CN101226106A - Method of testing multinomial performance of double mass flywheel torsion vibrating absorber and test stand - Google Patents
Method of testing multinomial performance of double mass flywheel torsion vibrating absorber and test stand Download PDFInfo
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- CN101226106A CN101226106A CNA2008100468586A CN200810046858A CN101226106A CN 101226106 A CN101226106 A CN 101226106A CN A2008100468586 A CNA2008100468586 A CN A2008100468586A CN 200810046858 A CN200810046858 A CN 200810046858A CN 101226106 A CN101226106 A CN 101226106A
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Abstract
The invention relates to a test method of multiple properties of automobile engine double mass flywheel torque insulator and a relative test bed. The method comprises utilizing a torsion movement device, first converting the rotation motion of a variable frequency motor into the torque motion demanded by the double mass flywheel torque insulator dynamic test, using a frequency converter to adjust the rotation speed of the variable frequency motor to realize the frequency needed by the torsion movement, then according to a demanded swing angle, adjusting the eccentricity of a crank wheel of the torsion movement device and the length of an adjustable link bar, to realize the amplitude of swing needed by the dynamic test torsion. The test bed comprises a variable frequency motor (1), a sensor detector, a test sample, a relative connector and a device for converting the rotation motion of the variable frequency motor into the torsion motion demanded by the double mass flywheel torque insulator dynamic test. The invention can process static property test, dynamic property test and durability test of double mass flywheel torque insulator on one test bed.
Description
Technical field
The present invention relates to a kind of motor car engine double mass flywheel torsion vibrating absorber dynamic property test method and a kind of multi-function test stand of realizing the test of double mass flywheel torsion vibrating absorber static properties, dynamic property test and endurancing of being used for.
Background technology
Current automobile develops towards the direction of high pulling torque, high speed, lightweight, high-level efficiency and low resistance, and people have proposed more and more higher requirement to various aspects such as the vibration of automobile, noise, riding comforts.As everyone knows, automobile is a vibrational system with quality, elasticity and damping.Piston engine is to rely on Piston Compression gas, makes fuel oil explosion and produce periodical impulse force and promote the crank throw acting under the High Temperature High Pressure effect, becomes the power source of whole running car.Because of the unbalance inertia force cyclical variation of gaseous-pressure in the cylinder and movement parts, and the result of road injustice can make crankshaft system and engine complete machine produce vibration during running car.Wherein the torsional oscillation of bent axle and kinematic train is important, and closely related with the car load kinematic train.Bent axle is subjected to periodically variable perturbed force effect, and this perturbed force can make engine and kinematic train produce strong torsional oscillation.Because the extra-stress of these devices that torsional oscillation causes substantially exceeds working stress, this can influence the work quality and the life-span of engine and power train, produces noise, causes serious destruction.Therefore, be necessary the twisting vibration of strict control engine crankshaft and the twisting vibration of reduction power train.In the practice in the past, Automobile Design teacher have adopted many effective measures, and one of them is important and torsional vibration damper is adopted in measure widely exactly.
The double mass flywheel torsional vibration damper is a breakthrough invention that solves the automotive transmission Torsional Vibration.It is automobile scientific research and driver and crew the requirement of riding comfort to be developed rapidly with estimating under the background that becomes better and approaching perfection day by day.Double mass flywheel (English Dual Mass Flywheel, abbreviation DMF) is exactly that traditional flywheel mass is divided into two parts, and the one, primary flywheel, it and engine crankshaft are connected, and still belong to the engine inertia square; The 2nd, secondary flywheel, it with variator separate and in conjunction with not finishing with the clutch coupling of vibration damper by one, then it belongs to the drive train inertia square, be used to improve the moment of inertia of variator, between the flywheel mass after two separation by one sleeve spring-damping system, the torsional vibration damper connection that is double mass flywheel is as a whole, and secondary flywheel is contained on the bearing, can be with respect to the active flywheel torsion.Make double mass flywheel have following advantage like this: 1. two parts quality connects by spring-damp system, plays the vibration damping and vibration isolation effect; 2. under the prerequisite of the moment of inertia that does not increase flywheel, improved the moment of inertia of power train, shaken, improved comfortableness thereby fall; 3. resonance speed depends on all moment of inertia of power train, and the big more resonance speed of power train moment of inertia is low more, facts have proved to use double mass flywheel to make resonance speed far below idling; 4. reduced synchronizing quality, made shifting of transmission be more prone to, it is little to wear and tear, and avoids impacting overload protection.
Double mass flywheel is in the emission control of engine; riding comfort and variator and other protection aspect to the parts of vibration sensing all brought into play traditional unrivaled superiority of driven disc type vibration damper; business and consumer's cry is also more and more stronger; as seen its economic benefit of bringing is appreciable, has very big market potential.Double mass flywheel has formed the 600 ten thousand cover scales of annual output per year abroad, adopt new material, new technology, quite ripe in technology, its theory is also very perfect, use very wide, many moneys vehicle such as Audi, masses, benz, BMW, Toyota and Volvo etc. such as Germany, Japan, Britain, the U.S., approximately per four cars just have one to assemble double mass flywheel in Europe, and its range of application also develops into and is used for gasoline car, motor bus, low and middle-grade car by being used for diesel vehicle.But in China, double mass flywheel still belongs to emerging technology, on theoretical and technology, all also be in conceptual phase, have only minority clutch coupling factory and some colleges and universities, institute to study, double mass flywheels such as DMF350, DMF228 as Changchun one Dong Liheqichang and Jilin University's exploitation, the double mass flywheels such as DMF225, DMF390 of Hubei Sanhuan Clutch Co., Ltd.'s exploitation, these only are a small amount of exemplar and product, do not form a perfect theoretical system and standard.Therefore, relevant test and the testing table of exploitation double mass flywheel is imperative.
