing reliability through its structural design. The specific technical solution is as follows: The lower chuck 300 is made of high-strength wear-resistant alloy material in one piece. It has an adjustable clamping structure that is compatible with steel plates, round steel and other profiles. The clamping surface is equipped with anti-slip teeth. The clamping gap can be adjusted according to the cross-sectional dimensions of the material to be tested (such as the thickness of steel plates and the diameter of round steel) to achieve stable clamping of material samples of different specifications, avoid material slippage and displacement during the test, and ensure that tensile / compressive loads and torsional loads can be accurately transmitted to the material body.

[0066] In terms of connection, the bottom of the lower chuck 300 and the top of the piston rod of the lifting linear drive mechanism 100 are detachably rigidly fixedly connected, which not only ensures assembly accuracy but also facilitates later maintenance and replacement of chuck components adapted to different profiles. At the same time, this rigid connection structure can realize lossless power transmission, so that the axial tensile / compressive force output by the lifting linear drive mechanism and the torsional load generated by the rotation of the piston rod driven by the swing cylinder can be synchronously transmitted to the clamped material sample through the lower chuck, ensuring the consistency of the material under combined stress and providing structural support for the accuracy of test data.

[0067] Furthermore, the clamping center of the lower chuck 300 and the clamping center of the upper chuck 500 are coaxially arranged, and the coaxiality error is controlled within a preset range. Together with the upper chuck, they form a symmetrical clamping structure, which effectively avoids additional bending moments caused by eccentric force on the material during testing, eliminates the interference of eccentric loads on tensile and torsional test parameters, and further ensures the accuracy of composite mechanical property testing, meeting the stringent requirements for testing accuracy in the new material development stage. The structure of the upper chuck 500 in this case is the same as that of the lower chuck 300.

[0068] The operating principle of a hydraulic chuck is as follows: Figure 5-6 As shown; Initial state, such as Figure 6 As shown, at this time, oil enters through port two, and the chuck body 310 moves downward relative to the chuck piston 330, forming a... Figure 5 In the first position, the clamping wedge 320 moves along the inclined surface at the top of the chuck body 310 under the tension of the spring 340, completing the closing action and clamping the sample. Conversely, when oil enters through the oil port, the sample is released. This clamping structure uses a wedge structure, which has a force-amplifying effect. When clamping the sample, the clamping force of the left and right clamping blocks is amplified by the wedge mechanism. Then, the amplified clamping force multiplied by the coefficient of friction between the left and right clamping blocks and the sample is greater than the force of vertical tension.

[0069] To further summarize the overall operation process of the equipment: Operate the upper crossbeam 230 lifting button at the front of the equipment to control the upper crossbeam 230 to run to the designated position, and then reset the button to the stop position. At this time, the crossbeam lifting cylinder 231 automatically completes the locking action of the upper crossbeam 230. If it is necessary to further improve the connection stability, multiple connectors can be used to fix the column to the upper crossbeam 230 to ensure that the crossbeam position does not shift during the test.

[0070] Place the sample to be tested between the upper and lower chucks of the equipment, operate the chuck control button to the clamping position, and complete the reliable clamping and positioning of the sample through the chuck.

[0071] The electrical control program of the equipment is started. The static pressure piston rod drives the upper clamp to perform reciprocating stretching and compression movements. At the same time, the swing cylinder rotor 405 rotates synchronously, driving the static pressure piston rod to swing accordingly, so that the sample under test is in a complex alternating stress state of tension, compression and torsion, and the comprehensive performance test is completed.

[0072] During the test, the linear displacement generated by the tension and compression of the sample is detected and output in real time by the displacement sensor 420; the tensile and compressive forces are accurately collected and output by the tension-torsion tester 510; the angular displacement generated by the torsion of the sample is detected and output synchronously by the angular displacement sensor 407; and the torsional torque is collected and output uniformly by the tension-torsion tester 510, realizing real-time monitoring of various test data.

