CN201364223Y

CN201364223Y - Fully-automatic rider type force calibration machine

Info

Publication number: CN201364223Y
Application number: CNU2008200725025U
Authority: CN
Inventors: 张学成; 李春光; 于立娟
Original assignee: Jilin University
Current assignee: Jilin University
Priority date: 2008-09-25
Filing date: 2008-09-25
Publication date: 2009-12-16
Anticipated expiration: 2018-09-25

Abstract

The utility model discloses a fully-automatic rider type force calibration machine, which overcomes the problems of low efficiency, narrow range of force value, poor service performance, larger defectiveness in fitness degree of the detection regulations of a dynamometer and the like of the existing force calibration machine. The fully-automatic rider type force calibration machine comprises a main machine, a lever transverse beam and a control system; a mode of knife-edge bearing is adopted between the lever transverse beam and a fulcrum on the main machine; the knife-edge bearing at the fulcrum comprises a fulcrum knife and a fulcrum knife bearing; the small-radius edge of the fulcrum knife and the smaller-radius groove of the fulcrum knife bearing are in contact connection; the mode of knife-edge bearing is also adopted between the lever transverse beam and a force point on the main machine; the knife-edge bearing on the force applying point comprises a force point knife and a force point knife bearing; the small-radius edge of the force point knife and the small-radius groove of the force point bearing are in contact connection; a mounting plate below the right end of the lever transverse beam is fixedly provided with a damper which comprises a liquid damper and a semiactive frictional damper; and the control system is provided with a computer which is provided with computer programs to realize visualized monitoring during working by running the computer programs.

Description

Full-automatic rider type force calibrator

Technical Field

The utility model relates to a be applied to mechanical measurement, production test field's standard force source device, more specifically say, it relates to a full-automatic trip code formula force calibrator that uses in metrological verification, calibration or the production test of being applied to various dynamometers.

Background

The force standard machine is used as an important link of a force value transmission system and is widely applied to metering departments, scientific research departments and force measuring instrument production and use departments. Among them, the lever machine is particularly favored because of its excellent cost performance. The lever type force standard machine utilizes the gravity of a weight with known mass to reproduce a force value according to the dynamic effect of the force, but the gravity of the weight with known mass is amplified by an unequal arm lever to generate the force value. In practice, lever force standards consist of a dead weight force standard plus a lever amplification mechanism. Therefore, the static gravity type force standard machine has the defects of the traditional static gravity type force standard machine, such as complex structure, narrow range of applied force values, few stages, low efficiency and high cost; in addition, in order to ensure the accuracy of the lever ratio, the structure adjustment process is complex, the realization difficulty is high, the working efficiency is lower, and the automatic work is difficult to realize. Overall, the main technical problems of such standard force sources include the following: the method has the advantages of low working efficiency, narrow force value range, poor service performance (low automation degree and poor simplicity), great defects in the applicability of the calibration procedure of the dynamometer, high cost, few new technical applications, no new structure and no new method.

Disclosure of Invention

The utility model aims to solve the technical problem that overcome prior art and had that work efficiency is low, the power value scope is narrow, performance is poor, there is great lack, with high costs to the suitability of dynamometry appearance examination regulation, new technical application is few, do not have the problem of new structure, new method, provide a full-automatic journey code formula force calibration machine of edge of a knife supporting.

In order to solve the technical problem, the utility model discloses an adopt following technical scheme to realize: full-automatic trip code formula power calibrator, including host computer, lever crossbeam, control system, full-automatic trip code formula power calibrator's lever crossbeam and host computer in adopt the connected mode of edge of a knife supporting between the fulcrum of 1 # framework entablature, the edge of a knife supporting of fulcrum department includes fulcrum sword, fulcrum sword and holds, the fulcrum sword holds the top of fixing at the lever crossbeam, the top at 1 # framework entablature in the host computer is fixed to the fulcrum sword, the cutting edge of fulcrum sword is connected with the groove contact of fulcrum sword.

The full-automatic rider type force calibrator is characterized in that a knife edge support connection mode is adopted between a lever cross beam and a force application point on a host, the knife edge support at the force application point comprises a force point knife and a force point knife bearing, the force point knife is fixed to the top of a reverse frame in the host, the force point knife bearing is fixed to the bottom of the lever cross beam, and a knife edge of the force point knife is in contact connection with a groove of the force point knife bearing.