Torsional vibration damper is in when typing, or bigger change arranged and change at structure, material and technology and must make a service test when factory produces.Double mass flywheel torsion vibrating absorber, also must make a service test after producing trial-production as a emerging torsional vibration damper product.Its main performance test comprises envelope test and dynamic test: envelope test mainly is to draw static twist rigidity according to the quiet moment of torsion of test and corresponding corner, further determines the static torque characteristic; Dynamic test then is to determine dynamic torsional rigidity and ratio of damping and elastic vibration moment allowable according to (frequency and amplitude all change) under the dynamic condition.
The double mass flywheel torsion vibrating absorber performance test stand is the device that the torsional vibration damper to the double mass flywheel in the vehicle transmission parts makes a service test.Domestic is also very limited to the research of motor car engine double mass flywheel torsion vibrating absorber performance test stand.Because double mass flywheel work pivot angle is big, strengthen the also sharply increase of its moment of inertia along with rocking frequency when rocking, because double mass flywheel work pivot angle can be very big, generally can reach ± 40 °～± 65 °, and conventional clutch clutch plate torsional vibration damper pivot angle has only ± 8 °～± 12 °, the rotating speed of automobile is also at 600rpm～4500rpm simultaneously, be that frequency is in 10～75Hz scope, so the testing table that the big pivot angle high-frequency that realizes double mass flywheel is rocked is quite difficult, and the testing table of the torsional vibration damper performance of existing double mass flywheel all is the improvement on driven disc type torsional vibration damper performance test stand.Domestic testing table about torsional vibration damper has following several:
1. exciting box testing table: carry out torsional excitation with mechanical means.By changing the installation angle of every pair of exciting piece in the exciting case, can change the size of excitation moment, excitation frequency (0～80) Hz; Excitation moment (0～6) kNm; Amplitude modulation Rotary Inertia of Flywheel (20.17～58.23) kgm, this device adopt silicon controlled rectifier to control the work of two DC frequency-changing motor, realize stepless speed regulation, and dynamic velocity drop is less than 1%; Vibration frequency and amplitude size are adjustable, are applicable to that external diameter is not more than the dynamic test of the various vibration dampers of 1.0m, can determine the vibration frequency of sample, dynamic torsional rigidity and damping number etc.At double mass flywheel, still there is its deficiency in this testing table: its peak swing can not satisfy the requirement of double mass flywheel;
2. universal shaft type testing table: adopt mechanical means to carry out torsional excitation.By departing from the excitation angle of a setting of universal knot main shaft, cause and in rotary course, produce the torsional oscillation vibration.This device excitation frequency (10～100) Hz; 0 °～2 ° of excitation angle; Under vibration damper coupling shaft rotating speed the same terms, excitation frequency (than exciting box) can improve 1 times; Vibration frequency and amplitude size also are adjustable; Be applicable to that external diameter is not more than the dynamic test of the various vibration dampers of 0.40m, can determine the vibration frequency of sample, dynamic torsional rigidity and ratio of damping etc.At the double mass flywheel torsion vibrating absorber test, its amplitude still can not satisfy the requirement of double mass flywheel;
3. hydraulic actuation type testing table: adopt hydraulic driving mode to encourage, promptly with hydraulic piston pole pair torsional vibration damper not the stiff end start make torsional vibration damper carry out torsional movement, utilize support equipment to carry out data processing.Its excitation frequency (0～400) Hz; Excitation moment (0～1) kN.m; 0 °～± 3 ° of the anglecs of rotation; Load steadily the accuracy height; Make to computerize, and the control mode of four kinds of various combinations is arranged, to satisfy different testing requirementss; Can select different waveforms for use during dynamic test: sine wave or triangular wave; Be applicable to that external diameter is not more than the dynamic rate test of the various elastic suspensions of 0.25m, can determine the vibration frequency of sample, dynamic torsional rigidity and accurate dynamic antivibration coefficient etc.At the double mass flywheel torsion vibrating absorber test, its amplitude still can not satisfy the requirement of double mass flywheel.
Therefore, performance test at double mass flywheel torsion vibrating absorber, need to propose a kind of new test method, especially its dynamic test, the dynamic property that at all can't finish with general torsional vibration damper testing table under the duty of double mass flywheel high-frequency long arc is tested.Need redesign vibrator, make the characteristics of its suitable double mass flywheel, utilize necessary instrument to carry out data processing, important technological parameters is according to the characterisitic parameter (design load) of sample, decide by selected device (vibrator), as long as testing table satisfies the requirement of apparatus preparation rate; The accuracy of test findings depends primarily on the overall uncertainty of necessary instrument, is applicable to the dynamic rate test of various elastic suspensions, just can determine the vibration frequency of sample, dynamically torsional rigidity and accurate dynamic antivibration coefficient etc.