[0073] The core technological advantages of the equipment in this case: 1. The sample clamping adopts a wedge-type hydraulic chuck, which increases the clamping force based on the wedge force-increasing principle to achieve a firm clamping of the sample, effectively preventing the sample from slipping or shifting during the test and ensuring the stability of the test.

[0074] 2. The power systems for tensile, compressive, and torsional testing of the sample are all hydraulically driven and controlled. All hydraulic moving pairs adopt a gap-sealing structure without seals, which has the advantages of long sealing life and low friction. Combined with the hydraulic servo control system, it can quickly respond to the action commands of dynamic testing and meet the high responsiveness requirements of dynamic composite testing.

[0075] 3. The tension and torsion tester is integrated and installed directly above the upper chuck, and is rigidly connected only to the upper chuck. This effectively avoids force transmission interference from other moving parts of the equipment, eliminates testing errors from the structural design, and greatly improves the accuracy and precision of force value detection.

[0076] 4. The equipment can accurately detect the linear displacement of tensile / compression and the angular displacement of torsion of the sample. At the same time, it can simultaneously collect and output key mechanical parameters such as tensile force, compressive force, and torsional torque. The test data is comprehensive and accurate. It is a special equipment suitable for the comprehensive mechanical property testing of materials under tension, compression and torsion, and is adapted to the composite mechanical property testing needs of various materials.

[0077] Existing single-item testing operations are cumbersome, inefficient, and lack data correlation, making it difficult to support the qualification assessment of new materials. This project achieves "one-time clamping, multiple tests" through an integrated structure, significantly simplifying the operation process and improving testing efficiency. The coordinated control of the lifting linear drive mechanism and the swing cylinder can simultaneously acquire the tensile / compression parameters (such as tensile / compressive strength, elongation) and torsional parameters (such as torsional strength, torsion angle) of the material under combined forces, ensuring the correlation and consistency of test data and avoiding the fragmentation of independent test data. All components are integrated into the frame, with precise structural positioning, further ensuring testing accuracy. This provides reliable data support for the accurate evaluation and optimization of the comprehensive mechanical properties of new materials, ultimately solving the technical problem that existing equipment cannot efficiently and accurately complete the comprehensive testing tasks in the development stage of new materials. In other words, this project achieves an organic combination of simultaneous testing under combined forces, adaptation to specific profiles, and high-precision control through an integrated design of "clamping-tension / compression-torsion," meeting the comprehensive mechanical property testing needs of new materials such as steel plates and round bars in the development stage.

[0078] Regarding the information disclosed in this case, the following points need to be clarified: (1) The accompanying drawings of the embodiments disclosed in this case only involve the structures involved in the embodiments disclosed in this case. Other structures can refer to the general design. (2) Where there is no conflict, the embodiments and features disclosed in this case can be combined with each other to obtain new embodiments; The above are merely specific embodiments disclosed in this case, but the scope of protection of this disclosure is not limited thereto. The scope of protection disclosed in this case shall be determined by the scope of protection of the claims.

Claims

1. A hydraulic integrated testing device for tensile-compression-torsion of materials, characterized in that, include: The lifting linear drive mechanism (100) is vertically fixed inside the frame (200); the lifting linear drive mechanism (100) is a double-outlet drive component, both ends of its static pressure piston rod extend out of the cylinder body, and the piston rod can move up and down along the cylinder body axis and can rotate around its own axis. The lower chuck (300) is fixedly connected to the top of the piston rod of the lifting linear drive mechanism (100), and moves up and down and rotates synchronously with the piston rod. A swing cylinder (400) is slidably disposed within the frame (200) and can slide vertically up and down; the output shaft of the swing cylinder (400) is fixedly connected to the bottom end of the piston rod of the lifting linear drive mechanism (100). By rotating the output shaft of the swing cylinder (400), the piston rod of the lifting linear drive mechanism (100) is driven to rotate around its own axis, thereby controlling the rotation angle of the lower chuck (300); The upper chuck (500) is fixed above the lower chuck (300) and is arranged correspondingly to the lower chuck (300). It is used to jointly clamp the material to be tested so as to realize the comprehensive testing of the material's tensile and torsional properties.

