CN101943544B - Double-lever type press - Google Patents

Double-lever type press Download PDF

Info

Publication number
CN101943544B
CN101943544B CN 201010271316 CN201010271316A CN101943544B CN 101943544 B CN101943544 B CN 101943544B CN 201010271316 CN201010271316 CN 201010271316 CN 201010271316 A CN201010271316 A CN 201010271316A CN 101943544 B CN101943544 B CN 101943544B
Authority
CN
China
Prior art keywords
lever
crossbeam
counterweight
force
loading
Prior art date
Application number
CN 201010271316
Other languages
Chinese (zh)
Other versions
CN101943544A (en
Inventor
杨丽侠
张学成
于立娟
周岚
靳建伟
黄小梧
张衡
刘来东
张邹邹
Original Assignee
西安近代化学研究所
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 西安近代化学研究所 filed Critical 西安近代化学研究所
Priority to CN 201010271316 priority Critical patent/CN101943544B/en
Publication of CN101943544A publication Critical patent/CN101943544A/en
Application granted granted Critical
Publication of CN101943544B publication Critical patent/CN101943544B/en

Links

Abstract

The invention discloses a double-lever type press, which comprises a frame, a loading lever system and an electric control system. The loading lever system is positioned on the top of the frame; the frame has a frame structure; a balanced lever system is arranged below the loading lever system; two sets of lever systems are horizontally arranged and are parallel; a crossbeam of a loading lever 1 in the loading lever system works according to the principle of the second type of lever, a pivot is positioned at one end of the crossbeam of the loading lever 1 and a force point is positioned in the middle of the crossbeam of the loading lever 1; the balanced lever works according to the principle of the first type of lever, a pivot is positioned in the middle of the lever and a force point is positioned at one end of the lever; the force point of the crossbeam of the loading lever 1 and the force point of the crossbeam of the loading lever 2 are coupled through a reverse frame; the distances between the pivots and the force points of the two sets of levers are equal; the pivots are positioned in the same vertical line; a loading weight of the crossbeam of the loading lever 1 can move along the crossbeam of the lever; and the crossbeam of the loading lever 2 can balance the gravity of the crossbeam of the loading lever 1 and the loading weight.

