A high-power dynamometer torque calibration device

Abstract

The application discloses a kind of high-power dynamometer torque calibration device, it is related to the improvement of torque test technology, including base and the lifting mechanism being installed on base, lifting mechanism side is provided with the drive mechanism for its lifting control, the lifting end of lifting mechanism is connected with connecting shaft, the upper end of this connecting shaft is connected with the force arm of loading device by high-precision tension sensor, lifting mechanism is the mechanism based on the action of inclined wedge principle, it includes horizontally movable upper wedge and vertically movable lower wedge, upper wedge is horizontally moved by drive mechanism, and the loading of tension sensor is realized by forcing lower wedge to produce vertical displacement using inclined surface cooperation.The application has the long-term stability of calibration force value by the mechanical self-locking of inclined wedge mechanism, and using the weight adjustment system of automatically adjustable lower wedge, while significantly expanding the torque range of device, effectively reduce the load of drive unit and other advantages.

Description

Technical Field

[0001] This invention relates to improvements in torque testing technology, and more particularly to a torque calibration device for a high-power dynamometer. Background Technology

[0002] High-power dynamometers are core devices for performance testing of heavy power equipment such as engines and gas turbines, and their torque measurement accuracy is directly related to the reliability of product development and quality control. Traditional torque calibration generally adopts the static loading method of weights, using the gravity of the weights to generate a standard torque on the calibration arm.

[0003] In existing technologies, with the widespread application of high-power equipment, torque levels have reached hundreds of thousands to millions of Newton-meters, placing extremely stringent demands on torque calibration technology. Against this backdrop, the limitations of traditional weight loading methods are becoming increasingly apparent: on the one hand, weights cannot achieve continuous, stepless force adjustment, making it difficult to meet the demands of high-precision calibration for minute force quantification; on the other hand, the calibration process requires frequent lifting, adding, and replacing of weights, making the operation cumbersome and heavy, posing significant safety hazards and efficiency bottlenecks. Therefore, modern calibration devices are gradually replacing weights with hydraulic servo systems or electric servo mechanisms, applying precisely controllable tension through servo electric cylinders, precision lead screws, and other mechanisms, significantly improving calibration efficiency and reducing manual labor intensity. However, this active loading-based technical approach still faces a key challenge: its ability to maintain force stability is still difficult to match the constant load generated by weights, which is determined solely by gravity. Hydraulic systems may experience creep due to factors such as oil temperature changes and internal leakage, while electric mechanisms may experience positional drift due to elastic deformation of the transmission links and gear backlash. This can lead to attenuation or fluctuation of the applied force under continuous high load conditions, which restricts further improvement of calibration accuracy, especially in field calibration scenarios where long-term stability requirements are extremely high.

[0004] Furthermore, when applying precisely controllable tension to a dynamometer for calibration using mechanisms such as servo electric cylinders and precision lead screws, the reaction force generated by the torque being measured will be primarily transmitted through the transmission chain and concentrated on the lead screw assembly itself. This results in the lead screw and its associated nut mechanism bearing extremely high axial loads. This singular force flow path not only places extremely high demands on the strength, stiffness, and fatigue life of the lead screw but also triggers a series of chain problems: to drive the lead screw to overcome this load, the servo motor or other drive components must output a corresponding amount of torque, thus forcing the power rating of the entire drive system to be strictly matched to the maximum magnitude of the torque being measured, significantly increasing the specifications, cost, and size of key components such as motors and reducers. Moreover, since the force output range of a single lead screw mechanism and its drive unit has a clear upper limit, such devices often lack sufficient load adaptability when facing torque calibration tasks with a wide range, thus exhibiting certain limitations in application flexibility.

