CN101158622A - Vehicle electric power-assisted steering system tester - Google Patents
Vehicle electric power-assisted steering system tester Download PDFInfo
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- CN101158622A CN101158622A CNA2007101900750A CN200710190075A CN101158622A CN 101158622 A CN101158622 A CN 101158622A CN A2007101900750 A CNA2007101900750 A CN A2007101900750A CN 200710190075 A CN200710190075 A CN 200710190075A CN 101158622 A CN101158622 A CN 101158622A
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Abstract
The invention belongs to the testing equipment technical field of car engineering, more particularly, relating to a testing device that does such related research on the assisted-power characteristic and the control policy of EPS, etc., and tests the power-assisted steering effect as well as the safety of vehicle electric power steering system by simulating the vehicle running under practical conditions. The device includes an integrated system of a steering front wheel and a suspension, a mechanical steering system, an installation bench of the mechanical steering structure, an AC motor controller, a current sensor, a torque sensor, a vehicle speed sensor, a data collecting system and a digital electrohydraulic servo testing system. The device is characterized by the setting of a wheel power input mechanism, a steering reversal simulation mechanism and an evenly loading mechanism. The invention can perform relatively exact simulation of the strained condition of the vehicle steering system in a laboratory and can reflect the influence of such factors as the vehicle load, the pavement behavior, the wheel alignment parameters, the suspension system, the tyre characteristic and the vehicle speed, etc., on the stress of the steering system.
Description
Technical field
The invention belongs to Vehicle Engineering testing apparatus technical field, be specifically related under a kind of simulating vehicle operation actual condition, EPS carried out correlative study such as assist characteristic and control strategy and detect the test unit of vehicle electric boosting steering system power steering effect and security.
Background technology
Electric boosting steering system (EPS:Electric Power Steering System) is different from traditional hydraulic power-assist steering system (HPS:Hydraulic Power Steering System) and electric-controlled hydraulic servo steering system, it does not need complicated mechanical and hydrostatic control, have energy-saving and environmental protection and improve plurality of advantages such as automobile operation performance, receive many scholars' concern, become the focus of Hyundai Motor steering research and development.Its system principle diagram as shown in Figure 1.
Driver's steering wheel rotation 1, turn to input shaft 2 to drive steering wheel torque sensor 3, torque sensor is converted into the controller 9 that electric signal is passed to the EPS system to the torque signal of measuring, controller 9 according to vehicle speed signal 12 ', steering wheel torque signal 13 ', calculate the desirable power-assisted electric current 16 of motor according to the assist characteristic opisometer, under the driving of ECU9, assisted electric machine 8 provides suitable booster torquemoment.Simultaneously, ECU disconnects according to 14 pairs of electromagnetic clutchs 10 of engine rotational speed signal and combination control.When electromagnetic clutch 10 was in bonding state, the booster torquemoment of motor turned on the output shaft 15 and driver's steering moment is finished steering operation together slowing down under the effect of speed reduction unit 4 to increase to turn round to be loaded into.
In EPS design and development process, need several below aspects to study: in (just under the Vehicular turn moment actual change rule situation) under the vehicle actual operating state, according to some parameters of vehicle determine the different control strategies of assist characteristic curve, comparison the control effect, the steering parameter is carried out matching Design etc., these researchs all need to verify at last.Therefore, the design bench test is very necessary.
But existing test unit is difficult to the Changing Pattern of steering reversal moment, the steering moment of resistance under the accurate simulating vehicle actual travel state.Partly be installed in steering gear drag link two ends in gantry designs in " automobile engineering " 2004 (Vol.26) No.5 " the bench test research of the electric boosting steering system control " literary composition with two double helix springs, in case steering wheel rotation, one side spring is compressed, and turns to load to change along with the variation of steering wheel angle.Electric power steering test device described in the literary composition, the rotational resistance torque of bearing circle and aligning torque are simulated roughly by the spring force that the volute spring compression and tension that is installed in steering gear drag link two ends is produced, as shown in Figure 2.Behind steering wheel rotation 1, tooth bar 6 tangential movement under the synergy of driver's steering moment and motor power-assisted square, make spring 17 distortion, thereby apply a reacting force, with the main moment of resistance and the aligning torque in the simulating vehicle steering procedure to steering.Its shortcoming is apparent, and in the vehicle traveling process, the booster torquemoment that travel speed, pavement behavior, load, front alignment angular dimensions and suspension parameter etc. should apply bearing circle and the size of aligning torque all have very important influence.The test unit of mentioning in the literary composition is not all considered these factors, just has no way of investigating these factors to the influence of EPS power-assisted effect and the mechanism of research EPS unstability.