Description

Double-lever type press
Technical field
The present invention relates to a kind of power value loading tester of plastic deformation manometric method static pressure calibration of measuring for gun pressure, relate in particular to a kind of Double-lever type press.
Background technology
Breech pressure is one of important tactical and technical norms of all kinds of armament systems, be estimate that products such as comprising rifle, big gun, automatic weapon and bullet, fuse, propellant powder use and security performance must survey parameter, be that its scientific research and design of check, development and production and product are delivered for a check the extremely important characterisitic parameter of a plurality of links.The plastic deformation manometric method has easy to use, only need a plasticity pressure measurement device (plasticity sensing element copper post (ball), manograph), simple to operate, reliable and the economic dispatch plurality of advantages of data stabilization, therefore, be widely used in the research and production of various rifles, big gun, bullet, medicine, applying unit country-wide military enterprise, scientific research institutions, proving ground.For a long time, plastic deformation manometric method adopts the static calibration system.The method of static calibration is after copper post (ball) is applied accurately active force according to certain load mode, measure the deflection of copper post (ball), examine its repeatability, stability, and then the relation that draws between pressure and amount of plastic deformation obtains the static pressure table of comparisons.
Apply accurate power and generally add static load with counterweight on forcing press and realize on copper post (ball), the gravity of known quality counterweight is amplified to produce the power value through multiplying lever.Lever ratio is fixed, and realizes applying different power values by quantity and the size that changes the gravity counterweight.The power value degree of accuracy that this forcing press exists is relatively poor, inefficiency, the power numerical series is limited, power value scope is little, the upper line of action of copper post (ball) and copper post (ball) axis have the drift angle, easily produced the uneven shortcoming of end face by school copper post,
Summary of the invention
Technical problem to be solved by this invention is to have overcome shortcomings and deficiencies of the prior art, and a kind of Double-lever type press is provided.This Double-lever type press not only have the degree of accuracy of power value better, operating efficiency is higher, power value scope is large, and the upper line of action of copper post (ball) with copper post (ball) axis without the drift angle, by the parallel advantage of school copper styletable face.
In order to solve the problems of the technologies described above, Double-lever type press of the present invention, comprise frame, load lever system and electric-control system, described loading lever system is positioned at the top of frame, it is characterized in that, described frame is frame structure, and its underpart is fixedly connected with base plate, and the fulcrum on its upper beam is connected for knife-edge support with loading between lever 1 crossbeam; Described loading lever system below is provided with the balanced lever system, two cover lever system horizontal positioned, and parallel; Load and load lever 1 crossbeam in lever system according to the work of second-class lever principle, its fulcrum is positioned at an end that loads lever 1 crossbeam, and the force is positioned at the middle part that loads lever 1 crossbeam; Balanced lever is according to the work of lever of first order principle, and its fulcrum is positioned at the middle part of lever, and the force is positioned at an end of lever.The force that loads lever 1 crossbeam connects by reverse frame with the force of balanced lever 2 crossbeams, and two overlap the fulcrum of levers equates with distance between the force, and fulcrum is positioned on same plumb line.The loading counterweight that loads lever 1 crossbeam can be along the lever crossbeam shift position, thereby changes the lever ratio size; Balanced lever 2 crossbeams can balance load lever 1 crossbeam and the gravity that loads counterweight, and by the counterweight counterweight of a fixed mass, the gravity of its generation is as the power of lever.
Double-lever type press of the present invention loads in lever 1 crossbeam along the gravity counterweight of lever crossbeam shift position and adopts Split type structure.Gravity counterweight 6 is comprised of body counterweight 19 and link code 18 two parts.Body counterweight 19 and link code 18 are fastenedly connected by attachment pegs 22, holding screw 23, and link code 18 connects by line slideway 21 with lever crossbeam.Attachment pegs 22 is arranged on body counterweight 19, and axis is parallel with the counterweight moving direction, and holding screw 23 is arranged on link code 18, is in vertical, and line slideway 21 is arranged on lever crossbeam.Only need use link code 18 when applying small value force, unclamp holding screw 23 this moment, simultaneously body counterweight 19 use lock-screws 20 fixed and are locked on lever crossbeam, and lock-screw 20 is arranged on body counterweight 19, is in the vertical direction with the counterweight moving direction.
Double-lever type press of the present invention is the initial position that is calculated as follows gravity counterweight when determining the lever initial balance:
L 0 = - P 0 L 2 W