[0005] To address the above technical problems, this invention discloses a high-power dynamometer torque calibration device. Summary of the Invention

[0006] The purpose of this invention is to overcome the shortcomings of existing technologies and provide a torque calibration device for a high-power dynamometer. This addresses the limitations of traditional static weight loading in high-power dynamometer torque calibration, which is cumbersome, inefficient, and lacks stepless adjustment in ultra-high torque scenarios. Furthermore, active loading methods such as servo electric cylinders face challenges in long-term force stability due to system creep and elastic deformation, as well as cost, size, and adaptability limitations imposed by concentrated high loads on transmission components. This invention ensures long-term stability of the calibration force value through the mechanical self-locking of a wedge mechanism and utilizes an automatically adjustable lower wedge counterweight system, significantly expanding the device's torque range while effectively reducing the load on the drive unit. This achieves advantages such as high-precision, wide-range, and safe torque calibration.

[0007] This invention is achieved through the following technical solution: This invention discloses a torque calibration device for a high-power dynamometer, including a base and a lifting mechanism mounted on the base. A drive mechanism for lifting and controlling the lifting mechanism is provided on one side of the lifting mechanism. A connecting shaft is connected above the lifting end of the lifting mechanism. The upper end of the connecting shaft is connected to the lever arm of the loading device through a high-precision tension sensor. The lifting mechanism is a mechanism based on the wedge principle, which includes a horizontally movable upper wedge and a vertically movable lower wedge. The drive mechanism pushes the upper wedge to move horizontally, and the inclined plane cooperation forces the lower wedge to produce a vertical displacement, thereby realizing the loading of the tension sensor. Furthermore, the inclined plane angle of the wedge mechanism is set to meet the mechanical self-locking condition, so that the position can be maintained by frictional resistance after the loading stops.

[0008] Furthermore, the lifting mechanism also includes an outer frame and a guide assembly. The outer frame is fixed to the base, and the guide assembly includes a guide sleeve set on the top plate of the outer frame and a guide column fixedly connected to the lifting seat. The guide column and the guide sleeve are slidably engaged to guide the lifting seat and the lower wedge block to move smoothly in the vertical direction.

[0009] Furthermore, the drive mechanism includes a screw and a worm gear transmission pair. The screw is rotatably connected to the upper wedge and forms a helical pair with the threaded hole fixed on the outer frame. The worm gear drives the screw to rotate, thereby converting the rotational motion into the horizontal linear motion of the upper wedge.

[0010] Furthermore, the drive mechanism is connected to the screw drive through a transmission mechanism, which includes a set of wedge disks. The wedge disks consist of two wedge disks with inclined surfaces that engage and are held in engagement by a spring. When the transmission torque exceeds the set value, the wedge disks overcome the spring force and disengage, interrupting the power transmission.

[0011] Furthermore, the axial reciprocating motion of the wedge disk assembly in the disengaged state of the transmission mechanism is linked to a weight-adding mechanism. The reciprocating motion of the wedge disk assembly drives the pumping component of the weight-adding mechanism to inject liquid into the sealed tank connected to the lower wedge block.

[0012] Furthermore, the weight-increasing mechanism includes a sealed tank fixed to the lower part of the lower wedge, which adjusts the total weight of the lower wedge system by increasing the weight of the liquid inside the tank.

[0013] Furthermore, the transmission mechanism includes a piston cylinder, the piston rod of which is connected to the wedge plate assembly and driven by it to reciprocate, thereby drawing in external liquid through the pipeline and pressing it into the sealed tank.

[0014] Furthermore, the lower wedge is detachably connected to the guide assembly, allowing for the replacement of lower wedge modules of different weights according to the range of the calibrated torque.

[0015] Furthermore, the drive mechanism is an electric drive device, which converts the rotational motion of the motor into the horizontal thrust of the upper wedge through a combination of worm gear transmission and helical pair.

[0016] Furthermore, the screw is connected to the wedge assembly via a key shaft and a key sleeve; the key shaft is fixedly connected to one end of the screw, and one end of the key sleeve is connected to the drive shaft via the wedge assembly.

[0017] The present invention has the following advantages:

[0018] (1) This invention effectively improves the adaptability and efficiency of torque calibration by integrating a wedge-type force conversion mechanism and an adjustable counterweight system. It adopts the principle of inclined plane self-locking, which can reliably maintain the load after the drive stops, avoiding the force drift caused by internal force relaxation in traditional hydraulic or electric loading; at the same time, by changing the lower wedge block of different weights or injecting liquid into its auxiliary container, the system configuration can be quickly adjusted, significantly expanding the torque range of the device, enabling a single device to cover a wider range of calibration requirements, reducing the dependence on and replacement frequency of corresponding weight sets, and making the operation safer and more convenient.