In the national inventing patent 200410013398.9 mode of spring loading force is improved, proposed to come the simulated automotive wheel to turning to the resistance of output shaft by resistance servo motor.As shown in Figure 3, replaced spring 17 by resistance servomotor 18.When carrying out the correlation test of EPS system, control system is controlled the size of servomotor exciting current, thereby changes the size of whole steering steering drag.This device has been simulated steering drag, the aligning torque size of vehicle actual travel process to a certain extent.But, model over-simplification: ignore of the influence of ground tangential force to tire cornering characteristics; Ignore load change to the influence of tire cornering characteristics and the influence of tyre moment; Ignore the effect of suspension.
These simplification make test unit can't reflect the Changing Pattern of the moment of resistance and aligning torque when turning to, nor can response speed, load, road condition change and tire characteristics change the influence to the EPS system performance.
Summary of the invention
Technical matters to be solved by this invention provides the electric power steering test device that turns to the moment of resistance and aligning torque Changing Pattern in a kind of accurately simulating vehicle actual travel process, this test unit can be used for investigating the influence to EPS power-assisted effect of Vehicle Speed, pavement behavior, load, front alignment angular dimensions and suspension parameter, so as to carry out assist characteristic rule to EPS, control strategy and the EPS instability Mechanism of EPS studied.
For solving the problems of the technologies described above, the invention provides the experimental investigation of vehicle electric power-assisted steering system device, comprise steering front wheel and suspension integrated system, mechanical steering system, mechanical steering structure installation stand, AC electrical machine controller, current sensor, torque sensor, vehicle speed sensor, data acquisition system (DAS) and numerical control electrohydraulic servo test system.The present invention is characterised in that: be provided with the wheel power input mechanism, with the travelling speed that provides test to need, investigation speed is to the influence of EPS; Be provided with the steering reversal simulation mechanism, offer the steering resisting moment and the aligning torque of steering with road surface in the simulating vehicle steering procedure; Be provided with load and divide equally load maintainer, with the influence of simulation wheel alignment parameter, suspension parameter, load aligning torque.
Described steering reversal simulation mechanism, as shown in Figure 6, between doughnut and exciting head, the steering reversal simulation mechanism has the load supporting tire load, the surface resistance aligning torque is provided, simulates the function on different road surfaces.The requirement that it is selected according to different test road pavement grades, the crawler belt of selected respective surfaces roughness is installed on the support rollers of steering reversal simulation mechanism, and the crawler belt of different surface roughness can be simulated the road surface of different surfaces attachment coefficient.Four of the steering reversal simulation mechanism survey torsion springs be evenly distributed in rotating shaft around, when steering wheel rotation, tyre rotation certain angle and track surface have produced moment of friction, this moment of friction makes four to survey torsion spring generation stretcher strain, the steering reversal simulation mechanism has produced aligning torque to tire, and the aligning torque that obtain this moment is the maximum aligning torque that the road surface can offer tire.
Described load is divided equally load maintainer, and as shown in Figure 7, it comprises: the loading case 56 that load is divided equally beam 57 and is placed on it.Load is divided equally the load average that beam 57 will load case 56 and is assigned on the automotive suspension of test unit, has kept the stable of test device systematic.Simultaneously, this load is divided equally the camber angle of back rake angle, leaning angle and tire that beam 57 can guarantee the tire stub.Front wheel Alignment Parameters can be guaranteed on structure, during test, can reflect accurately that load is to the influence of aligning torque in the motor turning process.
The spacing guiding mechanism of described steering reversal simulation mechanism, this mechanism had both limited vibrator telescopic shaft freely rotating in the course of the work, had guaranteed again that steering reversal simulation mechanism and tire and charger can move along the guidepost easy on and off.This mechanism has guaranteed the accurate measurement of aligning torque in the tire steering procedure.
Described wheel power importation adopted universal shaft coupling device, remedied the change of tire motor and tire distance in rotation process, and tire is with respect to the change of motor angle.Adopt speed reduction unit and chain sprocket drive structure double reduction, the speed that realized is adjustable on a large scale, and its velocity range is 0～100Km/h, can satisfy the rate request of Vehicular turn test.