P wherein 0Be the active force that is produced by the gravity that loads lever 1 crossbeam and gravity counterweight, W is the gravity of gravity counterweight, L 2It is the distance between fulcrum and force;
Be calculated as follows the size of the active force P that sample is applied:
P = P 0 + W L 2 × L
Wherein the initial value of arm of force L is L 0.
Compared with prior art the invention has the beneficial effects as follows:
1. the present invention adopts double lever to load, the fulcrum, the force that make top load fulcrum, force and bottom balanced lever 2 crossbeams of lever 1 crossbeam form parallelogram, two fulcrums on a plumb line and the arm of force in two lever forces equate, assurance is during to the sensing element imposed load, the direction vertical of exerting a force is downward, without the drift angle, guarantee that on stressed copper post, bottom surface is parallel with copper post (ball) axis.Compare with existing same category of device, forcing press has fundamentally solved the uneven problem in copper post upper and lower end face that copper post on traditional lever punch press is pressed rear appearance.
2. the loading lever system of Double-lever type press of the present invention adopts the fixed mass counterweight as gravity source when work, utilize lever amplification principle to move loading to sensing element, and accurately Detection ﹠ Controling automatically of displacement, in test process, counterweight needn't be changed, and the control that is about to apply size, the degree of accuracy of power value and the afterburning speed of power value is converted into to be controlled the accurate, quick of counterweight displacement.The gravity counterweight that has so just saved the complexity that traditional forcing press has adds unloading system, machine construction is simplified greatly, and easily be automated.
Can add again the counterweight of fixed mass on above-mentioned mobile counterweight basis, thereby guarantee to make the expanded range of loading force value under the accurate prerequisite of power value.
3. the movement of the counterweight of the loading lever system fixed mass of Double-lever type press of the present invention realizes by the driven by servomotor ball screw framework, by microcomputer and digital control technology, speed and the position of counterweight are controlled, and the size, precision and the speed that like this copper post are applied the power value of static force are all controlled.Solve fundamentally that the lever punch press loading velocity is slow, efficient is low, unhandy problem, meet weapon gun pressure plasticity pressure measurement static calibration fully to the requirement of sensing element imposed load.
4. the loading technique in Double-lever type press of the present invention is used for copper post (ball) load test, the geometric error on gear shaper without theoretical and power value error.The actual error main source is to bring because there is friction in knife-edge support, can be reduced so that eliminate by the quality that the raising cutter holds.Other error can and increase the measures such as the rigidity of structure, raising displacement control accuracy by reasonable structure design and control the very little degree that reaches.
5. the present invention can compensate by changing mobile counterweight displacement for the error of known rules, realizes high accuracy by precisely controlling displacement.This is also the advantage of uniqueness of the present invention, is that traditional lever punch press can't be realized.
Description of drawings
The present invention is further illustrated below in conjunction with accompanying drawing:
Fig. 1 is copper post (ball) manometric method know-why schematic diagram;
Fig. 2 is the lever load system fundamental diagram of Double-lever type press;
Fig. 3 is the lever view of Double-lever type press after the copper post is stressed;
Fig. 4 is copper post schematic diagram that affects on machine work when placing disalignment;
The stress envelope that when Fig. 5 is copper post placement disalignment, cutter holds;
Fig. 6 is special-purpose Double-lever type press structural principle;
Fig. 7 is special-purpose Double-lever type press planform figure;
Fig. 8 is Double-lever type press gravity counterweight 6 structural representations.
parts list: 1. load lever 1 crossbeam, 2. balanced lever 2 crossbeams, 3. the force cutter that loads lever 1 holds, 4. the force cutter of balanced lever 2 holds, 5. the fulcrum pivot that loads lever 1 holds, 6. loading counterweight, 7. balance detecting device, 8. the fulcrum pivot of balanced lever 2 holds, 9. the counterweight counterweight of balanced lever 2, 10. frame, 11. ball-screw, 12. servomotor 1, 13. base plate, 14. feed screw nut, 15. servomotor 2, 16. support, 17. electric-control system, C. reverse frame, D. move crossbeam, 18. link code, 19. body counterweight, 20. lock-screw, 21. guideway, 22. attachment pegs, 23. holding screw.
The specific embodiment
Below in conjunction with accompanying drawing, the present invention is explained in detail:
The objective of the invention is to seek a kind of high efficiency, the application of force (big or small direction) power adjusting machine accurately, overcome traditional copper column press in load time, operating efficiency, automaticity, apply the problem aspect power value size direction accuracy, make weapon gun pressure plasticity pressure measurement static calibration reach the purpose of high accuracy, high efficiency, wide region, automation.
1. know-why