[0019] (2) This invention significantly enhances the reliability and accuracy of operation through overload protection and automatic counterweight functions. When the load exceeds the motor capacity, the wedge mechanism in the transmission chain can automatically disconnect to prevent equipment damage; at the same time, the reciprocating motion triggered by the disconnection state can drive the liquid pump to automatically add weight to the lower wedge until the system load falls back to a safe range and transmission is restored. This mechanism not only avoids the risk of equipment overload due to operational negligence, but also automates the counterweight process. Finally, through standardized tare operation, it can ensure that the reading of the force sensor accurately reflects the pure calibration force value, thereby achieving high-precision and high-repeatability torque calibration while ensuring the safety of personnel and equipment.

[0020] (3) By adjusting the configurable weight of the lower wedge, this invention optimizes the stress state of the system and significantly improves its overall performance. The increased weight of the lower wedge can generate a component force on the inclined plane mechanism, thereby greatly improving the static self-locking reliability of the inclined wedge mechanism and ensuring that the calibrated force value remains stable under load for a long time. At the same time, this configuration can balance most of the torque to be measured before applying force, which greatly reduces the external thrust required to move the upper wedge. This allows for the selection of a drive motor with lower power, lower cost, and higher control precision, thus optimizing the system's structure and energy consumption while ensuring the calibrated torque range. Attached Figure Description

[0021] Figure 1 This is a schematic diagram of the overall structure of the present invention;

[0022] Figure 2 This is a schematic diagram of the upper and lower wedge blocks of the present invention;

[0023] Figure 3 This is a schematic diagram of the key shaft and wedge block assembly structure of the present invention;

[0024] Figure 4 This is a schematic diagram of the transmission mechanism of the present invention.

[0025] In the diagram: 1. Base; 2. Lifting mechanism; 3. Drive mechanism; 4. Connecting shaft; 5. Tension sensor; 6. Lever arm; 7. Connecting plate; 8. Screw; 9. Transmission mechanism; 10. Tank body; 11. Base plate; 12. Key sleeve; 13. Key shaft; 14. Sliding shaft; 15. Spring; 16. Pipeline; 201. Outer frame; 202. Lifting seat; 203. Guide assembly; 204. Wedge block assembly; 2011. Vertical plate; 2012. Top plate; 2013. Bottom plate; 2031. Guide sleeve; 2032. Guide column; 2041. Upper wedge block; 2042. Lower wedge block; 901. Transmission shaft; 902. Wedge disk assembly; 903. Piston cylinder. Detailed Implementation

[0026] The embodiments of the present invention are described in detail below. These embodiments are implemented based on the technical solution of the present invention, and provide detailed implementation methods and specific operation processes. However, the scope of protection of the present invention is not limited to the following embodiments. In the description of the present invention, words such as "front", "rear", "left", and "right" that indicate orientation or positional relationship are only for the convenience of describing the present 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. Therefore, they should not be construed as limitations on the present invention.

[0027] An embodiment discloses a torque calibration device for a high-power dynamometer, such as Figures 1-4 As shown, it includes a base 1 and a lifting mechanism 2 mounted on the base 1. In addition, a drive mechanism 3 for lifting mechanism 2 is provided on one side of the lifting mechanism 2 to control the lifting of the lifting mechanism 2. A connecting shaft 4 is connected above the lifting end of the lifting mechanism 2. The upper end of the connecting shaft 4 is connected to the lever arm 6 of the loading device through a high-precision tension sensor 5.