During work:
Wheel power input motor is under the control of AC electrical machine controller, wheel power input mechanism and universal shaft coupling device link to each other with the axis of rolling of steering front wheel, provide power to wheel, AC motor control can be adjusted vehicle wheel rotational speed according to the requirement of test, vehicle wheel rotational speed is measured by vehicle speed sensor, and its value is given the data collecting card of system.Adjust the weight of counterweight in the load load maintainer, can adjust the vehicle loaded weight, whole loaded weight is loaded into steering front wheel by suspension system.According to power between the object is mutual characteristic, and steering reversal simulation mechanism simulation ground when motor turning just returns wheel with respect to the moment of resistance that tire produced, and the vehicle gravity aligning torque that carload produced when low-speed heave-load turns to.Selection has the crawler belt of different roughness and adjusts the Oscillation Amplitude and the frequency of numerical control electrohydraulic servo test system exciting head, the Surface of Trial Pavement of simulation different brackets.Torque sensor is positioned on the steering axle of mechanical steering system, is used to measure driver's rotating torque.Computing machine is gathered data such as force transducer, current sensor, vehicle speed sensor, torque sensor by data collecting card, and processs and displays by corresponding software, obtains test result.
The present invention can more accurately simulate by the force-bearing situation to wheel steering system in the laboratory, can reflect that factors such as carload, pavement behavior, wheel alignment parameter, suspension system, tire characteristics, car speed are to the stressed influence of steering.Utilize the present invention can be under simulated environment, carry out different EPS hardware and software debuggings under the various real vehicle situations, the control effect of the assist characteristic rule of research EPS system, the different control strategies of research also evaluates and optimizes, EPS is carried out parameter matching control strategy; Simultaneously, research EPS system failure mechanism.
Compare with existing test unit, the present invention has the following advantages:
1, considers the influence of the characterisitic parameter of suspension and tire to steering moment, load is divided equally load maintainer not only can finish the carload value-added tax function, and can guarantee the positional parameter of vehicle front-wheel, thereby make test unit can more accurately reflect the influence of load to aligning torque.
2, the wheel power input mechanism can provide the car speed of testing requirements, thereby test unit just can more accurately reflect the influence of car speed to the EPS system.
3, the steering reversal simulation mechanism can be simulated the performance impact of different brackets road surface to EPS, more accurately simulates simultaneously the size of steering resisting moment and aligning torque under different loads, speed, the pavement behavior.
Description of drawings
Fig. 1 is the electric boosting steering system synoptic diagram;
Fig. 2 is existing electric boosting steering system and spring-loaded system structural representation;
Fig. 3 is existing electric boosting steering system and resistance servo motor loading system structural representation;
Fig. 4 is vehicle electric servo steering system research test experiments horse structure synoptic diagram;
Fig. 5 is vehicle electric servo steering system research test experiments stand assembling synoptic diagram;
Fig. 6 is a steering reversal simulation mechanism synoptic diagram.Wherein Fig. 6 (a) is a front elevation, and Fig. 6 (b) is a vertical view.
Fig. 7 divides equally the load maintainer synoptic diagram for load.Wherein Fig. 7 (a) is a front elevation, Fig. 7 (b) A-A cross-wise direction view.
Fig. 8 is the power input device structural representation.
Fig. 9 is the spacing guiding mechanism synoptic diagram of roller tray.Wherein Fig. 9 (a) is a front elevation, and Fig. 9 (b) is a left view.
1 bearing circle; 2 turn to input shaft; 3 steering wheel torque sensors; 4 speed reduction units; 5 gears; 6 tooth bars; 7 drag links; 8 assisted electric machines; 9 controllers; 10 electromagnetic clutchs; 11 electromagnetic clutch control signals; 12 vehicle speed sensor; 12 ' vehicle speed signal; 13 ' steering wheel torque signal; 14 engine rotational speed signals; 15 turn to output shaft; 16 desirable power-assisted electric currents; 17 springs; 18 resistance servomotors; 19 power input systems; 20 torque measurement roller traies; 21 numerical control electrohydraulic servo test systems; 22 data collecting cards; 23 computing machines; The dynamo-electric stream of 24 ' assisted electric signal; 25 ' vehicle front-wheel weight signal; 26 ' steering wheel angle signal; 26 angular transducers; 27 ' displacement signal; 28 load chargers; 29 tire suspension systems; 30 portal frames; 31 load are divided equally load maintainer; 32 nylon bushs; 33 left suspension 34 left suspension struts; 35 steering reversal simulation mechanisms; The spacing guiding mechanism of 36 roller traies; The 37 numerical control electrohydraulic servo test .38 of system stands; 39 power input mechanisms; 40 tires; 41 right suspensions; 42 tension springs; 43 Connection Blocks; 44 intermediate supports axles; 45 bolts; 46 crawler belts; 47 ball bearings; 48 pressure ball bearings; 49 upright shafts; 50 rolling sleeves; 51 support the basin frame; 52 support sets; 53 springs connect inner disc; 54 springs connect outer dish; 55 end back shafts; 56 load case; 57 load are divided equally beam 58 varying-speed motors; 59 speed-regulating motor controllers; 60 speed reduction units; 61 minor sprockets; 62 chains; 63 hinge wheels; 64 supporting seats; 65 universal shaft coupling devices; 66 guide frames; 67 SDeflector bearings; 68; 69 location-plates
Embodiment
The present invention is further detailed explanation below in conjunction with accompanying drawing and example.