The technical method requirement that copper post sample loads, two member A and B have respectively plane E and F, and E are parallel with F, sample (copper post) are installed, with reference to figure 1 between member.When two members do relative motion along copper mast axis direction, and keep E parallel with F, there is no relative motion with copper mast axis vertical direction, make the copper post be subject to pure pressure-acting and produce distortion.
2. the loading principle of Double-lever type press
With reference to figure 1, Figure 2 shows that a lever load system operation principle, it is comprised of 1,2 liang of cover lever system.Lever system 1,2 crossbeam all are in level, its supporting and stressed being shown in figure.Wherein W is the gravity of removable counterweight, W 1Be the gravity that the equivalent mass on hinged right side in the middle of lever 1 produces, W 2The gravity that produces for the equivalent mass in hinged left side in the middle of lever 1; W 3Be the gravity that the equivalent mass in hinged left sides in the middle of lever 2 produces, W 4The gravity that produces for the equivalent mass (comprising the vertical rod quality) on hinged right sides in the middle of lever 2; Copper post sample is placed in a rectangular frame, by a beam supporting.Respectively have up and down a vertical rod to be connected with lever with lever 1 by frictionless hinge in rectangular frame and be connected, two vertical rods are coaxial with the copper mast axis.Two vertical rods apply active force P to lever 1 and lever 2 respectively 1And P 2According to the standing balance principle of lever, get the equilibrium equation of lever 1
W×(L+L 2)+W 1×(L 1+L 2)+W 2×L 22=P 1×L 2??(1)
The equilibrium equation of lever 2
W 3×L 3-W 4×L 44=P 2×L 4?(2)
If the active force that sample is applied is P, the equilibrium equation of vertical rod
P = P 1 - P 2 = W × ( L - L 2 ) + W 1 × ( L 1 + L 2 ) + W 2 × L 22 L 2 - W 3 × L 3 - W 4 × L 44 L 4 (3)
= W 1 × ( L 1 + L 2 ) + W 2 × L 22 L 2 - W 3 × L 3 - W 4 × L 44 L 4 + W + W L 2 × L = P 0 + W L 2 × L
As seen after lever quality, lever arm length are determined, active force P and arm of force L that sample is applied namely are directly proportional to the position of mobile counterweight on crossbeam.
The initial balance condition:
P=0 during initial balance, L=L 0, solve
L 0 = - P 0 L 2 W - - - ( 4 )
As seen can guarantee the initial balance of lever by the position of regulating counterweight.
3. elementary error analysis
(1) Error Analysis
For making the stressed rear upper bottom surface of copper post parallel, the vertical rod in Fig. 2 should under any circumstance be in the vertical state all the time, and center of effort's line should be consistent with copper post center line simultaneously.
1. the geometric error that causes of deviation of lever
If each bar is rigid body, because making lever, stressed change departs from equilbrium position one angle θ, see Fig. 3.If make L2=L4, because lever 1,2 crossbeam are parallel, so vertical rod will keep the vertical state, and two plane parallel of sample do not have theoretical error.But vertical rod meeting translation, two hinged meetings of vertical rod move up and down.If lever rotates θ angle, upper and lower displacement detected value
h=L 5sinθ(5)
Detect worst error Δ h if establish max, hard-over θ max
θ max = sin - 1 Δ h max L 5 - - - ( 6 )
If hard point translation δ in up and down gets according to geometrical relationship
δ=L 2(1-cosθ)(7)
Visible detection and control make Δ h maxEnough little, up and down hard point shift value is ignored.To sum up, this loading method is being worked as the L that satisfies condition 2=L 4And L 5Large, when accuracy of detection is higher, the geometric error of load test can be ignored.
2. sample is placed disalignment to the impact of machine work
During load test, sample is placed may disalignment.If sample is along lever length direction deviation distance Δ, as shown in Figure 4.Can get according to the standing balance principle
P=P 1-P 2
P·Δ=T 2·h
T 1 = T 2 = P · Δ h - - - ( 8 )
T wherein 1, T 2Be respectively the side force at two hinged places, h is two distances between hinged.As seen sample is placed along the lever length direction power P of influence on sample not, but hinged place has side force, and h is larger, and side force is less.If hinged is knife-edge support, because being subjected to lateral forces, can increase the wearing and tearing that cutter holds.
Sample is placed disalignment also may along the blade parallel direction, establish the deviation distance Δ 1, see Fig. 5.The power P that act on sample on according to the standing balance principle this moment is unaffected, but hold will be uneven along blade direction stress distribution for cutter, as shown in Figure 5.Obvious Δ 1Larger, the stress distribution gradient is just larger, will cause an end stress of blade larger, increases the wearing and tearing that cutter holds.
3. the geometric error that causes of lever strain, manufacture accuracy
Because each member is not all rigid body, thereby can cause strain, the reason due to machine-building also can make member depart from the tram simultaneously, will inevitably cause geometric error thus, and focusing surface is not parallel up and down to make copper post sample.These problems can be by increasing stiffness of structural member, improving the manufacture accuracy solution.
(2) power value error analysis
1. lever crossbeam departs from the power value error that horizontal level causes
Omit moment of friction, establishing member is rigid body.Because lever crossbeam departs from horizontal level, bias angle theta, as shown in Figure 2, this moment, active force was made as P ', got according to standing balance
P ′ = P 1 - P 2 = W 1 × ( L 1 + L 2 ) cos θ + W 1 × L 22 cos θ L 2 ′ cos θ - W 3 × L 3 cos θ - W 4 × L 44 cos θ L 4 ′ cos θ (9)
