CN101943626A - Dynamic calibration device of counter-force roller braking bench based on hydraulic servo - Google Patents
Dynamic calibration device of counter-force roller braking bench based on hydraulic servo Download PDFInfo
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- CN101943626A CN101943626A CN 201010257509 CN201010257509A CN101943626A CN 101943626 A CN101943626 A CN 101943626A CN 201010257509 CN201010257509 CN 201010257509 CN 201010257509 A CN201010257509 A CN 201010257509A CN 101943626 A CN101943626 A CN 101943626A
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Abstract
The invention relates to a dynamic calibration device of a counter-force roller braking bench based on a hydraulic servo, mainly comprising a hydraulic servo force application device, a buffering shock absorption mechanism, a force transmission beam mechanism, a force measurement mechanism and a support frame mechanism. The invention mainly aims to solve the problem that the traditional counter-force roller braking bench can not be used for evaluating the dynamic response of a braking bed. The dynamic calibration device is arranged on the counter-force roller braking bench to form a force closed-loop control system to provide a force value changed according to an ideal standard force value curve for the calibration of the braking bed, and the standard force value curve is compared with a measuring force value curve measured by the force measurement sensor of the braking bed per se and obtained after being amplified by a filter amplifying circuit to evaluate the dynamic response quality of the braking bed to realize dynamic calibration.
Description
Technical field
The invention belongs to calibration facility, particularly relate to a kind of dynamic calibration device of drum reaction braking checkout stand based on hydraulic servo.
Background technology
At present, on mobile testing line, demarcation to drum reaction braking checkout stand is to adopt the specific weight lever method, method is as follows: special-purpose lever is fixed tightly on the brake platform suitable position, adjust the static equilibrium and the level of lever, select several measurement points, be loaded on full scale step by step by the number percent of brake platform full scale, off-load reads the corresponding brake platform indicating value of each point to zero step by step then.Its outstanding characteristics are static, and brake platform is a dynamic process when detecting damping force.Because static demarcation is to react the dynamic response of brake platform,, make testing reliability descend so can occur to react the objective reality situation more truly by the qualified brake platform resulting data when testing damping force of static demarcating.
Summary of the invention
The objective of the invention is the problem that to make an appraisal to the dynamic response of brake platform for the calibration facility that solves existing drum reaction braking checkout stand, provide a kind of simple in structure, test is reliably based on the dynamic calibration apparatus of the drum reaction braking checkout stand of hydraulic servo.
Above-mentioned purpose of the present invention can be achieved through the following technical solutions, and accompanying drawings is as follows:
A kind of dynamic calibration device of drum reaction braking checkout stand based on hydraulic servo mainly is made up of hydraulic servo force application apparatus A, buffer damping mechanism B, the C of transfer beam mechanism, force measuring machine D and the E of support frame mechanism,
The end of buffer damping mechanism B is fixedly connected on the C of transfer beam mechanism by oscillating bearing 38; The end of force measuring machine D is fixedly connected on the C of transfer beam mechanism by axis pin base 43, and the other end is fixedlyed connected with the speed reduction unit of drum reaction type brake platform test by stretching out frame 54; The C of transfer beam mechanism is connected on the E of support frame mechanism by globe bearing 39, and the E of support frame mechanism is bolted to connection on the frame of brake platform.
Said hydraulic servo force application apparatus A comprises Hydraulic Station F and force application mechanism G two parts, and the end of force application mechanism G is fixedly connected on the end of buffer damping mechanism B by piston rod 20.Described servo force application mechanism A provides driving force, through buffer damping mechanism B, the C of transfer beam mechanism and force measuring machine D transfer function to the brake platform speed reduction unit, this power value feeds back to electrohydraulic servo valve 29 among the force application mechanism G by the force cell that is contained among the force measuring machine D through servoamplifier, after adjusting on request by electrohydraulic servo valve 29, control is applied to the power value size on the brake platform speed reduction unit, constitutes the closed-loop control system of power value.