[0028] During torque calibration, the drive mechanism 3 is operated, causing the lifting end of the lifting mechanism 2 to move the connecting shaft 4 downwards. The downward movement of the connecting shaft 4 applies a load to the dynamometer to be calibrated through the lever arm 6 mechanism. The force generated during this process is measured in real time by a high-precision tension sensor 5 connected in series in the force transmission path. Based on the pre-determined length of the lever arm 6, the measured force value is converted into a standard torque value. When the force value displayed by the tension sensor 5 reaches the preset calibration value, the movement of the lifting mechanism 2 is immediately stopped, and its current position is maintained by utilizing the mechanism's self-locking characteristic, thereby stabilizing the force value measured by the tension sensor 5 at the calibration value. With the force value remaining stable, the calculated standard torque value is compared with the torque reading displayed by the dynamometer's own measurement system, thus completing the calibration or standardization of the dynamometer's torque measurement accuracy.

[0029] During torque calibration using the above method, the lifting mechanism 2 must immediately stop operating when the tension sensor 5 reaches the preset calibration force value. At this point, whether the lifting mechanism 2 can continuously and stably maintain its current position under high load directly affects the accuracy of the force value shown by the tension sensor 5, and thus the final accuracy of the entire torque calibration. While traditional weight loading methods are simple in principle, they are cumbersome to operate when applying large tonnage loads and are difficult to achieve stepless force adjustment. While using a direct lifting mechanism 2 such as an electric hydraulic cylinder or lead screw can achieve controllable loading, the mechanism may drift due to internal force relaxation or elastic deformation under prolonged heavy loads, leading to unstable force values ​​and thus limiting further improvement in calibration accuracy.

[0030] To overcome the above limitations, in this implementation plan, such as Figures 1-3 As shown, a significant improvement has been made to the lifting mechanism 2: it has been designed as a wedge-based mechanism. This mechanism applies a push-pull force to the wedge in the horizontal direction via a driver, utilizing the guiding effect of the wedge surface to convert the horizontal motion into a vertical lifting motion, thereby achieving tensile and compressive loading on the object being measured. By precisely controlling the inclination angle of the wedge surface to meet the mechanical self-locking condition, the position can be locked entirely by the frictional resistance of the inclined surface after reaching its position, without the need for continuous external force. The wedge action not only provides a good force amplification effect but also significantly enhances the mechanism's resistance to displacement under load, thus providing a high-precision and highly stable force value reference for torque calibration.

[0031] In this embodiment, the lifting mechanism 2 is specifically composed of an outer frame 201, a lifting seat 202, a guide assembly 203, and a wedge block assembly 204. The outer frame 201 is fixedly installed on the base 1 and located on one side of the drive mechanism 3. Its structure consists of a top plate 2012, two vertical plates 2011 for support, and a bottom plate 2013. The top plate 2012 is fastened to the vertical plates 2011 on both sides, and the bottom of the vertical plates 2011 is fixed to the bottom plate 2013. The bottom plate 2013 is securely installed on the surface of the base 1 with screws.

[0032] The lifting seat 202 is mounted on the base plate 2013, and the bottom end of the connecting shaft 4 is directly fixed to the upper surface of the lifting seat 202, so that the vertical movement of the lifting seat 202 can be transmitted to the calibration arm 6 connected to the tension sensor 5. To ensure the accuracy of the lifting movement, the lifting seat 202 is guided and limited by the guide assembly 203. In addition, a wedge block assembly 204 is provided below the base plate 2013. The lifting seat 202 is connected to the wedge block assembly 204 through the guide assembly 203, so that the horizontal movement of the wedge block assembly 204 can be converted into the precise lifting movement of the lifting seat 202.

[0033] To further explain, such as Figures 2-3As shown, the guide assembly 203 includes guide sleeves 2031 and guide posts 2032. Four guide sleeves 2031 are evenly distributed and fixedly installed at the four corners of the upper surface of the top plate 2012. A guide post 2032 is slidably inserted into each guide sleeve 2031. The bottom end of the guide post 2032 extends downwards to below the top plate 2012, while its top end is fixedly connected to the bottom surface of the lifting seat 202. Through the cooperation of the guide sleeves 2031 and guide posts 2032, the lifting seat 202 is smoothly guided in the vertical direction.