+ W + W L 2 ′ cos θ × L cos θ = P 0 + W L 2 × L
As seen, the angle of revolution does not change equilibrium condition, does not change application of force value size yet.
2. the power value error that causes due to the moment of friction that supports
If the supporting-point of lever is knife-edge support, the edge of a knife can produce certain moment of friction.Can cause the error of the active force P that sample is applied due to edge of a knife moment of friction.Following lever 1 equation of static equilibrium formula of standing balance when considering moment of friction
W×(L+L 2)+W 1×(L 1+L 2)+W 2×L 22+M 12-M 11=P 1×L 2(10)
Lever 2 equation of static equilibrium formulas
W 3×L 3-W 4×L 44-M 21-M 22=P 2×L 4(11)
If the active force P ' that sample is applied, vertical rod equation of static equilibrium formula
P ′ = P 1 - P 2
= W × ( L + L 2 ) + W 1 × ( L 1 + L 2 ) + W 2 × L 22 + M 12 - M 11 L 2 - W 3 × L 3 - W 4 × L 44 - M 21 - M 22 L 4
= W 1 × ( L 1 + L 2 ) + W 2 × L 22 + M 12 - M 11 L 2 - W 3 × L 3 - W 4 × L 44 - M 21 - M 22 L 4 + W + W L 2 × L - - - ( 12 )
= P 0 ′ + W L 2 × L
So power value error
δP = P - P ′ = P 0 - P 0 ′ = M 12 - M 11 L 2 + M 21 + M 22 L 4 = M 12 - M 11 + M 21 + M 22 L 2 - - - ( 13 )
Conclusion: when member was rigid body, application of force error was mainly caused by edge of a knife friction, increases L 2Be conducive to reduce error.Usually very little when the θ angle, when edge radius was very little, moment of friction was very little so that can ignore [4], and the power value error that therefore causes thus can be ignored.
3. the power value error that causes of displacement accuracy
According to formula (3), the power that acts on sample is proportional to L.Differentiate gets to formula (3)
dP dL = W L 2 - - - ( 14 )
Be that unit displacement changes the quality that the power value variation that causes is proportional to mobile counterweight, with L 2Be inversely proportional to.Being write following formula as differential form has
ΔP = W L 2 ΔL - - - ( 15 )
Following formula is illustrated in the power value error size that produces when the minimum resolution of displacement is Δ L.
4. the power value error that causes of lever strain
For the member of actual device, it is all the elastomer that can produce distortion after stressed.Suppose to cause that in Fig. 1, each several part arm of force size changes after stress deformation, so formula (3) is got as total differential
dP = ∂ P ∂ L dL + ∂ P ∂ L 1 d L 1 + ∂ P ∂ L 2 d L 2 + ∂ P ∂ L 3 d L 3 + ∂ P ∂ L 22 d L 22 + ∂ P ∂ L 44 d L 44 =
W L 2 dL + W 1 L 2 d L 1 + W 2 L 2 d L 22 + W 3 L 2 dL 3 + W 4 L 2 d L 44 - - - - ( 16 )
W 1 × ( L 1 + L 2 ) + W 2 × L 22 - W 3 × L 3 + W 4 × L 44 L 2 2 d L 2
To sum up, power value composition error is
∑=δP+ΔP+dP??(17)
Adopt the premium properties knife-edge support, reduce the displacement control resolution, increase the stiffness of structural member Reducing distortion and all can subtract the small value force error.Simultaneously, according to formula (15), if any systematic error is arranged in system, can be compensated by the size that changes L, and then improved precision.
4. to the detailed description of Double-lever type press structure
Consult Fig. 2 and Fig. 6, Figure 2 shows that the lever load system operation principle, it is comprised of up and down two cover lever systems.The crossbeam of up and down two cover lever systems all is in level, its supporting and stressed being shown in figure.Wherein W is the gravity of removable counterweight, W 1Be the gravity of the equivalent mass generation on hinged right side in the middle of top loading lever, W 2For loading the gravity that the equivalent mass in hinged left side produces in the middle of lever; W 3Be the gravity that the equivalent mass in hinged left side in the middle of the balanced lever of bottom produces, W 4The gravity that produces for the equivalent mass (comprising the vertical rod quality) on hinged right side in the middle of balanced lever; Sensing element copper post (ball) is placed in a rectangular frame, by a beam supporting.Respectively have up and down a vertical rod to be connected with balanced lever with the loading lever by frictionless hinge in rectangular frame, two vertical rods are coaxial with the copper mast axis.Two vertical rods apply active force P to loading lever and balanced lever respectively 1And P 2
Shown in Figure 6, Double-lever type press is divided into four major parts on the whole, i.e. frame, loading lever system, balanced lever system and electric-control system.Described loading lever system is located at the top of frame, servomotor 12, ball-screw 11 and balance detecting device 7 that it comprises that the fulcrum pivot that loads lever 1 crossbeam 1, loads lever 1 crossbeam holds 5, the force cutter that loads lever 1 crossbeam 1 holds 3, loads counterweight 6, rider moves; The fulcrum pivot that loads lever 1 crossbeam holds 5 and is positioned at the one end, the force cutter that loads lever 1 crossbeam holds 3 and is positioned at its middle part, the point of application that loads lever 1 crossbeam is positioned at cutter and holds 3 opposite side, and by loading counterweight 6 application of forces, and the point of application changes on crossbeam along its length.This fulcrum is called second-class lever at the lever system of lever one end.