The endurancing of torsional vibration damper is that torsional vibration damper is damaged at the number of times or the test specimen of certain load mode down to regulation.For the endurancing of double mass flywheel torsion vibrating absorber, the present domestic correlation test standard that also do not have.Therefore it is being carried out in the endurancing process, can be with reference to the test standard of clutch plate torsional vibration damper endurance torsion test, adjust accordingly in conjunction with the characteristic of double mass flywheel itself and to carry out.According to two conditions of clutch plate torsional vibration damper endurance torsion test as can be known, the dual mode that is loaded with to the clutch plate torsional vibration damper: 0～1.2Memax during 1. unidirectional loading, or forward 1.0Memax, oppositely 0.5Memax (Memax is a maximum engine torque) during two-way loading.2. the windup-degree by above-mentioned load correspondence loads; Next is a torsion frequency: 6Hz～25Hz.Because technical to the domestic blockage that is at double mass flywheel abroad, its experimental technique is not also to domestic open.At home, double mass flywheel itself is an emerging product, and its testing equipment also is a focus of research, but still neither one test standard and a perfect testing equipment.Therefore, invention and the research of carrying out the double mass flywheel testing table under such background is highly significant.
Summary of the invention
Technical matters to be solved by this invention is: the test method that a kind of multinomial performance at double mass flywheel torsion vibrating absorber is provided, and can realize comprising that dynamic test performance test, static properties are tested and the testing table of the multinomial performance of endurancing, be implemented in the test of on the same testing table torsional vibration damper of double mass flywheel being carried out described multinomial performance, thereby provide reliable test data for the performance of motor car engine double mass flywheel torsion vibrating absorber.
The technical scheme that the present invention solves its technical matters employing is: use the torsional movement device, earlier change rotatablely moving of adjustable frequency motor into double mass flywheel torsion vibrating absorber dynamic test required torsional movement, regulate the required frequency of rotational speed realization torsional movement of adjustable frequency motor again by frequency converter, then according to the pivot angle that will realize in advance, the eccentric throw that is installed in crankwheel top shoe axle in the adjusting torsional movement device and the length of adjustable connecting-rod, the realization dynamic test is rocked the required amplitude of oscillation.
The present invention compared with prior art has following major advantage:
One. do not need that testing table is done too many adjustment and can on same testing table, carry out the static properties test of double mass flywheel torsion vibrating absorber, dynamic property test and endurancing;
They are two years old. realize the required torsional movement of double mass flywheel torsion vibrating absorber performance test with the torsional movement device.In this device, the pivot angle of fork is symmetry substantially, be contained in the eccentric throw of crankwheel top shoe axle and length pivot angle when certain limit changes of adjustable connecting-rod and still keep symmetry substantially, thereby dynamic property test of realization double mass flywheel and endurancing symmetry is rocked;
They are three years old. by the stepless speed regulation of adjustable frequency motor, realize the adjusting of torsional movement frequency easily; Be installed in the eccentric throw of crankwheel top shoe axle and the length of adjustable connecting-rod by adjusting, realize adjusting, thereby provide dynamic condition for dynamic test the torsional movement amplitude of oscillation;
They are four years old. take the pre-loaded angle of angle pre-load means, the torsional movement of basic symmetry is added on the angle in advance at this to carry out, add angle in advance by regulating difference, can cover the whole operating angle scope of double mass flywheel torsion vibrating absorber, be implemented in little and the high-frequency dynamic property test in the scope that absolute operating angle is big of relative pivot angle, avoided double mass flywheel because the problem of big moment of inertia during the big pivot angle of high-frequency.
Description of drawings
Fig. 1 is a double mass flywheel torsion vibrating absorber multi-function test stand physical construction wiring layout.
Fig. 2 is the partial right side view of torsional movement device among Fig. 1.
Fig. 3 is the schematic diagram of torsional movement device.
Fig. 4 is the structural representation of slide block axle 37.
Fig. 5 is the left view of Fig. 4.
Fig. 6 is the structural representation of arbitrarily angled joint flange 23.
Among the figure: 1. adjustable frequency motor; 2. big flexibility shaft coupling; 3. crank axle; 4. bearing; 5. crankwheel backstay; 6. crankwheel is located the rod guidance road; 7. crankwheel; 8. angular displacement sensor; 9. fork axle regulating center bearing base; 10. fork axle; 11. rod guidance road, fork location; 12. fork backstay; 13. fork shaft stool; 14. primary flywheel joint flange; 15. double mass flywheel torsion vibrating absorber; 16. secondary flywheel joint flange; 17. bearing seat; 18. torque sensor; 19. coupling band; 20. bearing; 21. large straight gear; 22. transmission shaft; 23. arbitrarily angled joint flange; 24. bearing; 25. worm reduction gear; 26. shaft coupling; 27. worm gear output shaft; 28. small Spur gear; 29. bearing spider; 30. base plate; 31. support; 32. handle; 33. fork; 34. first connecting rod; 35. nut; 36. length of connecting rod adjustable pipe; 37. slide block axle; 38. round nut; 39. second connecting rod; 40. locating sleeve; 41. rivet; 42. positioning screw mandrel; 43. counterbalance weight; 44. cylinder roller bearing; 45. cylinder roller bearing; 46. fork bearing pin.