General structure synoptic diagram of the present invention as shown in Figure 4.
Vehicle speed signal 12 ' measured by vehicle speed sensor 12, this sensor is positioned on the axletree.This signal is one of key signal of determining the desirable booster torquemoment of motor.
Bearing circle dtc signal 13 ' measured by the torque sensor 3 that is positioned on the steering axle, it can measure the level of torque that is applied in driver's steering procedure.This signal is an another key signal of determining the desirable booster torquemoment of motor.
Assisted electric electromechanics stream signal 24 ' measured by the external hanging type Hall current sensor, it can measure the size of the dynamo-electric stream of assisted electric of electric boosting steering system, and one and the proportional voltage signal of current of electric are provided.
Vehicle front-wheel weight signal 25 ' measured by the force sensor signals in the numerical control electrohydraulic servo test system 21, expression is loaded into the carload of Vehicular turn front-wheel.
Displacement transducer 27 is positioned on the exciting head of numerical control electrohydraulic servo test system 21, gathers the distance that steering front wheel moves up and down, to data collecting card 22 provide displacement signal 27 '.
The running velocity signal that computing machine 23 is gathered according to data collecting card, the calculation engine tach signal transmits engine rotational speed signals 14 by data collecting card to EPS controller 9, makes the EPS can operate as normal.
Before the test, the counterweight of adjusting in the load charger 28 according to testing requirements reaches testing requirements, and the motor in the adjustment power input system 19 is to fixing speed.After on-test, the signal sampling analytic system starts automatically.The PC of sampling system monitors that the signal of each sensor of examination changes.In case steering wheel rotation, tire is done corresponding deflection around stub, and four tension springs of torque measurement roller tray 20 are tightened up, and steering resisting moment changes along with the variation of steering wheel angle, until reaching following maximal value that can reach of this driving cycle.Increase along with steering wheel angle, the steering-wheel torque signal increases gradually, when surpassing the power-assisted threshold value, the electric-control system instruction motor begins power-assisted, by the EPS system controller according to bearing circle dtc signal, Vehicle Speed, table look-up according to the assist characteristic curve and to determine the working current size of motor, the i.e. desirable power-assisted electric current of assisted electric machine.Current signal and desirable power-assisted electric current that controller is constantly gathered the assisted electric machine compare, adopt that suitable control strategy makes that the motor actual current is quick, little overshoot reach desirable power-assisted current value.When one turn to end cycle after, sampling analysis system can be drawn out steering-wheel torque, corner and the power-assisted electric current change curve with wheel weight, the road conditions of travelling and Vehicle Speed.And then analyze power-assisted effect, the assist characteristic curve of electric boosting steering system, the situation of change of aligning torque.
Test unit mechanical part shown in the accompanying drawing 5 comprises: portal frame 30, load are divided equally load maintainer 31, nylon bush 32, left suspension 33, left suspension strut 34, steering reversal simulation mechanism 35, the spacing guiding mechanism 36 of roller tray, numerical control electrohydraulic servo test system 37, stand 38, power input mechanism 39, tire 40, right suspension 41.
The placement of portal frame 30 levels on the ground, load is divided equally load maintainer 31 and is passed the crossbeam of portal frame through nylon bush 32, left suspension 33 is divided equally the left pedestal of load maintainer 31 with load respectively and the upper end of left suspension strut 34 is connected with bolt.The lower end of left side suspension strut 34 and the terminal pad of steering reversal simulation mechanism 35 are hinged.The lower end terminal pad of steering reversal simulation mechanism 35 is connected with exciting head terminal pad in the numerical control electrohydraulic servo test system 37 by bolt, tire 40 vertically is placed on the crawler belt of steering reversal simulation mechanism 35, and the driving shaft of power input mechanism 39 is connected with the axis hole of tire with bolt by flat key.The lower end of right suspension 41 is connected by the suspension pedestal of bolt and tire 40, and the upper end of right suspension is connected with bolt with the right pedestal that load is divided equally load maintainer 31.Stand 38 is installed in by foot bolt on the pedestal of portal frame 30, and the motor of power input mechanism 39 is installed on the support of stand 38 by bolt.Numerical control electrohydraulic servo test system 37 is installed on the pedestal of portal frame 30 by foot bolt, and is positioned at the terminal pad lower end of steering reversal simulation mechanism 35.