Below described loading lever 1 crossbeam 1, the balanced lever system is set below the middle beam of frame, described balanced lever system comprises that balanced lever 2 crossbeams, balanced lever 2 fulcrum pivots hold 8, balanced lever 2 force cuttves hold 4, counterweight counterweight 9.Load lever 1 crossbeam and balanced lever 2 crossbeams two of up and down lever crossbeams by a reverse frame C respectively through cutter hold 3 and cutter hold 4 and link together.Oppositely frame C is also the rectangular frame of above-mentioned placement sensing element copper post (ball).The fulcrum pivot of balanced lever 2 crossbeams holds 8 and is positioned in the middle part of balanced lever 2 crossbeams, the force cutter of balanced lever 2 crossbeams holds 4 ends that are positioned at balanced lever 2 crossbeams, the point of application of balanced lever 2 crossbeams is positioned at the other end of crossbeam, and active force is the gravity that counterweight counterweight 9 produces.This fulcrum is called lever of first order at the lever system at lever middle part.On structure, load the force of lever 1 and the force of balanced lever and be on same plumb line, load the fulcrum of lever 1 and the fulcrum of balanced lever and be on same plumb line.
Oppositely frame C is the framework of a geometry to holding, 3 groove contact connections are held by force, vertical rod upper end cutter and the force cutter cutter that loads lever 1 crossbeam in its upper end, and 4 groove contact connections are held by the force cutter of a vertical rod bottom force cutter and balanced lever 2 crossbeams in its lower end; Frame is that the load of machine is born main body, and its part comprises frame 10, moving crossbeam D, transmission mechanism 14, drive motors 15.Moving crossbeam D can do under the drive of drive motors 15 and move up and down motion, and the upper plane of moving crossbeam D is level all the time, and moving crossbeam D can also self-locking, makes it be unlikely to fall voluntarily when not moving.The active force in machine when work by cutter hold 5, cutter holds 3, oppositely frame C, test specimen, moving crossbeam D are applied on frame 10; Electric-control system is used for the course of work of controlled pressure machine, and electric-control system 17 comprises control device and switch board.A support member 16 is installed at the top of switch board, be used for supporting loading lever crossbeam 1 when the forcing press off working state, control device is arranged in switch board, be one to be embedded with the device that computer is core, computer is equipped with computer program, and the operation computer program makes the course of work of double lever forcing press, each structure state all can be presented on computer screen, realize course of work monitoring, and data acquisition and data processing work, realize the fully automatic working of forcing press; Base 13 is positioned at the bottom of forcing press, is used for support frame and switch board.
Install on the top cross-bar of frame 10 and load lever system.Load gravity counterweight 6 is installed on lever 1 crossbeam, gravity counterweight 6 is load on lever 1 crossbeam can be along this crossbeam length direction moving linearly, and driven by ball-screw 11.Ball-screw 11 is driven by servomotor 12, and detects gravity counterweight 6 in the displacement that loads on lever 1 crossbeam by the encoder that servomotor carries.Load install on lever 1 crossbeam the force cutter hold 3 and fulcrum pivot hold 5 (seeing Fig. 5, Fig. 6), with the end of gravity counterweight 6 opposite ends, balance detecting device 7 is installed loading on lever 1 crossbeam.The balanced lever system is installed below the middle beam of frame 10, the force cutter that balanced lever 2 is installed on balanced lever 2 crossbeams hold 4 and the fulcrum pivot of balanced lever 2 crossbeams hold 8 (seeing Fig. 5, Fig. 6), and fixed weight 9.Load lever system and balanced lever system two of up and down lever system by fulcrum pivot on the end of the vertical rod up and down of reverse frame C respectively with the force cutter of loading lever 1 hold 3 and the force cutter of balanced lever 2 hold 4 and connect.The blade that all knives holds should be parallel, the force cutter that loads lever 1 hold 3 and the force cutter of balanced lever 2 hold 4 blades in same plane.During lever balance, the length direction that loads lever 1 crossbeam and balanced lever 2 crossbeams should be vertical with this plane.
Moving crossbeam D is driven by feed screw nut 14, and this feed screw nut is driven by servomotor 15.Servomotor 15 is fixed on frame 10.Electric-control system 17 is arranged on frame 10 1 sides, and on base plate 13, it is support 16 that a support member is installed at the top of switch board, when lever is in nonequilibrium condition, with its supporting loading lever 1 crossbeam 1.
During work, at first the initial position according to formula (4) adjustment gravity counterweight 6 makes lever be in poised state, and poised state is detected by displacement detector 7.Then control system is controlled gravity counterweight 6 and is moved to the position that requires that sample is added load, crossbeam D is moved sample is applied active force, is in the equilbrium position until checkout gear detects lever, adds load complete.The translational speed of moving crossbeam D has namely been controlled loading velocity.
The present invention uses
The basic parameter of Double-lever type press of the present invention is:
Load lever crossbeam length 2000mm, maximum amplification ratio 20, loading range 500N-50kN, L 2=95, L 5=200, L 3=240, L 4=95, h=1000 loads Weight gravity W 01=2000N, the heavy W of the counterweight counterweight of balanced lever 2 02=600N, servomotor 1 power 750W, rated speed 2000rpm, counterweight move and at cross beam movement displacement resolution δ=1 μ m.
Key property index: power value error 0.5%~0.05%, the maximum 2.5kN/s of loading speed.