Embodiment
The test method of multinomial performance of double mass flywheel torsion vibrating absorber provided by the invention, promptly adopt the torsional movement device, earlier change rotatablely moving of adjustable frequency motor into double mass flywheel torsion vibrating absorber dynamic test required torsional movement, regulate the required frequency of rotational speed realization torsional movement of adjustable frequency motor again by frequency converter, then according to the pivot angle that will realize in advance, the eccentric throw that is installed in crankwheel top shoe axle in the adjusting torsional movement device and the length of adjustable connecting-rod, the realization dynamic test is rocked the required amplitude of oscillation.Specifically be to adopt the method that may further comprise the steps:
(1) realization of basic symmetrical torsional movement:
Adopt a torsional movement device that contains fork that links to each other with two quality primary flywheels and the crankwheel that links to each other with adjustable frequency motor, change rotatablely moving of adjustable frequency motor into double mass flywheel torsion vibrating absorber dynamic test required torsional movement, and special relationship is satisfied in the position of the crankwheel of torsional movement device, connecting rod and fork, be installed in the eccentric throw of crankwheel top shoe axle and the length of adjustable connecting-rod simultaneously and meet the demands when changing, the pivot angle of its fork keeps symmetry substantially.
(2) rock the realization of frequency adjustment: adopt adjustable frequency motor to drag the torsional movement device, regulate the adjustable frequency motor rotational speed, thereby realize the adjusting of torsional movement frequency by frequency converter.
(3) rock the realization that the amplitude of oscillation is regulated: adopt the eccentric throw and all variable torsional movement device of length of connecting rod that are installed in crankwheel top shoe axle, before test according to wanting the pivot angle realized, adjusting is installed in the eccentric throw and the extremely corresponding length of connecting rod of crankwheel top shoe axle, and the realization dynamic test is rocked the adjusting of the amplitude of oscillation.
(4) add the angle realization of loading in advance: because double mass flywheel work pivot angle big (can reach ± 40 °～± 65 °), it realizes that under high-frequency big torsional movement can produce very big moment of inertia, if directly realize that with torsional movement so big pivot angle is very difficult, its intensity and security are not easy to guarantee, and the duty of so big pivot angle just just occurs under special operation conditions such as engine start and braking usually, therefore take a pre-loaded angle, the torsional movement of basic symmetry is added on the angle in advance at this to carry out, add angle in advance by regulating difference, can cover the whole operating angle scope of double mass flywheel torsion vibrating absorber.Therefore, here adopt a gear on the worm reduction gear projecting shaft and a gearing mesh on the axle of double mass flywheel secondary flywheel place, hand rotation worm gear reducer cleaner handgrip, make the double mass flywheel secondary flywheel turn over one and add angle in advance, because the double mass flywheel primary flywheel links to each other with the torsional movement device, therefore it moves back the extreme position that forwards fork to and has just no longer rotated, again because the self-locking action of worm reduction gear, release handle, the secondary flywheel of double mass flywheel also can not move back and goes back to owing to unclamping of handle will add angle in advance, loads thereby realize adding in advance angle.For the sake of assurance, in double mass flywheel secondary flywheel output shaft tip designs can realize the connection joint of arbitrarily angled connection, guarantee secondary flywheel fixing in dynamic test.
The present invention carries out the test of double mass flywheel torsion vibrating absorber dynamic property by above-mentioned steps.
The invention provides a kind of testing table that can realize the test method of above-mentioned multinomial performance of double mass flywheel torsion vibrating absorber, its structure is: comprise adjustable frequency motor 1, sensing detection device, test specimen and link thereof, also comprise the device that rotatablely moving of adjustable frequency motor is changed into the required torsional movement of double mass flywheel torsion vibrating absorber dynamic test.The device of torsional movement is mainly by the crankwheel 7, the fork 33 that links to each other with the primary flywheel of double mass flywheel that drive with adjustable frequency motor, form the crankwheel assembly with the adjustable connecting-rod that fork 33 links to each other, wherein, the pivot angle of fork 33 is symmetry substantially, and adjusting is installed in the eccentric throw of crankwheel top shoe axle and length this pivot angle when certain limit changes of adjustable connecting-rod still keeps symmetry substantially.
The invention will be further described below in conjunction with specific embodiment and accompanying drawing, but do not limit the present invention.
The invention provides a multi-function test stand that can carry out envelope test, dynamic test and the endurancing of double mass flywheel torsion vibrating absorber, its structure such as Fig. 1 show: comprise rotary driving part, torsional movement device, test specimen and link thereof, angle pre-load means and pick-up unit and miscellaneous part, these parts all are arranged on the support 31, describe in detail respectively below:
Dynamic test is owing to designed the angle pre-load means, and it rocks promptly and carries out on certain angle, therefore can realize that relative pivot angle is little, and the absolute very big high frequency dynamic test of operating angle; Endurancing at double mass flywheel torsion vibrating absorber, still the torsional movement that needs big pivot angle, because double mass flywheel has very big moment of inertia under high frequency and the big situation of work pivot angle, require (6～25Hz rocks frequency) according to the endurancing of GB clutch plate torsional vibration damper, get to hang down and rock frequency 6～8Hz, carry out endurancing according to forward and reverse symmetrical load mode and get final product.The static properties test needs to load slowly, and power changes under the little situation and carries out pivot angle and torsion-testing.
(1) described rotary driving part is an adjustable frequency motor 1, and it provides rotary power, links to each other with crank axle 3 by big flexibility shaft coupling 2, and crank axle 3 is by bearing 4 supportings.