On the basis of the technical scheme, a damper is arranged on a mounting plate below the right end of the lever beam and consists of a liquid damper and a semi-active friction damper, wherein the semi-active friction damper mainly comprises a switch, an eccentric shaft, a friction plate, a bearing, a motor and a signal plate).

The motor is fixedly arranged on a mounting plate below the right end of the lever beam, a vertical upward output shaft of the motor is fixedly connected with an eccentric shaft which is sequentially and fixedly provided with two eccentric wheels, bearings are respectively sleeved on the outer edges of the two eccentric wheels, two identical friction plates are fixedly arranged on the inner side walls of the lever beams on the two sides of the eccentric shaft, the two bearings can be respectively contacted with or separated from the two friction plates at the same time, two identical switches are fixed at the upper end of a support, the lower end of the support is fixed on the mounting plate, the included angle of the two identical switches in the horizontal plane at the upper end of the support is 90 degrees, and the symmetric center of the two switches and the two ends. This forms a second set of solutions. On the basis of the first and second schemes, the distance between the rider and the fulcrum of the lever beam is changed to reduce the force value variation, and when a displacement resolution unit delta is used, the force value variation is eliminated_LThe resolution delta of the displacement reduced component to be compensated for when the compensation force value is changed to delta F_LThe number of (A) is:

wherein,

L₁＝f₁(x，T，t)，L₁is a function of x, T, T,

L₂＝f₂(x，T，t)，L₂is a function of x, T, T,

L₁the distance of the rider from the fulcrum of the lever beam,

L₂the distance of the force application point from the fulcrum of the lever beam,

x. the position of the rider on the lever beam,

t, the ambient temperature,

t. time.

The control system in each technical scheme is provided with a computer which is loaded with a computer program and runs the computer program to enable the working process, each component state and the test process of the code type force calibrator to be displayed on a screen in an animation mode and realize that the mark on the animation is directly clicked to enable the code type force calibrator to complete the visualization monitoring of the working process with various control requirements.

Compared with the prior art, the beneficial effects of the utility model are that:

1. the utility model discloses a monolithic fixed mass weight utilizes the lever to enlarge the principle and applys the load to being target object. The magnitude of the applied force value is changed by changing and accurately controlling the position of the fixed mass weight along the length direction of the lever arm. Compared with the existing similar equipment, the sliding weight type force calibrator omits a complex gravity weight system, does not need to have accurate distance between a force point, a fulcrum and any key point for lever amplification, and adopts a rolling friction type knife edge support with mature technology for the force point, the fulcrum and the key point, so that the structure of the calibrator is greatly simplified and the calibrator is easy to manufacture.

2. The utility model discloses the drive and the control of the moving speed and the position of well fixed mass's weight along the lever arm length direction are realized through servo electric motor and microcomputer control device. The purpose of accurately applying force values is achieved by precisely controlling the positions of the weights, and the moving speed of the weights is increased so that the load applying speed can be increased. By means of microcomputer and advanced digital control technology, the problems of low loading speed, low efficiency and inconvenient operation of the lever type force standard machine are fundamentally solved, the accurate, rapid and automatic loading target of the force source device is realized, and the requirements of various standards on the load applied in the detection process of the dynamometer are completely met.

3. The utility model discloses add the uninstallation in-process and used liquid and controllable friction damping mechanism, this mechanism restraines initial balance's low-frequency swing in the course of the work, reduces and restraines the lever vibration of loading process to can shorten the reading stabilization time.

4. The utility model discloses a working process adopts visualization automatic monitoring, has realized man-machine operation dialogue, screen animation show the quick-witted operating condition of code walking and real-time power value dynamic curve, can judge the power value stable situation automatically, automatic acquisition test data to require to accomplish data processing and management according to the test standard of difference. The invented device is a high-precision, high-efficiency, high-reliability and low-cost working device.