Claims (3)

1. Double-lever type press, comprise frame, load lever system and electric-control system, described loading lever system is positioned at the top of frame, it is characterized in that described frame is frame structure, its underpart is fixedly connected with base plate, and the fulcrum on its upper beam is connected for knife-edge support with loading between lever (1) crossbeam; Described loading lever system below is provided with the balanced lever system, two cover lever system horizontal positioned, and parallel; Load and load lever (1) crossbeam in lever system according to the work of second-class lever principle, its fulcrum is positioned at an end that loads lever (1) crossbeam, and the force is positioned at the middle part that loads lever (1) crossbeam; Balanced lever is worked according to the lever of first order principle, its fulcrum is positioned at the middle part of lever, the force is positioned at an end of lever, the force that loads lever (1) crossbeam connects by reverse frame with the force of balanced lever (2) crossbeam, the fulcrum of two cover levers equates with the distance between the force, fulcrum is positioned on same plumb line, and the loading counterweight that loads lever (1) crossbeam can be along the lever crossbeam shift position, thereby changes the lever ratio size; Balanced lever (2) crossbeam can balance loads lever (1) crossbeam and loads the gravity of counterweight, and the gravity that is produced by a counterweight counterweight that is arranged on the fixed mass of balanced lever (2) crossbeam one end is as the power of lever.
2. Double-lever type press claimed in claim 1, it is characterized in that, load in lever system along the loading counterweight of lever crossbeam shift position and can be divided into body counterweight and link code two parts, body counterweight and link code pass through attachment pegs, holding screw is fastenedly connected, link code connects by line slideway with lever crossbeam, attachment pegs is arranged on the body counterweight, axis is parallel with body counterweight moving direction, holding screw is arranged on link code, be in vertical, line slideway is arranged on lever crossbeam, only need use link code when applying small value force, unclamp holding screw this moment, fix and be locked at lever crossbeam on lock-screw the body counterweight simultaneously, lock-screw is arranged on the body counterweight, be in the vertical direction with body counterweight moving direction.
3. the described Double-lever type press of claim 1 or 2 is characterized in that being calculated as follows the initial position that loads counterweight when determining the lever initial balance:
L 0 = - P 0 L 2 W
P wherein 0That W is the gravity that loads counterweight, L by the active force of the gravity generation of lever crossbeam and loading counterweight 2It is the distance between fulcrum and force;
Be calculated as follows the size of the active force P that sample is applied:
P = P 0 + W L 2 × L
Wherein the initial value of arm of force L is L 0..
CN 201010271316 2010-09-03 2010-09-03 Double-lever type press CN101943544B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN 201010271316 CN101943544B (en) 2010-09-03 2010-09-03 Double-lever type press