(2) described torsional movement device is made up of crankwheel parts, adjustable connecting-rod and fork, as Fig. 2, shown in Figure 3.
The crankwheel parts are made up of crankwheel 7, the slide block axle 37 that embeds T shape slideway on the crankwheel, counterbalance weight 43 and positioning screw mandrel 42.The structure of slide block axle 37 as shown in Figure 4, its rectangular end embeds in the T shape slideway of crankwheel 7, by rotation positioning screw mandrel 42, slide block axle 37 is moved in slideway, and the adjusting of eccentric throw is realized to the distance in crankwheel axle center in adjusting slider axle axle center, by tightening round nut 38, it is acted on the locating sleeve 40 by cylinder roller bearing 44 inner rings, and locating sleeve 4 is clamped on T shape slideway with the slide block axle, guarantees that the eccentric throw that is installed in crankwheel top shoe axle in process of the test immobilizes.Counterbalance weight 43 links to each other with crankwheel 7 by rivet 41, and counterbalance weight is that balanced crank is taken turns in 7 rotary courses because the part centrifugal force that the off-centre of slide block axle is brought.Adjustable connecting-rod is made up of first connecting rod 34, second connecting rod 39 and length of connecting rod adjustable pipe 36, wherein: an end of first connecting rod 34 and second connecting rod 39 links to each other with the two ends screw thread of length of connecting rod adjustable pipe 36 respectively and with nut 35 lockings, the other end interlocks by cylinder roller bearing 44,45 and slide block axle 37, fork bearing pin 46 respectively; One end of fork 33 links to each other with fork bearing pin 46, and the other end links to each other with fork axle 10 by spline.
Has following position relation between each bar of this torsional movement device: when fork 33 and crankwheel 7 axle center are parallel with slide block axle 37 axial connecting lines, fork bearing pin 46 axle center are vertical with fork 33 with crankwheel 7 axle center lines of centres, such torsional movement device has that strain is big or reduce mutually with the eccentric throw of slide block axle and its swinging angle of swinging rod of adjustable connecting-rod length variations, and pivot angle remains the characteristics of basic symmetry, when therefore needing to regulate the swinging angle of swinging rod amplitude, only need according to pivot angle and above-mentioned position relation, regulate the eccentric throw and length of connecting rod to the corresponding length that are installed in crankwheel top shoe axle simultaneously and get final product.
This torsional movement device turns round when carrying out dynamic property test and endurancing, the static properties test is not turned round, since the dynamic property test design angle pre-load means, can be implemented in to add in advance and carry out the little pivot angle of high-frequency on the angle and rock and finish test, therefore slide block axle and the crank axle distance of shaft centers of being regulated gets final product from less, and in endurancing, still the torsional movement that needs big pivot angle, so this need be got final product greatly apart from transferring, any parts that realization need not be changed on the testing table can be realized a plurality of tests on a testing table.
(3) test specimen and link thereof: test specimen is a double mass flywheel torsion vibrating absorber 15, the major and minor flywheel of it and double mass flywheel is an indivisible integral body, its link structure is: the primary flywheel end connects by bolt with the primary flywheel joint flange 14 of the identical size of engine crankshaft boss by one, and the other end of this flange links to each other by two flat keys with fork axle 10.The secondary flywheel end is removed clutch coupling, and is connected by bolt with secondary flywheel joint flange 16, and the other end of this flange links to each other by flat key with angle prestrain parts.Wherein for guaranteeing the support stiffness of fork axle 10, being provided with fork axle regulating center bearing base 9 and fork shaft stool 13 is supported, for the coupling stiffness of guaranteeing double mass flywheel torsion vibrating absorber 15 and the axle that reduces to be attached thereto are the influence of weight etc., its secondary flywheel joint flange 16 is also with bearing seat 17 supportings.
As the link of test specimen, they all need to play a role in each test.For primary flywheel joint flange 14, it all serves the same role in each test, is about to test specimen double mass flywheel torsion vibrating absorber and torsional movement device and couples together.For secondary flywheel joint flange 16, its effect in each test all is to connect test specimen double mass flywheel torsion vibrating absorber and angle pre-load means.
(4) angle pre-load means: form by base plate 30, worm reduction gear 25, bearing spider 29, transmission shaft 22, large straight gear 21, small Spur gear 28 and any angle joint flange 23 etc.Worm reduction gear 25 is installed on the base plate 30, its worm screw input shaft end is installed handle 32, can apply turning moment for staff, and a small Spur gear 28 is installed on the worm gear output shaft 27, worm gear output shaft 27 is parallel with transmission shaft 22, and worm gear output shaft 27 links to each other with worm reduction gear 25 by shaft coupling 26.Transmission shaft 22 is supported by the bearing 20 and the bearing 24 that are installed on the base plate 30, the large straight gear 21 of an identical modulus also is installed on transmission shaft, large and small spur gear is meshed and transmits prestrain moment, transmission shaft 22 1 ends and secondary flywheel joint flange 16 link to each other by flat key, and the other end links to each other with any angle joint flange 23.Angle joint flange 23 structures as shown in Figure 5 arbitrarily, it is 120 ° uniform arcuate socket that the coupling bolt hole that is about to common half a coupler changes three central angles into, and to offer three same central angles on the bearing 24 of afterbody be 120 ° uniform arcuate socket, so any angle joint flange 23 can be realized that transmission shaft 22 rotates and arbitrarily angledly all can be connected by bolt with the bearing 24 of afterbody, in dynamic test, realize that with the bolt connection secondary flywheel is adding fixing under the angle arbitrarily in advance in the dynamic test process, in the envelope test process, do not need to connect with bolt, but crankwheel and fork are fixed, directly utilize prestrain to obtain moment of torsion on angle and the transmission shaft, each bearing in the angle pre-load means and worm reduction gear 25 all are installed on the base plate 30 so that whole parts are done as a wholely, are convenient to installation and adjustment before the test of different model double mass flywheel torsion vibrating absorber.Adopting worm reduction gear as the angle pre-load means, is because the speed ratio of worm reduction gear is very big, is convenient to realize manual loading, and secondly worm couple has good self-locking performance, can be because of staff application of force rollback not in the prestrain process.