[0034] The wedge assembly 204 consists of an upper wedge 2041 and a lower wedge 2042. The lower end of the upper wedge 2041 is inclined, and the upper end is flat. It is horizontally slidably connected to the bottom of the top plate 2012 via a slide rail. Its sliding direction is coaxial with the length direction of the wedge, and the lower inclined surface is also arranged in this direction, with the thicker end facing the drive mechanism 3. The lower wedge 2042 is located below the upper wedge 2041, and connecting plates 7 are fixed on both its front and rear sides. The guide post 2032 is detachably connected to the connecting plate 7 at its bottom end below the top plate 2012 via screws, so that the lower wedge 2042 can only move longitudinally under the constraint of the guide post 2032. The upper surface of the lower wedge 2042 is also inclined, and its inclination direction is symmetrically matched with the inclined surface of the upper wedge 2041. That is, the thicker end of the lower wedge 2042 corresponds to the thinner end of the upper wedge 2041, and the thinner end is closer to the drive mechanism 3. When the drive mechanism 3 pushes the upper wedge 2041 to move horizontally, the interaction of the inclined planes forces the lower wedge 2042 to move downward, thereby driving the lifting seat 202 to move downward, and finally subjecting the tension sensor 5 to a precise and controllable force.

[0035] In this embodiment, the lifting mechanism 2 adopts an inclined structure with upper and lower wedges 2042. By precisely setting the inclined angle of the wedges, it has a reliable self-locking function when the movement ends. This allows the force value to remain stable after the calibration force reaches the preset value and loading stops, effectively improving the accuracy and reliability of the calibration data. Furthermore, the lower wedge 2042 and the bottom of the guide post 2032 are detachably connected, allowing the user to flexibly replace the lower wedge 2042 module with one of appropriate weight according to different ranges of the torque to be calibrated. It should be noted that the total weight of the selected lower wedge 2042 and its connecting components should always be less than the minimum starting torque of the device under test to prevent its own weight from interfering with the initial position of the lever arm 6.

[0036] In the actual calibration process, for different torque ranges, a lower wedge 2042 with an appropriate weight range can be selected. Then, the upper wedge 2041 is moved horizontally by the drive mechanism 3, pushing the lower wedge 2042 to move vertically along the guide post 2032, thereby driving the calibration lever arm 6. The high-precision tension sensor 5 collects force data in real time. After each replacement of the lower wedge 2042, a strict "tare" operation must be performed: that is, after installing the new module and before applying the calibration force, the value displayed by the tension sensor 5 is reset to zero to eliminate the influence of the lower wedge 2042's own weight on the measurement results. Then, the formal loading is performed to obtain the true calibration force value. Finally, the standard torque is calculated by combining the length of the lever arm 6.

[0037] A key advantage of this embodiment is that, during high-torque calibration, when the loading stops and the lower wedge 2042 remains stationary, a portion of the torque load it bears is distributed by its own weight, rather than being entirely applied to the wedge-fitting inclined surface. This force decomposition mechanism significantly reduces the actual normal pressure on the inclined surface contact surface, thereby reducing minor errors caused by material elastic deformation and micro-slippage. Simultaneously, because the stress on the inclined surface is alleviated, wear and creep effects under long-term high-load conditions are suppressed, helping to maintain the accuracy and stability of the mechanism during repeated use. Therefore, even in high-torque calibration scenarios, this structure ensures that the force on the wedge pair remains within a reasonable range, improving the overall durability and measurement consistency of the device. Furthermore, by selecting an appropriate weight for the lower wedge 2042, increasing its weight during high-torque calibration directly reduces the thrust requirement for the upper wedge 2041, making the operation of the drive mechanism 3 (such as a manual wrench or servo motor) feel less strenuous, which in turn means that smaller, more economical electrical equipment can be used.