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN 201010271316 CN101943544B (en) 2010-09-03 2010-09-03 Double-lever type press

Publications (2)

Publication Number Publication Date
CN101943544A CN101943544A (en) 2011-01-12
CN101943544B true CN101943544B (en) 2013-05-08

Family

ID=43435664

Family Applications (1)

Application Number Title Priority Date Filing Date
CN 201010271316 CN101943544B (en) 2010-09-03 2010-09-03 Double-lever type press

Country Status (1)

Country Link
CN (1) CN101943544B (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102954828B (en) * 2011-08-30 2014-12-24 上海市计量测试技术研究院 Balancing device
CN105021346A (en) * 2015-06-23 2015-11-04 陶泽成 Multi-lever ratio lever mechanism
CN106289636A (en) * 2016-07-21 2017-01-04 南京卓砾智测控技术有限公司 Plasticity pressure measurement equipment high/low temperature Quasi-dynamic calibration device based on compressor mode

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1432276A (en) * 1973-05-07 1976-04-14 Schloemann Siemag Ag Press for producing closed-bottomed articles
CN2599515Y (en) * 2002-12-16 2004-01-14 南京理工大学 Copper column pressure measuring automatic interpretoscope
RO119214B1 (en) * 1997-03-11 2004-05-28 Aurel Filoteanu Mass/force generator, having the capacity of signalling the charging yoke touching
CN201203473Y (en) * 2008-06-03 2009-03-04 山东省计量科学研究院 Dead weight / lever dual-purpose type force standard plane
CN201444098U (en) * 2009-01-11 2010-04-28 天水红山试验机有限公司 Lever-type force standard machine
TW201022645A (en) * 2008-12-04 2010-06-16 Ind Tech Res Inst Three-purpose force standard machine with independent dead-weight stack and lever arm

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4250278B2 (en) * 1999-11-04 2009-04-08 株式会社ミツトヨ Torque calibration device
DE102008022088B4 (en) * 2008-05-05 2010-05-12 Horiba Europe Gmbh Calibration device and calibration method for a test stand

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1432276A (en) * 1973-05-07 1976-04-14 Schloemann Siemag Ag Press for producing closed-bottomed articles
RO119214B1 (en) * 1997-03-11 2004-05-28 Aurel Filoteanu Mass/force generator, having the capacity of signalling the charging yoke touching
CN2599515Y (en) * 2002-12-16 2004-01-14 南京理工大学 Copper column pressure measuring automatic interpretoscope
CN201203473Y (en) * 2008-06-03 2009-03-04 山东省计量科学研究院 Dead weight / lever dual-purpose type force standard plane
TW201022645A (en) * 2008-12-04 2010-06-16 Ind Tech Res Inst Three-purpose force standard machine with independent dead-weight stack and lever arm
CN201444098U (en) * 2009-01-11 2010-04-28 天水红山试验机有限公司 Lever-type force standard machine

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
JP特开2001-133348A 2001.05.18

Also Published As

Publication number Publication date
CN101943544A (en) 2011-01-12

Similar Documents

Publication Publication Date Title
CN103389243B (en) Micro material mechanical performance testing platform under stretching-bending-twisting multi-loads
US8132447B2 (en) Universal testing machine
CN105606047B (en) Axial workpiece automatic checkout equipment
CN201110822Y (en) Self-balance multifunctional structure static loaded experiment loading unit
CN101806592B (en) On-line double-sided automatic thickness measuring device of organic glass
CN202903617U (en) In-situ three-point bending test device
CN100595513C (en) Cylinder diameter and form and position error integrated measuring apparatus
CN105091802B (en) A kind of Portable two-dimensional slave laser measurement apparatus based on laser range sensor
CN101947929B (en) Vehicle weighing device and calibration method thereof
CN101451897B (en) Electromagnetic type small force value standard apparatus
DE60003744T2 (en) Device for stress and strain measurements
CN205002959U (en) Measuring instrument of axial clearance of bearing
CN108362439B (en) A kind of standardized centroid exemplar centroid position two-dimentional measuring device and measurement method
CN106525412B (en) A kind of rotary table component comprehensive performance detection platform and detection method
CN102252804B (en) Multi-functional torque calibration device
CN101261171B (en) Measuring mechanism for measuring object centroid position
KR20090003611A (en) A creep tester equipment for precision load control
CN203396532U (en) Torque wrench calibrator
CN104697780A (en) Gear shifter performance testing device
CN102162768B (en) Device for detecting performance of static pressure air flotation guide rail and using method of device
CN103353429B (en) A kind of Simple test-piece fatigue tester
CN107110751A (en) Equipment for implementing bend test
CN2635482Y (en) Railway vehicle brake regulator performance testing table
CN1212509C (en) Pressure shearing testing machine for detecting rubber product
CN105758360B (en) A kind of steering bearing blowout patche raceway groove parameter measurement instrument and its measurement method

Legal Events

Date Code Title Description
PB01 Publication
C06 Publication
SE01 Entry into force of request for substantive examination
C10 Entry into substantive examination
GR01 Patent grant
C14 Grant of patent or utility model
CF01 Termination of patent right due to non-payment of annual fee

Granted publication date: 20130508

Termination date: 20160903

CF01 Termination of patent right due to non-payment of annual fee