Drawings

The invention will be further described with reference to the accompanying drawings:

FIG. 1 is a schematic diagram of a lever beam stress situation of a full-automatic code type force calibrator according to a statics principle under the condition of omitting influences of fulcrum and force application point friction, beam deformation and the like in consideration of a technical scheme;

FIG. 2 is a schematic diagram of a lever beam stressed situation of the full-automatic rider type force calibration machine under the condition of considering the frictional resistance in a knife edge support;

FIG. 3 is a front view of a knife-edge supported fully automatic rider-type force calibrator assembly;

FIG. 4 is an enlarged partial view taken at I of FIG. 3;

FIG. 5-a is a front view of a semi-active friction damper assembly in a fully automatic rider-powered force calibration machine;

FIG. 5-b is a left side view of a semi-active friction damper structural assembly in a fully automatic rider force calibrator with the lever beam front side wall removed;

FIG. 6 is an illustrative automated monitoring program interface provided by the full-automatic rider force calibrator on a computer screen in the control system;

in the figure: 1. the device comprises a lever beam, a No. 2.1 rack, a No. 3 movable beam, a No. 4 lead screw, a No. 5 sliding weight, a No. 6 guide rail, a No. 7 servo driving device, a No. 8 balance detection device, a No. 9 damper, a No. 10 reversing frame, a No. 11 workpiece, a No. 12 force point knife, a No. 13 fulcrum knife, a No. 14 switch, a No. 15 eccentric shaft, a No. 16 friction plate, a No. 17 bearing, a No. 18 motor, a No. 19 control system, a No. 20 ball lead screw, a No. 21 mechanical transmission system, a No. 22 main machine, a No. 23 fulcrum knife bearing and a No. 24 force. 25.2 # rack, 26 # mounting plate, 27 # signal plate, S # dynamometer, Q # centroid position line, m # weight, H # lever beam theoretical stress horizontal line.

Detailed Description

The present invention will be described in detail with reference to the accompanying drawings:

the utility model aims at seeking a power calibrator that cost performance is higher, overcome traditional lever power calibrator in the structure, with the problem of the aspect such as time, work efficiency, work process automation, error compensation and manufacturing use cost, reach efficiency, precision and the stability of precision, simplify structure, reduce cost's that improves power calibrator purpose.

Referring to fig. 1, the present invention provides a technical solution based on the lever principle. The loading mode that the fixed lever ratio of a traditional lever type force calibrator (or a force standard machine) and the size and the number of the weights of a single gravity weight are changed into a floating weight with single weight and fixed mass, and the purpose of changing the loading is achieved by changing the lever ratio when the gravity weight moves along the length direction of a lever beam 1. The gravity and other external forces of the lever are omitted, and the formula is provided according to the first lever amplification principle:

in the formula, F₁-gravity of rider, L₁Distance of the rider from the fulcrum, F₂-force applied to the object, L₂-distance of the force point from the fulcrum.

It can be seen that if L is₂Invariable, F₁Is constant when changing L₁Can change F when in size₂The size of (2). Thus, the control of the magnitude of the force value can be converted into the control of the precise position of the rider 5 on the cross beam 1. After the lever is precisely and automatically controlled to balance and measures such as improving the precision, accelerating the stable balance time and the like are taken, the full-automatic sliding code type force calibrator can be formed.

1. Analyzing problems associated with accurately applied force values

Referring to fig. 1, the lever beam AB is arranged, and the gravity generated by the left and right masses at the pivot point C is W₂、W₁The length of the position of the center of mass from the pivot is L₂₁、L₁₁. The weight with mass m can move along the lever beam AB, and the distance from the position of the weight at a certain moment to the fulcrum C is set as L₁With a gravity of F₁. The upper point B of the lever beam is the action point of the applied force, and the magnitude of the force is set as F₂At a distance L from the fulcrum C₂. The influences of friction, beam deformation and the like of a fulcrum and an applied force action point are omitted, and the method comprises the following steps of:

F₁×L₁+L₁₁×W₁＝F₂×L₂+_W2×L₂₁、

it can be seen that when the lever beam structure is determined, i.e. m, W₂、W₁、L₂₁、L₁₁、L₂I.e. determined. Downward force F generated by weight with mass m₁The force F is amplified by the lever beam and acts on the detected force meter₂Position L of weight m₁Is in direct proportion. Namely, the L can be changed without replacing the weight m₁Can realize the stage number and the size of the required load applied to the detected force meter, thereby being used for F₂Control of magnitude is converted into a pair displacement L₁And (4) controlling.