Said Hydraulic Station F comprises: be fixedly connected on the motor 1 on the fuel tank cap 5, filtrator 7, integrated package 8, accumulator 13 and pouring orifice screen pack 14, connect on the dish 2 by being bolted to motor, and the hydraulic pump 4 that links to each other with motor 1 by shaft coupling 3, one end links to each other with integrated package 8 by oily steel pipe, the retaining valve 11 that the other end links to each other with threeway 12 by oily steel pipe, the tensimeter 10 that links to each other with integrated package 8 by oily steel pipe, be installed in the liquid level thermometer 15 on the side of oil box 6, by being bolted to the surplus valve 9 on the integrated package 8, described fuel tank cap 5 is connected on the oil box 6 by screw retention, one end of threeway 12 is connected with accumulator 13 by oily steel pipe, and the other end links to each other with electrohydraulic servo valve 29 among the force application mechanism G by flexible pipe;
Described force application mechanism G is mainly by oil cylinder assembly H, oscillating bearing 33, electrohydraulic servo valve 29 and contiguous block 30 are formed, described oil cylinder assembly H is connected with middle link slot steelframe 57 bolt among the E of support frame mechanism by oscillating bearing 33, described electrohydraulic servo valve 29 is by being bolted on the contiguous block 30, advancing of contiguous block 30, oil-out links to each other by the threeway 12 among flexible pipe and the Hydraulic Station F and the oil return opening of oil box 6 respectively, and electrohydraulic servo valve 29 two ends are connected with oil cylinder rear flange 31 with oil cylinder forward flange 23 among the oil cylinder assembly H by steel pipe 26 respectively.
Described oil cylinder assembly H is made up of oil cylinder 28 and piston rod 20, oil cylinder forward flange 23 is fixedlyed connected with 28 by thru-bolt 27 with oil cylinder rear flange 31, afterbody bearing pin Connection Block 32 is fixedlyed connected with oil cylinder rear flange 31 by bolt, piston rod 20 is assemblied in 28 li of oil cylinders, and fixedly connected with piston 21 by clamp nut 22, an end of piston rod 20 links to each other with spring contiguous block 35 among the buffer damping mechanism B by screw thread.
Said buffer damping mechanism B mainly is made up of volute spring 34, the two ends of volute spring 34 are separately installed with spring contiguous block 35, two anti-loosing slices 36 are fixedly connected on the spring contiguous block 35 at volute spring 34 two ends respectively by screw, to prevent volute spring 34 plaies, oscillating bearing 38 is fixedly connected on by M20 clamp nut 37 on the spring contiguous block 35 of volute spring 34 1 ends, and the spring contiguous block 35 of the other end of volute spring 34 is fixedlyed connected with piston rod 20 among the servo force application apparatus A by M20 clamp nut 37.
The said transfer beam C of mechanism is made up of transfer beam 41 and transfer beam axle 42, and transfer beam 41 is connected with transfer beam axle 42 interference fit, and the two ends of transfer beam axle 42 are connected with globe bearing 39 respectively, and carry out axial location by transfer beam axle sleeve 40.
Said force measuring machine D is mainly by force cell, last connection steel pipe 48 with under be connected steel pipe 51 and form, last connection steel pipe 48 connects by passing through thread bush 50 with an end that is connected steel pipe 51 down, and it is fastening by clip 49, the other end of last connection steel pipe 48 is threaded with M39 spherical plain bearing rod end 46, and it is locking by M39 clamp nut 47, M39 spherical plain bearing rod end 46 is connected with axis pin base 43 by pin type force cell 45, and the 44 pairs of pin type force cells of catch 45 that are connected on the axis pin base 43 by screw retention carry out axial location and circumferential registration, under connect steel pipe 51 and be threaded with oscillating bearing 53, and locking by M33 clamp nut 52, oscillating bearing 53 is bolted to connection and is stretching out on the frame 54.
Among the said support frame E of mechanism, preceding support slot steelframe 55 is connected channel-section steel 58 connections by indirect channel-section steel frame 57 with the back, two oblique straining beams 56 of equal angle by bolt be connected preceding support slot steelframe 55 with after be connected on the channel-section steel 58; Before support slot steelframe 55 the lower end with after be connected channel-section steel 58 and fixedly connected with the frame of brake platform by bolt.
The present invention can solve the problem that the calibration facility of existing drum reaction braking checkout stand can't be made an appraisal to the dynamic response of brake platform, realizes the dynamic calibration to drum reaction braking checkout stand, thereby guarantees the reliability of brake platform test data.The design is simple in structure, and test is reliable.
Description of drawings
Fig. 1 is based on the layout synoptic diagram of dynamic calibration device of drum reaction braking checkout stand on brake tester of hydraulic servo;
Fig. 2 is based on the dynamic calibration device of drum reaction braking checkout stand synoptic diagram of hydraulic servo;
Fig. 3 is based on the dynamic calibration device of drum reaction braking checkout stand side view of hydraulic servo;
Fig. 4 is the Hydraulic Station synoptic diagram;
Fig. 5 is the Hydraulic Station side sectional view;
Fig. 6 (a) is the Hydraulic Station top view;
Fig. 6 (b) is the Hydraulic Station side view;
Fig. 7 (a) is the force application mechanism synoptic diagram;
Fig. 7 (b) is the force application mechanism side partial sectional view;
Fig. 8 is the buffer gear synoptic diagram;
Fig. 9 is the transfer beam structural scheme of mechanism;
Figure 10 (a) is the force measuring machine synoptic diagram;
Figure 10 (b) is the local enlarged diagram on Figure 10 (a) top;
Figure 10 (c) is the local enlarged diagram at Figure 10 (a) middle part;
Figure 11 (a) is the support frame structural scheme of mechanism;
Figure 11 (b) is a support frame mechanism side view;
Figure 12 is the power value closed-loop control system figure of hydrostatic control.