Before the test, Installation and Debugging steering reversal simulation mechanism 5, its structure is as shown in Figure 6.Comprise: tension spring 42, Connection Block 43, intermediate supports axle 44, bolt 45, crawler belt 46, ball bearing 47, pressure ball bearing 48, upright shafts 49, rolling sleeve 50, support basin frame 51, support set 52, spring connect inner disc 53, spring connects outer dish 54, holds back shaft 55.
Ball bearing 47 is positioned at upright shafts 49 lower ends, and is pressed on the axis hole lower surface of Connection Block 43.Pressure ball bearing 48 is enclosed within on the upright shafts 49, is pressed on the axis hole upper surface of Connection Block 43 by the bolt on it.By bolt spring being connected outer dish 54 is pressed on the upper surface of Connection Block 43.Spring connects inner disc 53 and is enclosed within on the upright shafts 49, and 4 tension spring 42 two ends are hooked in spring respectively and connect on the inside and outside dish.4 support sets 52, lower surface be positioned at spring connect inner disc 53 above, the upper surface is positioned at the lower surface, bottom of supporting basin frame 51.By upright shafts 49 bolt topmost support basin frame 51 is pressed on 4 support sets 52.Rolling sleeve 50 passes intermediate supports axle 44, and the end-face hole that supports basin frame 51 is passed at the two ends of intermediate supports axle 44.Two end back shafts 55 lay respectively at the two ends of supporting basin frame 51, by being connected adjusting bolt 45 location of supporting on basin frame 51 supports.Crawler belt 46 covers on 10 rolling sleeves 50, the degree of tightness that the end back shaft 55 by two ends is regulated crawler belts.
Load is divided equally load maintainer as shown in Figure 7, comprising: loading case 56, load are divided equally beam 57.The terminal pad that loads case 56 lower ends is connected by bolted with the terminal pad that load is divided equally beam 57.
Power input mechanism comprises as shown in Figure 8: varying-speed motor 58, speed-regulating motor controller 59, speed reduction unit 60, minor sprocket 61, chain 62, hinge wheel 63, supporting seat 64, universal shaft coupling device 65.Varying-speed motor 58 is through the output of speed reduction unit 60 power, and minor sprocket links to each other by the output shaft of flat key with speed reduction unit 60, and links to each other with the hinge wheel 63 of universal shaft coupling device 65 1 ends through chain, and universal shaft coupling device 65 is fixed by bolts on the stand 38 by supporting seat 64.The other end of universal shaft coupling device 65 links to each other with the tire axis hole with bolt by flat key.
The spacing guiding mechanism of roller tray comprises as shown in Figure 9: guide frame 66, SDeflector bearing 67, axle 68, location-plate 69.On the pedestal of portal frame 30, location-plate 69 is by being bolted to the lower surface of vibrator head terminal pad by bolted for guide frame 66, and two axles 68 pass the microscler bolt hole of location-plate 69 respectively and pass through nut fastening.SDeflector bearing 67 is positioned at of axle 68, positions by step surface, uses bolted.The position of regulating two axles 68 makes the guidepost of guide frame 66 be in the centre of two SDeflector bearings, and making the gap between SDeflector bearing and the guidepost is 0.1mm.
The present invention be used to study automobile EPS assist characteristic rule, the different control strategies of research the control effect and control strategy evaluated and optimized, EPS carried out parameter matching; Simultaneously, research EPS system failure mechanism.Regulate the tire positional parameter, can study the vehicle structure parameter and change the EPS Effect on Performance; Regulate loading case quality, motor speed, can study load, velocity variations the EPS Effect on Performance; Regulate the skin-friction coefficient of crawler belt, the excited frequency and the amplitude of exciting head, can study the road surface and disturb the EPS Effect on Performance.