The angle pre-load means has different functions in different tests: as the angle pre-load means, guarantee that dynamic test covers each operating angle scope of double mass flywheel torsion vibrating absorber when dynamic test; When envelope test, be used for applying locked rotor torque to double mass flywheel, guarantee the mild increase of moment in the envelope test process; Generally do not need angle prestrain when endurancing, i.e. prestrain angle is 0, carries out endurancing after certain prestrain angle also can be set.
(5) sensing detection parts: mainly form by angular displacement sensor 8 and torque sensor 18.According to this bench run principle and structure, double mass flywheel torsion vibrating absorber 15 suffered moments of torsion are secondary flywheel end moment of torsion, that is the moment of torsion on the transmission shaft 22, therefore at transmission shaft 22 and secondary flywheel joint flange 16 junctions torque sensor 18 is set, to guarantee directly obtaining in dynamic or static properties process of the test to the torsional vibration damper moment of torsion.Angular displacement sensor 8 has different functions in different tests, and its installation site is also adjusted to some extent: in the dynamic property test, angular displacement sensor 8 is installed in fork axle 10 ends, and use bolt with secondary flywheel by any angle joint flange 23 this moment, to obtain the pivot angle of fork 33; In envelope test, angular displacement sensor 8 is installed in transmission shaft 22 ends, this moment with crankwheel 7 and fork 33 fixing and arbitrarily angle joint flange 23 do not reinstall bolt, obtaining the angle that transmission shaft 22 turns over, that is the angle that turns over of the relative primary flywheel of secondary flywheel; In endurancing, angular displacement sensor 8 still is arranged on fork axle 10 ends, and connected mode is identical with dynamic test everywhere, and just its effect is to be used for counting, rocks number of times according to the positive and negative conduct of rocking angle and carries out endurancing.Torque sensor 18 interlocks with coupling band 19.
(6) other parts: mainly be some setting elements in different tests, promptly on the bearing 4 of crank axle and fork shaft stool 13, be provided with crankwheel backstay 5 and fork backstay 12 and the crankwheel rod guidance road 6, location and the rod guidance road, fork location 11 of same structure respectively.On crankwheel 7 and fork bearing pin 46 ends all offer the hole, this hole lead with described two and backstay between adopt precision-fit, and guarantee that following position concerns: promptly crankwheel 7 axle center are parallel with fork with slide block axle 37 axle center lines of centres.Like this, before dynamic property test and endurancing, the backstay at two places need be inserted the hole that cooperates with it on crankwheel and the fork bearing pin respectively, being convenient to regulate the eccentric throw that is installed in crankwheel top shoe axle and the length of adjustable connecting-rod rocks with the basic symmetry of guaranteeing testing requirements, after the eccentric throw that is installed in crankwheel top shoe axle and adjustable connecting-rod length adjustment are finished, backstay need be extracted, and couple together with the bearing of bolt after finishing adding angle in advance any angle joint flange and afterbody, in the envelope test process, then do not need backstay is extracted, so that crankwheel and fork axle are fixed, and the coupling bolt of the bearing of any angle joint flange and afterbody removed, thereby the double mass flywheel primary flywheel is fixed, by the angle pre-load means secondary flywheel is loaded, the corner and the moment of torsion that obtain secondary flywheel get final product.