Among the figure: the A. hydraulic servo force application apparatus B. buffer damping mechanism C. transfer beam D. of the mechanism force measuring machine E. support frame F. of mechanism Hydraulic Station G. force application mechanism H. oil cylinder assembly
1. 2. 3. 4. 5. 6. 7. 8.9. 10. 11. 12. 13. 14. 15.16. 17. 18. 19. 20. 21. 22. 23. 24. 25. 26. 27. 28.29. 30. 31. 32. 33. 34. 35. 36. 37. 38. 39. 40. 41. 42. 43. 44. 45. 46. 47. 48. 49. 50. 51. 52.53. 54. 55. 56. 57. 58.
Embodiment
Shown in accompanying drawing, further specify the particular content of the present invention and the course of work thereof.
Referring to Fig. 1,2,3, a kind of dynamic calibration device of drum reaction braking checkout stand based on hydraulic servo mainly is made up of hydraulic servo force application apparatus A, buffer damping mechanism B, the C of transfer beam mechanism, force measuring machine D and the E of support frame mechanism.The end of buffer damping mechanism B is fixedly connected on the C of transfer beam mechanism by oscillating bearing 38; The end of force measuring machine D is fixedly connected on the C of transfer beam mechanism by axis pin base 42, and the other end is fixedlyed connected with the speed reduction unit of drum reaction type brake platform test by stretching out frame 54; The C of transfer beam mechanism is connected on the E of support frame mechanism by globe bearing 39, and the E of support frame mechanism is bolted to connection on the frame of brake platform.Said hydraulic servo force application apparatus A is made up of Hydraulic Station F and force application mechanism G, and the end of force application mechanism G is fixedly connected on the end of buffer damping mechanism B by piston rod 20.Described servo force application apparatus A provides driving force, through buffer damping mechanism B, C of transfer beam mechanism and force measuring machine D transfer function are to the brake platform speed reduction unit, this power value feeds back to electrohydraulic servo valve 29 among the force application mechanism G by the force cell that is contained among the force measuring machine D through servoamplifier, after adjusting on request by electrohydraulic servo valve 29, control is applied to the power value size on the brake platform speed reduction unit, the closed-loop control system of formation power value, accurately control is applied to the power value size on the brake platform speed reduction unit, power by the curvilinear motion of metric system power value is provided, thereby the ergometry value curve that obtains after this proof force value curve and the process filter amplification circuit that is recorded by the force cell of brake platform itself is compared, estimate the dynamic response quality of brake tester, realize dynamic calibration.
In drum reaction braking checkout stand, the speed reduction unit and the arm of force are fixed on the same drum shaft, and this device is applied to the power on the brake platform speed reduction unit so, also just have been loaded on the force cell of brake platform itself by the arm of force.As required, this device can provide the power according to the curvilinear motion of metric system power value, and this power can realize by the closed-loop control system of above-mentioned power, and precisely controlled.Ergometry value curve with obtaining after this proof force value curve and the process filter amplification circuit that is recorded by the force cell of brake platform itself compares, and estimates the dynamic response quality of brake tester.