1) Under the condition of sufficient displacement resolution, the device achieves the purpose of applying different loads by changing the position of the weight so as to change the lever ratio (force-arm ratio), and compared with the traditional lever-type force calibrator, the only difference in the working principle is that the weight of the device moves instead of being fixed. In order to realize the aims of simplifying the structure, reducing the volume, reducing the cost and improving the working efficiency, the single-stage lever system is the simplest in structure. While the floating weight mass m should not and is unlikely to be too large, which necessarily increases the magnification ratio (leverage ratio) to accommodate the need for a large force value output.

Referring to fig. 2, in the error analysis, the force application error is caused by the change of the length of the lever beam arm in consideration of any reason, and the error is amplified because of the increase of the lever ratio and the reduction of the short arm size. The reasons that the arm length and thus the lever ratio may be changed can be summarized as the support, the lever deformation under force, the temperature, the hysteresis elastic effect, etc. The simplified mechanical model of the lever type force calibrator is arranged in an x-y plane coordinate system, and the lever beam can change under the action of factors such as external force, temperature and the like. It can be seen that the arm length is a function L of the position x, the temperature T and the time T of the code₁＝f₁(x，T，t)；L₂＝f₂(x，T，t)，

The error generated is

Control of the long arm L by changing the position of the rider 5₁The size and direction of the dimensional change can thus be reduced to eliminate errors. One displacement resolution unit delta_LThe force value change that can be compensated is Δ F, so the displacement that needs to be compensated is converted into the resolution number

For systems with good bearing repeatability, the force point values corresponding to the different positions of the rider 5 can be determined by calibration. If the time and temperature change rule is known, the force value error caused by the change rule can be compensated.

2) What support the lever beam takes is one of the main factors affecting the accuracy of the force application of the lever force calibrator, because of the moment of resistance generated at the fulcrum. The lever beam adopts various supporting forms and types, and for precision machines with larger loads, knife edge supporting and elastic supporting are adopted. For the knife edge support, when the radius of the knife edge is small and the swing angle of the moving part does not exceed 8-10 degrees, the friction in the knife edge support can be regarded as pure rolling friction. However, since the radius of the cutting edge cannot be too small, especially under heavy load, the knife edge support generates a friction torque, which is one of the main reasons for the force measurement error of the lever type force calibrator. The presence of friction torque at the knife edge support causes additional torque to the lever. At the moment, the balance of the lever beam is changed into F₁×L₁+L₁₁×W₁-M_f1＝F₂‘×L₂+W₂×L₂₁-M_f2In the formula M_f1And M_f2Friction moments at the fulcrum and force point, respectively. F₂' is the force present at the force point due to the friction torque. The error Δ F ═ F due to the friction at the cutting edge₂‘-F₂-[F₁×L₁/L₂+(W₁L₁₁-W₂L₂₁)/L₂]＝(M_f2-M_f1)/L₂. Because of the friction torque of the knife edge, force value errors are caused, and the size of the force value errors is equal to that of the short arm L₂In inverse proportion. Depending on the nature of the friction, the magnitude and direction of the friction torque varies with the movement state of the lever, over time, and cannot be compensated for by the above-described method. It is therefore necessary to try to reduce the friction torque.

3) Static balance is a necessary condition for the lever beam to work, however, in an initial state, it must be stable and the lever beam must be in a horizontal state, for which the center of mass of the lever beam must satisfy the following condition: the center of mass must be located on the vertical line passing through the fulcrum, and the connecting line of the center of mass of the left part and the right part of the lever taking the fulcrum as a boundary should also be horizontal and located below the fulcrum. Because the position of the mass center depends on the geometric shape, the lever type force calibrator and the balance are provided with a mass center adjusting mechanism. For the rider-type device, the balance state of the lever can be changed by changing the position of the rider 5, so that the position of the mass center can be adjusted, and a mass center adjusting mechanism of a traditional force calibrator can be omitted.