[0038] In this embodiment, as Figures 1-4 As shown, the mechanism driving the upper wedge 2041 to move horizontally employs a composite configuration of a screw 8 and a worm gear transmission. Specifically, a screw 8 is rotatably connected to the end of the upper wedge 2041 near the drive mechanism 3, and this screw 8 forms a helical pair with a threaded hole fixed on the vertical plate 2011. The power transmission path is as follows: the operator rotates the worm gear through an external electric drive device (such as a motor), driving the meshing worm gear to rotate; the inner hole of the worm gear is connected to the screw 8 through a transmission mechanism 9. Thus, when the worm gear rotates, the torque is transmitted to the screw 8 through the transmission mechanism 9, driving it to rotate around its own axis; during the rotation process, the screw 8, through its engagement with the threaded hole of the vertical plate 2011, converts the rotational motion into a horizontal thrust on the upper wedge 2041, thereby achieving precise lateral feed of the upper wedge 2041.

[0039] To ensure the calibration device can cover a wider torque range, this embodiment includes a dedicated weight-adding mechanism below the lower wedge 2042. By configuring an appropriate weight for this mechanism, the total weight of the lower wedge 2042 system can be effectively adjusted, thereby increasing the torque calibration range of the entire device without altering the main structure. Furthermore, to further simplify the operation and enhance equipment safety, this embodiment specifically designs the weight-adding method as automatic liquid weight-adding. Specifically, multiple parallel-connected sealed tanks 10 are fixed to the lower part of the lower wedge 2042, serving as liquid containers. In this configuration, the weight-adding action is coupled with the overload protection function of the transmission mechanism 9: when calibrating a large torque, if the operator has not pre-added counterweight, the overload protection device in the transmission mechanism 9 will automatically activate when the motor load exceeds a safety threshold, simultaneously triggering the liquid pumping system to inject liquid into the tanks 10, thus adding weight to the lower wedge 2042. This process not only avoids the risk of motor overload due to operational negligence, but also automates the counterweight operation, effectively improving the safety and efficiency of calibration work.

[0040] like Figures 2-4 As shown, the transmission mechanism 9 in this embodiment specifically includes core components such as a transmission shaft 901, a wedge disk assembly 902, and a piston cylinder 903. The transmission shaft 901 is fixedly connected to the inner ring of the worm gear, and the piston cylinder 903 is mounted on its inner ring in the form of a revolute joint, applying axial limiting to the piston cylinder 903 so that it can rotate around the shaft but cannot move axially. A base plate 11 is provided inside the worm gear box, and a key sleeve 12 is mounted on the plate. A key shaft 13 is movably inserted into the key sleeve 12. One end of the key shaft 13 is fixedly connected to the screw 8, and the other end is connected to the transmission shaft 901 through the wedge disk assembly 902. The wedge disk assembly 902 consists of two wedge disks arranged facing each other. On the opposing disk surfaces of the two disks, there are multiple wedge-shaped protrusions with inclined surfaces arranged in a circular array along the circumference, and the inclined surfaces of each protrusion are correspondingly engaged with each other. A sliding shaft 14 is fixed to the outer side of the wedge disk near the transmission shaft 901. The outer circumference of the sliding shaft 14 is machined with splines, forming a sliding spline engagement with the end of the transmission shaft 901. A spring 15 is fitted around the sliding shaft 14. The spring 15 acts between the wedge disc and the drive shaft 901, providing an axial force to continuously press the two wedge discs together. One end of the sliding shaft 14 is connected to the outer end of the piston rod of the piston cylinder 903. The piston cylinder 903 contains a piston. The cylinder is connected to two pipes 16: one is connected to an external water source, and the other is connected to the weight-increasing tank 10. Both pipes 16 are equipped with one-way valves to control the directional flow of liquid.

[0041] Based on the above structural configuration, under normal operating conditions, the self-weight of the lower wedge 2042 is preset to be less than the target calibration torque, and the difference between the two is controlled within a certain range. This design ensures that during calibration, the self-weight of the lower wedge 2042 is insufficient to directly cause displacement of the lever arm 6, while simultaneously reducing the propulsion resistance experienced by the upper wedge 2041 as it ascends the inclined plane through the decomposition of system forces. Therefore, during normal calibration, the required thrust is within the rated power range of the drive motor, and the system can operate stably. Through the matching design of the wedge plate inclination angle and the stiffness of the matching spring 15, when the required thrust exceeds the motor's load-bearing capacity, the wedge plate transmission pair can automatically disengage, achieving overload protection.