Claims (5)
1. vehicle electric power-assisted steering system tester, comprise steering front wheel and suspension integrated system, mechanical steering system, mechanical steering structure installation stand, AC electrical machine controller, current sensor, torque sensor, vehicle speed sensor, data acquisition system (DAS) and numerical control electrohydraulic servo test system, it is characterized in that: be provided with wheel power input mechanism, steering reversal simulation mechanism, and load is divided equally load maintainer; Described steering reversal simulation mechanism, between doughnut and exciting head, the crawler belt of the different surface roughness on the road surface of selected simulation different surfaces attachment coefficient, be installed on the support rollers of steering reversal simulation mechanism, four of the steering reversal simulation mechanism survey torsion springs be evenly distributed in rotating shaft around; Described load is divided equally load maintainer and is comprised: the loading case (56) that load is divided equally beam (57) and is placed on it; Universal shaft coupling device has been adopted in described wheel power importation, adopts speed reduction unit and chain sprocket drive structure double reduction.
2. vehicle electric power-assisted steering system tester according to claim 1, it is characterized in that steering reversal simulation mechanism (5), comprising: tension spring (42), Connection Block (43), intermediate supports axle (44), bolt (45), crawler belt (46), ball bearing (47), pressure ball bearing (48), upright shafts (49), rolling sleeve (50), support basin frame (51), support set (52), spring connect inner disc (53), spring connects outer dish (54), holds back shaft (55); Wherein ball bearing (47) is positioned at upright shafts (49) lower end, and is pressed on the axis hole lower surface of Connection Block (43); Pressure ball bearing (48) is enclosed within on the upright shafts (49), is pressed on the axis hole upper surface of Connection Block (43) by the bolt on it; By bolt spring being connected outer dish (54) is pressed on the upper surface of Connection Block (43); Spring connects inner disc (53) and is enclosed within on the upright shafts (49), and 4 tension springs (42) two ends are hooked in spring respectively and connect on the inside and outside dish; Support set (52), lower surface be positioned at spring connect inner disc (53) above, the upper surface is positioned at the lower surface, bottom of supporting basin frame (51), makes by upright shafts (49) bolt topmost and supports basin frame (51) and be pressed on the support set (52); Rolling sleeve (50) passes intermediate supports axle (44), and the end-face hole that supports basin frame (51) is passed at the two ends of intermediate supports axle (44); Two end back shafts (55) lay respectively at the two ends of supporting basin frame (51), by being connected adjusting bolt (45) location of supporting on basin frame (51) support; Crawler belt (46) covers on 10 rolling sleeves (50), regulates the degree of tightness of crawler belt by the end back shaft (55) at two ends.
3. vehicle electric power-assisted steering system tester according to claim 1 is characterized in that described load divides equally load maintainer, and it comprises: load case (56), load is divided equally beam (57); The terminal pad that loads case (56) lower end is connected by bolted with the terminal pad that load is divided equally beam (57).
4. vehicle electric power-assisted steering system tester according to claim 1, it is characterized in that described power input mechanism, it comprises: varying-speed motor (58), speed-regulating motor controller (59), speed reduction unit (60), minor sprocket (61), chain (62), hinge wheel (63), supporting seat (64), universal shaft coupling device (65); Varying-speed motor (58) is exported through speed reduction unit (60) power, minor sprocket (61) links to each other by the output shaft of flat key with speed reduction unit (60), and link to each other with the hinge wheel (63) of universal shaft coupling device (65) one ends through chain, universal shaft coupling device (65) is fixed by bolts on the stand (38) by supporting seat (64); The other end of universal shaft coupling device (65) links to each other with the tire axis hole with bolt by flat key.
5. vehicle electric power-assisted steering system tester according to claim 1 is characterized in that being provided with the spacing guiding mechanism of steering reversal simulation mechanism, and it comprises: guide frame (66), SDeflector bearing (67), axle (68), location-plate (69); On the pedestal of portal frame (30), location-plate (69) is by being bolted to the lower surface of vibrator head terminal pad by bolted for guide frame (66), and two axles (68) pass the microscler bolt hole of location-plate (69) respectively; SDeflector bearing (67) is positioned at of axle (68); The position of regulating two axles (68) makes the guidepost of guide frame (66) be in the centre of two SDeflector bearings, and making the gap between SDeflector bearing and the guidepost is 0.1mm.
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Assignee: Chaoli Electrical Appliances Co., Ltd., Jiangsu Assignor: Jiangsu University Contract record no.: 2010320001092 Denomination of invention: Vehicle electric power-assisted steering system tester Granted publication date: 20100224 License type: Exclusive License Open date: 20080409 Record date: 20100820 |
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