Any change in the rider position on the rider force calibrator will cause an imbalance in the lever (which is the basis for the application of force), and the device structure on the force line at the force point and the over-force point will deform in the direction of the force line because the device structure is not infinitely rigid. This deformation can be detected. If an equal amount of displacement occurs in the opposite direction of the deformation, the balance of the lever can be restored.

2. Detailed description of full-automatic rider type force calibrator structure adopting knife edge supporting mode

Referring to fig. 3 and 5, a full-automatic rider type force calibration mechanism using a knife edge support is shown. The device consists of a main machine 22, a lever beam 1 and a control system 19. The main machine is used for installing workpieces, adjusting space and bearing load, and the core components of the main machine are a No. 1 frame 2, a first servo driving device (not shown), a mechanical transmission system 21 and a movable cross beam 3. The movable beam 3 is provided with a workpiece to which force is applied, and the load generated by the lever beam 1 and transmitted to the workpiece through the reversing frame 10 is applied to the No. 1 frame 2 through the movable beam 3 and the lead screw 4. The movable beam 3 can be driven by a first servo driving device to perform precise linear displacement up and down for adjusting the space and realizing the balance of the lever beam 1; the lever beam assembly comprises a lever beam 1, a fulcrum knife 13, a force point knife 12, a vernier 5, a guide rail 6, a servo driving device 7, a balance detection device 8, a damper 9 and the like. The lever beam 1 can swing around a fulcrum, a connecting mode of a knife edge support is adopted between the lever beam 1 of the full-automatic code type force calibration machine and a fulcrum of a No. 1 frame upper beam in a host machine 22, the knife edge support at the fulcrum comprises a fulcrum knife 13 and a fulcrum knife bearing 23, the fulcrum knife bearing 23 is fixed at the top of the lever beam 1, the fulcrum knife 13 is fixed at the top of the No. 1 frame upper beam in the host machine 22, and a cutting edge of the fulcrum knife 13 is in contact connection with a groove of the fulcrum knife bearing 23. The connecting mode of a knife edge support is also adopted between the lever beam 1 and a force application point on the main machine 22, the knife edge support at the force application point comprises a force point knife 12 and a force point knife bearing 24, the force point knife 12 is fixed at the top of the reversing frame 10 in the main machine 22, the force point knife bearing 24 is fixed at the bottom of the lever beam 1, and the knife edge of the force point knife 12 is in contact connection with a groove of the force point knife bearing 24. The force point knife 12 and the fulcrum knife 13 are both long strip-shaped structural members with unchangeable cross sections, the cross sections can be regarded as a combination of an isosceles trapezoid and a triangle, the edge angle at the highest position is a knife edge, the radius of the knife edge is preferably 0.2mm, the fulcrum knife bearing 23 and the force point knife bearing 24 are also long strip-shaped structural members with unchangeable cross sections, the cross sections can be regarded as an isosceles trapezoid, a groove is processed on the narrow parallel sides, and the radius of the groove is preferably 0.3 mm. The force point knife 12 transmits force to the workpiece 11 through a reversing frame 10. The weight 5 can move linearly along the guide rail 6 on the lever beam 1, and the movement of the weight 5 along the lever beam 1 is driven by the servo drive device 7 through the ball screw 20, and the displacement is detected by the displacement sensor. The balance detection device 8 is a precision linear displacement sensor for detecting the balance position of the lever beam 1. The damper 9 is used to reduce vibration and speed up the balancing time. It consists of a liquid damper and a semi-active friction damper. The semi-active friction damper mainly comprises a switch 14, an eccentric shaft 15 for mounting two eccentric wheels, a bearing 17, a motor 18, a friction plate 16, a signal plate 27 and the like. The motor 18 is fixedly installed on an installation plate 26 below the right end of the lever beam 1 and between the front side wall and the rear side wall of the lever beam 1, the installation plate 26 is fixedly installed at the top of the No. 2 rack 25, the No. 2 rack 25 is sleeved outside the control system 19, and the lower end of the No. 2 rack is fixed on a foundation. The vertical upward output shaft of the motor 18 is fixedly connected (connected by a key or a flange) with the eccentric shaft 15 which is fixedly provided with two eccentric wheels in sequence, the outer edges of the two eccentric wheels are respectively sleeved with a bearing 17, two same friction plates 16 are fixedly arranged on the inner side walls of the lever beams 1 at the two sides of the eccentric shaft 15, the two bearings 17 can be respectively contacted with or separated from the two friction plates 16 at the same time, namely, when the two eccentric wheels are arranged on the eccentric shaft 15, the included angle between the wheel centers of the two eccentric wheels and the connecting line of the rotation axis of the eccentric shaft 15 is 180 degrees, namely, the connecting line of the wheel centers of the two eccentric wheels and the rotation axis of the eccentric shaft. Two identical switches 14 are fixed at the upper end of the bracket, an arc beam is fixed at the upper end of the bracket, the rotation center of the arc beam is concentric with the rotation center of the output shaft of the motor 18, the two identical switches 14 are fixedly arranged on the arc beam, the symmetry center of each switch 14 is connected with the rotation center of the output shaft of the motor 18, the included angle between the two center connecting lines is 90 degrees, one of the connecting lines is vertical to the orthographic projection surface of the main view, the other connecting line is parallel to the orthographic projection surface of the main view, namely, the connecting line is vertical to the projection surface of the left view, two identical switches 14 are visible at the same height, both in front view (fig. 5-a) and in left view (fig. 5-b), the lower end of the bracket being fixed to the mounting plate 26, the centres of symmetry of the two switches 14 being aligned with, or disengaged from, the two ends of the signal plate 27 which are located below and rotate simultaneously with the eccentric wheel. The signal plate 27 is a strip-shaped structural member, and is mounted on the uppermost eccentric wheel through a circular hole in the middle of the signal plate, and rotates together with the eccentric wheel, and the included angle between the symmetry line of the signal plate 27 and the connecting line of the wheel centers of the two eccentric wheels and the rotation axis of the eccentric shaft 15 is zero.