[0042] Under normal load conditions, the thrust required for the horizontal movement of the upper wedge 2041 is relatively small, and the wedge assembly 902 remains engaged. Power is transmitted to the drive shaft 901 via a worm gear, and the drive shaft 901 drives the key sleeve 12 to rotate through the wedge assembly 902. The key sleeve 12 drives the key shaft 13 to rotate, which in turn causes the screw 8 to rotate. Under the constraint of the threaded pair, the screw 8 is converted into axial displacement, thereby pushing the upper wedge 2041 to achieve lateral feed. When the rated torque increases significantly, causing the difference between the weight of the lower wedge 2042 and the target torque to be too large, the thrust required by the upper wedge 2041 will cause the motor to overload. At this time, the drive shaft 901 continues to rotate, but its torque will be converted into axial thrust through the inclined surface of the wedge, compressing the spring 15, causing the wedge closest to the drive shaft 901 to retract axially, resulting in the two wedges disengaging from contact, interrupting the transmission chain, and achieving mechanical protection.

[0043] When the transmission chain is disconnected, the continuous operation of the drive shaft 901 will be converted into the axial reciprocating motion of the wedge assembly 902. This reciprocating motion is transmitted to the piston rod of the piston cylinder 903 through the sliding shaft 14, driving the piston to perform a reciprocating pumping action, drawing in external water through the one-way pipe 16 and pressing it into the tank 10 connected to the lower wedge 2042, thus increasing the system weight. As the liquid level in the tank 10 rises, the total weight of the lower wedge 2042 gradually increases. When the difference between its weight and the target torque narrows to a preset range, the thrust required by the upper wedge 2041 falls back to within the safe load of the motor, and the wedge assembly 902 re-engages under the action of the spring 15, automatically rebuilding the transmission chain. At this time, the operator can pause the equipment, perform a tare operation on the sensor to deduct the added weight of the lower wedge 2042, and then continue to perform accurate torque calibration under this configuration.

[0044] In this embodiment, during operation: When the system starts and performs torque calibration, the drive mechanism 3 drives the transmission shaft 901 to rotate. Initially, due to the large difference between the weight of the lower wedge 2042 and the target torque, the thrust required to move the upper wedge 2041 may exceed the rated load of the motor. At this time, the wedge assembly 902 in the transmission chain enters the disconnection protection state: the continuous rotation of the transmission shaft 901 is converted into the axial reciprocating motion of the wedge assembly 902. This motion is transmitted to the piston cylinder 903 through the sliding shaft 14, driving the piston to perform reciprocating pumping action. The reciprocating motion of the piston draws in external water through the one-way suction valve and presses it into the sealed tank 10 rigidly connected to the lower wedge 2042 through the one-way discharge valve, thus increasing the system weight. As the mass of liquid in the tank 10 increases, the total weight of the lower wedge 2042 continues to increase, gradually reducing the difference between its own weight and the target torque to a preset safe range. When the thrust required by the upper wedge 2041 drops below the motor's safe load, the wedge assembly 902 automatically re-engages under the action of the preload spring 15, and the transmission chain resumes power transmission. Subsequently, the operator pauses the equipment and performs a "tare" operation on the high-precision tension sensor 5, returning the initial force value generated by the added weight of the lower wedge 2042 to zero. After tare, the upper wedge 2041 can be driven to move precisely under this stable configuration, completing the final torque calibration. The entire process achieves fully automated control from overload protection and automatic counterweight adjustment to precise calibration.

[0045] It will be apparent to those skilled in the art that the present invention is not limited to the details of the exemplary embodiments described above, and that the invention can be implemented in other specific forms without departing from its spirit or essential characteristics. Therefore, the embodiments should be considered in all respects as exemplary and non-limiting, and the scope of the invention is defined by the appended claims rather than the foregoing description. Thus, all variations falling within the meaning and scope of equivalents of the claims are intended to be included within the present invention. No reference numerals in the claims should be construed as limiting the scope of the claims.