The course of work of testing table of the present invention is owing to different tests, and its process is slightly variant, and each experiment work process is as follows:
(1) dynamic property test: 1. before carrying out the dynamic property test, adjusting is installed in the eccentric throw of crankwheel top shoe axle, adjustable connecting-rod length: at first crankwheel backstay 5 and fork backstay 12 are inserted respectively in the hole corresponding on crankwheel 7 and the fork bearing pin 46, with guarantee crank axle and slide block axle the two the axle center line of centres and the parallel relation of fork, the position of rocking angle and each rod member of torsional movement device according to the test needs concerns then, calculate the corresponding eccentric throw and the length of connecting rod that are installed in crankwheel top shoe axle that rocks under the angle, and adjusting slider axle 37 to the distance of shaft centers of crank axle 3 from length of connecting rod to the length that calculates, finish the required eccentric throw that is installed in crankwheel top shoe axle of torsional movement, the adjusting of adjustable connecting-rod length, must extract the crankwheel backstay 5 and the fork backstay 12 at two places this moment.2. test is preceding according to testing requirements, be provided with and add angle in advance: by the angle pre-load means, turning handle 32, make transmission shaft turn to predetermined angle (this angle with rock angle and less than the maximal work angle of double mass flywheel), owing to be the torsional movement device, the fork axle can not rotate again after angle pre-load means promotion fork moved to extreme position, guaranteed proceeding of angle prestrain, again because the self-locking action of worm reduction gear, it can be owing to the staff application of force and will load angle and move back and go back to not, thereby realize that double mass flywheel can carry out torsional movement on this angle, after this angle setting is finished, fix for guaranteeing the double mass flywheel secondary flywheel, make primary flywheel add torsional movement on the angle in advance at this, except by the self-locking action of worm reduction gear, also in transmission shaft 22 tip designs can realize arbitrarily angled joint flange 23, after angle is loaded into needed value, arbitrarily angled joint flange 23 is connected with bearing 24 with bolt.3. dynamic test process: after preceding two steps are finished, energized, drive crank axle 3 rotations by adjustable frequency motor 1 by big flexibility shaft coupling 2, by the torsional movement device this is rotatablely moved and to be converted to the torsional movement of basic symmetry, thereby for dynamic test provides basic exercise, the fork axle 10 of this device is that the primary flywheel of double mass flywheel torsion vibrating absorber 15 links to each other by primary flywheel joint flange 14 and test specimen, the test specimen secondary flywheel links to each other with the angle pre-load means by secondary flywheel joint flange 16, thereby realization torsional movement device is connected with the test specimen double mass flywheel, because the transmission shaft 22 of angle pre-load means is fixing by any angle joint flange 23, that is the secondary flywheel of double mass flywheel torsion vibrating absorber 15 is fixed, thereby realize that this torsional movement carries out torsional movement adding in advance under the angle, and this motion acted on the test specimen double mass flywheel torsion vibrating absorber 15, finish the required mechanical motion of dynamic property test.Angular displacement sensor 8 by fork axle 10 front ends obtains the angle of rocking of any time, and finishes the collection of any time moment of torsion by the torque sensor 18 of 22 of secondary flywheel joint flange 16 and transmission shafts.
(2) static properties test: 1. crankwheel 7, fork 33 is fixing: crankwheel backstay 5 and fork backstay 12 are inserted respectively in the hole corresponding on crankwheel 7 and the fork bearing pin 46, fork 33 and fork axle 10 is fixing, also the primary flywheel that is about to double mass flywheel is fixed, should make the bolt on any angle joint flange 23 remove this moment, and this flange only plays transmission shaft 22 is bearing in effect on the bearing 24.2. laying of angular displacement sensor: the end that angular displacement sensor is installed in transmission shaft 22 is bearing 24 outer ends, to obtain the angle that the relative primary flywheel of secondary flywheel turns in the static properties process of the test.3. slow turning handle 32 is carried in this moment on the secondary flywheel of double mass flywheel lentamente by worm reduction gear and gear drive effect, and secondary flywheel is rotated relative to primary flywheel lentamente, the mechanical motion of test static properties test.The torque sensor 18 that angular displacement sensor 8 by the transmission shaft end and secondary flywheel joint flange 16 and transmission shaft are 22 is finished any time corner and the collection of moment of torsion.
(3) endurancing: its process of the test is identical with three steps in the test of aforementioned dynamic property, just before test, it is big that eccentric throw that is installed in crankwheel top shoe axle of regulating and length of connecting rod are wanted, make it rock the working limit angle that angle approaches double mass flywheel, and this moment, the angle pre-load means should not reload, this is by the decision of endurancing and double mass flywheel work characteristics, and two place's backstays need be extracted equally and with any angle joint flange bolt.No longer need the torque sensor image data this moment, and the number of times that the data of angular displacement sensor collection are also just rocked according to the positive negative judgement of angle gets final product.
Claims (10)
1. the test method of a multinomial performance of double mass flywheel torsion vibrating absorber, it is characterized in that adopting the torsional movement device, earlier change rotatablely moving of adjustable frequency motor into double mass flywheel torsion vibrating absorber dynamic test required torsional movement, regulate the required frequency of rotational speed realization torsional movement of adjustable frequency motor again by frequency converter, then according to the pivot angle that will realize in advance, the eccentric throw that is installed in crankwheel top shoe axle in the adjusting torsional movement device and the length of adjustable connecting-rod, the realization dynamic test is rocked the required amplitude of oscillation.
2. test method according to claim 1 is characterized in that adopting the method for following steps:
(1) realization of basic symmetrical torsional movement:
Adopt a torsional movement device that contains fork that links to each other with two quality primary flywheels and the crankwheel that links to each other with adjustable frequency motor, change rotatablely moving of adjustable frequency motor into double mass flywheel torsion vibrating absorber dynamic test required torsional movement, and when adjusting was installed in the length of the eccentric throw of crankwheel top shoe axle and adjustable connecting-rod, the pivot angle of its fork kept symmetry substantially;
(2) rock the realization of frequency adjustment:
Adopt adjustable frequency motor to drag the torsional movement device, by the rotational speed of frequency converter adjusting adjustable frequency motor, thus the adjusting of realization torsional movement frequency;
(3) rock the realization that the amplitude of oscillation is regulated:
According to the pivot angle of wanting to realize, adjusting is installed in the eccentric throw of crankwheel top shoe axle and the extremely corresponding length of length of adjustable connecting-rod before testing, and the realization dynamic test is rocked the adjusting of the amplitude of oscillation.