When the eccentric wheel is in operation, the motor drives the eccentric shaft 15 to rotate, and when the maximum eccentricity is approached, two identical bearings 17 sleeved on the outer edge of the eccentric wheel are respectively contacted with the friction plates 16 on two sides. When the friction plate 16 fixedly connected with the lever beam 1 swings up and down, friction force is generated, and proper friction plate materials are selected to enable the friction force to have positive damping characteristics in direct proportion to the relative movement speed, so that the damping effect is achieved. The magnitude of the frictional force is changed by adjusting the distance B, and the rotational position of the eccentric shaft 15 is detected by the switch 14.

The control system 19 is a set of control devices with a computer as a core. The working device comprising two sets of servo motor systems, a displacement detection system and a damper is controlled by a computer, a self-programmed computer program is installed in the computer, the computer program is operated to enable the working process, the state of each component and the test process of the sliding code type force calibrator to be displayed on a screen of the computer in an animation mode, and marks on the animation are directly clicked to enable the sliding code type force calibrator to meet various control requirements, so that the visual monitoring of the working process is realized. And meanwhile, data acquisition and data processing work is completed, and full-automatic work of the machine is realized.

The working principle of the full-automatic rider type force calibrator of the knife edge support:

when the system works, a workpiece 11 (such as a weighing sensor) is firstly placed on the reversing frame, the position of the movable beam 3 is manually adjusted to enable the workpiece 11 and the movable beam 3 to be in a state of contact but not contact (usually, the gap is 1mm, which is appropriate), and then the starting program starts to work. At the beginning, a servo motor system in a servo driving device 7 on the lever beam 1 drives the rider 5 to move, so that the lever beam 1 automatically searches for a balance position, and a damper 9 positioned at one end of the lever beam 1 plays a role in reducing amplitude in the balance process. The balance position is detected and determined by the displacement sensor. The load is then applied to the workpiece according to the programmed settings. The loading process starts with the movement of the driven beam 3, and after the contact of the driven beam and the workpiece is confirmed, a servo motor on the lever beam 1 is started to move the slider to a position to be loaded. The correct position is pre-calibrated and detected by the displacement sensor. At this point, the lever beam 1 will lose its balance due to the deformation of the mechanical system including the workpiece 11, and for this purpose the movable beam 3 position control motor is again activated, restoring the lever to balance. Meanwhile, the friction damper is started to reduce the swing amplitude of the lever beam and accelerate the stabilization time. Whether the workpiece is stable or not can be automatically judged by the controller according to the output of the workpiece 11. The friction damper is released after stabilization. At this point, the primary load application is complete. By analogy, loading and unloading of the workpiece can be realized. And after each stage of load loading and unloading is finished, the control system can acquire and process the data of the workpiece as required. The states of all components and the test process of the full-automatic rider type force calibration machine supported by the knife edge can be observed through a screen in the working process, and the movement and the action of the machine parts can be directly controlled on the screen in a mouse clicking mode during machine adjustment, so that the visual monitoring of the working process of the equipment is realized.