Claims

1. A torque calibration device for a high-power dynamometer, comprising a base (1) and a lifting mechanism (2) mounted on the base (1), wherein a drive mechanism (3) for lifting control is provided on one side of the lifting mechanism (2), and a connecting shaft (4) is connected above the lifting end of the lifting mechanism (2), the upper end of which is connected to the lever arm (6) of a loading device via a high-precision tension sensor (5), characterized in that, The lifting mechanism (2) is a mechanism based on the wedge principle. It includes an upper wedge (2041) that can move horizontally and a lower wedge (2042) that can move vertically. The upper wedge (2041) is pushed to move horizontally by the driving mechanism (3), and the lower wedge (2042) is forced to move vertically by the inclined plane, thereby loading the tension sensor (5). Furthermore, the inclined plane angle of the wedge mechanism is set to meet the mechanical self-locking condition, so that the position can be maintained by frictional resistance after the loading stops. The lifting mechanism (2) includes an outer frame (201) and a guide assembly (203). The drive mechanism (3) includes a screw (8) and a worm gear transmission pair. The screw (8) is rotatably connected to the upper wedge (2041) and forms a helical pair with the threaded hole fixed on the outer frame (201). The worm gear drives the screw (8) to rotate, thereby converting the rotational motion into the horizontal linear motion of the upper wedge (2041). The drive mechanism (3) is connected to the screw (8) via the transmission mechanism (9). The transmission mechanism (9) includes a set of wedge disks (902). The wedge disks (902) consist of two wedge disks with inclined surfaces that engage with each other and are kept engaged under the action of the spring (15). When the transmission torque exceeds the set value, the wedge disks overcome the force of the spring (15) and disengage, interrupting the power transmission. The axial reciprocating motion of the wedge disk assembly (902) of the transmission mechanism (9) in the disengaged state is linked with a weight-adding mechanism. The reciprocating motion of the wedge disk assembly (902) drives the pumping component of the weight-adding mechanism to inject liquid into the sealed tank (10) connected to the lower wedge block (2042).

2. The torque calibration device for a high-power dynamometer as described in claim 1, characterized in that, The outer frame (201) is fixed on the base (1). The guide assembly (203) includes a guide sleeve (2031) disposed on the top plate (2012) of the outer frame (201) and a guide column (2032) fixedly connected to the lifting seat (202). The guide column (2032) and the guide sleeve (2031) slide together to guide the lifting seat (202) and the lower wedge (2042) to move smoothly in the vertical direction.

3. The torque calibration device for a high-power dynamometer as described in claim 2, characterized in that, The weight-increasing mechanism includes a sealed tank (10) fixed to the lower part of the lower wedge (2042), which adjusts the total weight of the lower wedge (2042) system by increasing the weight of the liquid in the tank (10).

4. The torque calibration device for a high-power dynamometer as described in claim 3, characterized in that, The transmission mechanism (9) includes a piston cylinder (903), the piston rod of which is connected to the wedge plate assembly (902) and driven by it to reciprocate, thereby drawing in external liquid through the pipeline (16) and pressing it into the sealed tank (10).

5. The torque calibration device for a high-power dynamometer as described in claim 1, characterized in that, The lower wedge (2042) is detachably connected to the guide assembly (203), allowing the lower wedge (2042) module of different weights to be replaced according to the range of the calibrated torque.

6. The torque calibration device for a high-power dynamometer as described in claim 1, characterized in that, The drive mechanism (3) is an electric drive device, which converts the rotational motion of the motor into the horizontal thrust of the upper wedge (2041) through a combination of worm gear transmission and helical pair.

7. The torque calibration device for a high-power dynamometer as described in claim 1, characterized in that, The screw (8) is connected to the wedge assembly (902) via a key shaft (13) and a key sleeve (12); the key shaft (13) is fixedly connected to one end of the screw (8), and one end of the key sleeve (12) is connected to the drive shaft (901) via the wedge assembly (902).

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