2. The material tensile-compression-torsion hydraulic integrated testing equipment according to claim 1, characterized in that, The lifting linear drive mechanism (100) is one of a double-rod hydraulic cylinder, a double-rod pneumatic cylinder, or a double-rod electric cylinder.

3. The material tensile-compression-torsion hydraulic integrated testing equipment according to claim 1, characterized in that, The swing cylinder (400) slides up and down within the frame (200) via the cylinder body connecting seat (410).

4. The material tensile-compression-torsion hydraulic integrated testing equipment according to claim 3, characterized in that, The cylinder block connecting seat (410) includes at least one pair of connecting plates (411); The end of the connecting plate (411) is provided with a pair of rotatably connected rolling bearings (412). The frame (200) has a guide rail (413) located between and adapted to the pair of rolling bearings (412) on its inner side.

5. The material tensile-compression-torsion hydraulic integrated testing equipment according to claim 1, characterized in that, The rack (200) includes: Side panels (210) are provided in pairs, arranged symmetrically vertically; The top plate (220) is fixedly disposed on the top surface of the pair of side plates (210).

6. The material tensile-compression-torsion hydraulic integrated testing equipment according to claim 1, characterized in that, The top of the frame (200) is provided with an upper crossbeam (230) that is adjustable and fixedly connected vertically. The upper clamp (500) is connected to the bottom of the upper crossbeam (230) via a test assembly.

7. The material tensile-compression-torsion hydraulic integrated testing equipment according to claim 1, characterized in that, The lower chuck (300) includes: The chuck body (310) is provided with a piston chamber, and the top opening is provided with a clamping port communicating with the piston chamber; the clamping port has a cross-section that is smaller at the top and larger at the bottom; A pair of clamping wedges (320) are provided, which are adapted to the clamping opening and are symmetrically slidably assembled in the clamping opening. The opposite end faces of the pair of clamping wedges (320) constitute the sample clamping surface. The chuck piston (330) is slidably disposed in the clamping cavity. Its tail end is fixedly connected to the top end of the piston rod of the lifting linear drive mechanism (100), and its front end is correspondingly connected to a pair of clamping wedges (320). The distance between the pair of clamping wedges (320) is adjusted by the relative sliding of the chuck body (310) and the chuck piston (330) to realize the clamping and releasing of the material. There is at least one pair of contact springs (340). One end of each contact spring (340) is connected to the clamping wedge (320) on the corresponding side, and the other end is connected to the chuck piston (330). They are inclined so that the corresponding contact spring (340) is pulled outward so that the contact spring (340) is always in contact with the top inclined surface of the chuck body (310).

8. The material tensile-compression-torsion hydraulic integrated testing equipment according to claim 7, characterized in that, The top surface of the chuck piston (330) is provided with a clamping groove that is adapted to the clamping wedge (320).

9. A material tensile-compression-torsion hydraulic integrated testing device according to claim 7, characterized in that, The clamping opening is provided with a guide plate (350) that is fixedly connected to the clamping body (310); the guide plate (350) is provided with an inclined groove that is adapted to the sliding direction of the clamping wedge (320); The clamping wedge (320) is provided with a wedge pin fixedly connected thereto. The wedge pin extends out from the inclined groove and is used to connect with one end of the fitting spring (340). The other end of the fitting spring (340) is connected to the chuck piston (330).

10. A hydraulic integrated testing device for tensile-compression-torsion testing of materials according to claim 7, characterized in that, The outer circular surface of the chuck piston (330) is provided with a partition (331) extending in the circumferential direction. The piston chamber is provided with a control chamber adapted to the partition (331); by injecting oil into the upper or lower part of the partition (331), the chuck body (310) is driven to slide up and down on the chuck piston (330), thereby driving a pair of clamping wedges (320) to slide synchronously, and adjusting the distance between the pair of clamping wedges (320).

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