Examples

Referring to fig. 6, the following further illustrates the practice of the present invention in conjunction with practical examples.

1. The basic parameters of a full-automatic rider-type force calibration machine with the model number of 300kN are as follows:

the lever ratio i is 55;

the short arm of the lever beam 1 is 70mm long;

the total length of the lever beam 1 is 4200 mm;

run length 5 gravity 5600N;

the power of a motor for driving the sliding code to move is 750W, and the rated rotating speed is 2000 rpm;

the realized displacement resolution is 0.8 um;

the power of a motor driving the main movable cross beam to move is 750W, and the rated rotating speed is 2000 rpm;

the displacement resolution is 0.1 um;

a displacement sensor for detecting the balance of the lever beam 1, wherein the displacement range is +/-10 mm, and the resolution is 1 um;

2. the functional parameters of a full-automatic rider-type force calibration machine with the model number of 300kN are as follows:

rated load capacity: 300 kN;

resolution of force: 0.64N;

run length maximum speed: 4 mm/min;

the loading time can be realized: 20 s/stage;

and realizing an visualized automatic monitoring program interface.

Claims

1. A full-automatic sliding code type force calibrator comprises a host (22), a lever beam (1) and a control system (19), and is characterized in that a connecting mode of knife edge support is adopted between the lever beam (1) of the full-automatic sliding code type force calibrator and a fulcrum of a No. 1 frame upper beam in the host (22), the knife edge support at the fulcrum comprises a fulcrum knife (13) and a fulcrum knife bearing (23), the fulcrum knife bearing (23) is fixed at the top of the lever beam (1), the fulcrum knife (13) is fixed at the top of the No. 1 frame upper beam in the host (22), and a knife edge of the fulcrum knife (13) is in contact connection with a groove of the fulcrum knife bearing (23);

a knife edge support connection mode is also adopted between a lever beam (1) of the full-automatic rider type force calibration machine and a force application point on a host (22), the knife edge support at the force application point comprises a force point knife (12) and a force point knife bearing (24), the force point knife (12) is fixed to the top of a reverse frame (10) in the host (22), the force point knife bearing (24) is fixed to the bottom of the lever beam (1), and a knife edge of the force point knife (12) is in contact connection with a groove of the force point knife bearing (24).

2. The full-automatic rider-type force calibrator according to claim 1, wherein a damper (9) is mounted on a mounting plate (26) below the right end of the lever beam (1), and is composed of a liquid damper and a semi-active friction damper, and the semi-active friction damper is mainly composed of a switch (14), an eccentric shaft (15), a friction plate (16), a bearing (17), a motor (18) and a signal plate (27);

the motor (18) is fixedly arranged on a mounting plate (26) below the right end of the lever beam (1), a vertical upward output shaft of the motor is fixedly connected with an eccentric shaft (15) which is sequentially and fixedly provided with two eccentric wheels, bearings (17) are respectively sleeved on the outer edges of the two eccentric wheels, two identical friction plates (16) are fixedly arranged on the inner side walls of the lever beam (1) on two sides of the eccentric shaft (15), the two bearings (17) can be respectively contacted with or separated from the two friction plates (16) simultaneously, two identical switches (14) are fixed at the upper end of a support, the lower end of the support is fixed on the mounting plate (26), an included angle of the two identical switches (14) in a horizontal plane at the upper end of the support is 90 degrees, and the symmetric centers of the two switches (14) and two ends of a signal plate (27) which rotates along with the.