3. test method according to claim 1 and 2, it is characterized in that also adopting the angle pre-load means, a pre-loaded angle, the torsional movement of double mass flywheel is added on the angle in advance at this to carry out, thereby realize following three performance tests: add angle in advance by regulating difference, can cover the whole operating angle scope of double mass flywheel torsion vibrating absorber, be implemented in the high-frequency dynamic property test in the relative pivot angle scope that not quite and definitely operating angle is big; Realize comprising the static properties test of pivot angle and torsion-testing by slow loading; Realize the endurancing of double mass flywheel torsion vibrating absorber by regulating the torsional movement of realizing low frequency and big pivot angle.
4. the testing table of a multinomial performance of double mass flywheel torsion vibrating absorber, comprise adjustable frequency motor (1), sensing detection device, test specimen and link thereof, it is characterized in that also comprising the device that rotatablely moving of adjustable frequency motor is changed into the required torsional movement of double mass flywheel torsion vibrating absorber dynamic test, this device is mainly by the crankwheel (7) that drives with adjustable frequency motor, the fork (33) that links to each other with the primary flywheel of double mass flywheel, the adjustable connecting-rod that the crankwheel assembly links to each other with fork (33) is formed, wherein: the pivot angle of fork (33) is symmetry substantially, and adjusting is installed in the eccentric throw of crankwheel top shoe axle and length this pivot angle when certain limit changes of adjustable connecting-rod still keeps symmetry substantially.
5. testing table according to claim 4, it is characterized in that also comprising the angle pre-load means, this device mainly is made up of worm reduction gear (25), large straight gear (21), transmission shaft (22), small Spur gear (28) and any angle joint flange (23), wherein: worm reduction gear (25), its worm screw input shaft end is equipped with handle (32), and worm gear output shaft (27) is parallel with transmission shaft (22) and a small Spur gear (28) is housed; Transmission shaft (22) is by two seat supports, this transmission shaft is equipped with a large straight gear (21) that is meshed with small Spur gear (28), and an end of this transmission shaft links to each other by flat key with the secondary flywheel joint flange (16) of double mass flywheel, and the other end links to each other with any angle joint flange (23); Arbitrarily angle joint flange (23) is supported by bearing (24), and they all are provided with equally distributed three central angles is 120 ° arc connecting hole.
6. testing table according to claim 4, it is characterized in that described crankwheel assembly, form by slide block axle (37), the positioning screw mandrel (42) that links to each other with slide block axle (37) and the counterbalance weight (43) that links to each other with positioning screw mandrel (42), wherein: slide block axle (37) embeds in the T shape slideway of crankwheel (7), by rotary slider axle positioning screw mandrel 42, slide block axle 37 is moved in slideway, realization is installed in the adjusting of the eccentric throw of crankwheel top shoe axle, and promptly slide block axle (37) axle center is to the adjusting of the distance in crankwheel (7) axle center; By tightening round nut (38), slide block axle (37) is acted on the locating sleeve (40) by cylinder roller bearing (44) inner ring, locating sleeve (40) is clamped on T shape slideway with slide block axle (37), guarantees that the eccentric throw that is installed in crankwheel top shoe axle in process of the test immobilizes.
7. testing table according to claim 6, it is characterized in that described adjustable connecting-rod, form by first connecting rod (34), second connecting rod (39) and length of connecting rod adjustable pipe (36), wherein: an end of first connecting rod (34) and second connecting rod (39) links to each other with the two ends screw thread of length of connecting rod adjustable pipe (36) respectively and with nut lock, the other end respectively interlocks with slide block axle (37), fork bearing pin (46) respectively by cylinder roller bearing; One end of fork (33) links to each other with fork bearing pin (46), and the other end links to each other with fork axle (10) by spline.
8. testing table according to claim 4, it is characterized in that described sensing detection device, mainly by angular displacement sensor (8), and the torque sensor (18) that is arranged on the junction of transmission shaft (22) and secondary flywheel joint flange (16) is formed, wherein: in dynamic property and endurancing, angular displacement sensor (8) is contained on the fork axle (10), and use bolt with secondary flywheel by any angle joint flange (23) this moment, to obtain the pivot angle of fork (33); In envelope test, angular displacement sensor (8) is contained in the end of transmission shaft (22), this moment is with crankwheel (7) and fork (33) are fixing and any angle joint flange (23) does not reinstall bolt, obtaining the angle that transmission shaft (22) turns over, that is the angle that turns over of the relative primary flywheel of secondary flywheel.
9. testing table according to claim 4, it is characterized in that described test specimen and link thereof, test specimen is double mass flywheel torsion vibrating absorber (15), the major and minor flywheel of it and double mass flywheel is an indivisible integral body, the structure of its link is: the primary flywheel end is connected with primary flywheel joint flange (14) by bolt, and this flange other end links to each other by two flat keys with fork axle (10); The secondary flywheel end is removed clutch coupling, and is connected by bolt with an end of secondary flywheel joint flange (16), and the other end of this flange links to each other by flat key with transmission shaft (22); Fork axle (10) is by fork axle bearing seat (9) and fork shaft stool (13) supporting, and secondary flywheel joint flange (16) supports with bearing seat (17).
10. testing table according to claim 4 is characterized in that the output shaft of adjustable frequency motor (1) links to each other with the crank axle (3) of crankwheel (7) by big flexibility shaft coupling (2), and crank axle (3) is supported by crank axle bearing (4).
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