Referring to Fig. 4,5,6,7, said hydraulic servo force application apparatus A is made up of Hydraulic Station F and force application mechanism G, and among the said Hydraulic Station F, motor 1 connects dish 2 by motor and is fixedly connected on the fuel tank cap 5; Hydraulic pump 4 connects on the dish 2 by being bolted to motor, and links to each other with motor 1 by shaft coupling 3; Filtrator 7 is installed on the fuel tank cap 5, and its oil-in links to each other with the oil-out of hydraulic pump 4 by oily steel pipe, and its oil-in is connected with integrated package 8 by oily steel pipe; Surplus valve 9 is by being bolted on the integrated package 8, and integrated package 8 is bolted to connection on fuel tank cap 5, and tensimeter 10 links to each other with integrated package 8 by oily steel pipe; One end of retaining valve 11 links to each other with integrated package 8 by oily steel pipe, the other end links to each other with threeway 12 by oily steel pipe, one end of threeway 12 is connected with accumulator 13 by oily steel pipe, and accumulator 13 is installed on the fuel tank cap 5, and the other end of threeway links to each other with electrohydraulic servo valve 29 among the force application mechanism G by flexible pipe; Pouring orifice screen pack 14 is installed on the fuel tank cap 5, and fuel tank cap 5 is connected on the oil box 6 by screw retention; Liquid level thermometer 15 is installed on the leading flank of oil box 6, and drainage plug 16 is installed in the lower end of the leading flank of oil box 6, and attaching type hose adapter 18 is installed in the upper end of oil box 6 trailing flanks.Said force application mechanism G mainly is made up of oil cylinder assembly H, oscillating bearing 33, electrohydraulic servo valve 29 and contiguous block 30, in oil cylinder assembly H, oil cylinder forward flange 23 is fixedlyed connected with oil cylinder 28 by thru-bolt 27 with oil cylinder rear flange 30, afterbody bearing pin Connection Block 32 is fixedlyed connected with oil cylinder rear flange 31 by bolt, and piston rod 20 is fixedlyed connected with piston 21 by clamp nut 22 and is assemblied in 28 li of oil cylinders; Afterbody bearing pin Connection Block 32 among the oil cylinder assembly H is connected with oscillating bearing 33 by screw thread; Electrohydraulic servo valve 29 is by being bolted on the contiguous block 30, and the oil-in of contiguous block 30 links to each other with threeway 12 among the Hydraulic Station F by flexible pipe, and the oil-out of contiguous block 30 links to each other with the oil return opening of oil box 6 among the Hydraulic Station F by flexible pipe; The two ends of electrohydraulic servo valve 29 are connected with oil cylinder rear flange 31 with oil cylinder forward flange 23 among the oil cylinder assembly H by steel pipe 26 respectively, 25 pairs of steel pipes 26 of articulated pipe joint 24 and articulated pipe connector screw and the effect of playing oil cylinder forward flange 23 and being connected of oil cylinder rear flange 31 connection and fixing; One end of piston rod 20 links to each other with spring contiguous block 35 among the buffer damping mechanism B by screw thread, and oscillating bearing 33 is connected with middle link slot steelframe 57 bolt among the E of support frame mechanism.
Referring to Fig. 8, said buffer damping mechanism B mainly is made up of volute spring 34, the two ends of volute spring 34 are separately installed with spring contiguous block 35, two anti-loosing slices 36 are fixedly connected on the spring contiguous block 35 at volute spring 34 two ends respectively by screw, to prevent volute spring 34 plaies, oscillating bearing 38 is fixedly connected on by M20 clamp nut 37 on the spring contiguous block 35 of volute spring 34 1 ends, and the spring contiguous block 35 of the other end of volute spring 34 is fixedlyed connected with piston rod 20 among the servo force application apparatus A by M20 clamp nut 37.So the force application mechanism G of servo force application apparatus A and buffer damping mechanism B have just formed one two power linkage, thereby avoided unnecessary mechanical interference and, reduced labour intensity the excessive demand of whole device assembly precision.
Referring to Fig. 9, the said transfer beam C of mechanism is by globe bearing 39, transfer beam axle sleeve 40, and transfer beam 41 and transfer beam axle 42 are formed.
Referring to Figure 10, said force measuring machine D is by axis pin base 43, catch 44, pin type force cell 45, M39 spherical plain bearing rod end 46, M39 clamp nut 47, on connect steel pipe 48, clip 49, thread bush 50, under connect steel pipe 51, M33 clamp nut 52, oscillating bearing 53 stretches out frame 54 and forms.The end of force measuring machine D is connected with transfer beam 41 set bolts among the C of transfer beam mechanism by axis pin base 43, the other end is connected with the reducer casing set bolt of drum reaction braking checkout stand by stretching out frame 54, so pin type side force sensor 45 tests out the power value that is applied on the drum reaction braking checkout stand reducer casing, and this power value fed back to servo-driver 1 among the servo force application mechanism A, servo-driver 1 is adjusted the torque of servomotor 2 more as requested, thereby change the power value that is applied on the drum reaction braking checkout stand reducer casing, reach requirement power value size.Thread bush 50 can be adjusted and connect steel pipe 48 and the relative position that is connected steel pipe 51 down, and fastening by clip 49, plays locking effect.
Referring to Figure 11 (a), 11 (b), the described support frame E of mechanism is by preceding support slot steelframe 55, the oblique straining beam 56 of equal angle, and middle link slot steelframe 57, the back connects channel-section steel 58 and forms.Before support slot steelframe 55 by middle link slot steelframe 57 with after be connected channel-section steel 58 connections, before two oblique straining beams 56 of equal angle are connected by bolt support slot steelframe 55 with after be connected on the channel-section steel 58, the lower end of preceding support slot steelframe 55 with after be connected channel-section steel 58 and fixedly connected with the frame of brake platform by bolt.The upper end of preceding support slot steelframe 55 is connected with the C of transfer beam mechanism, and middle link slot steelframe 57 is connected with servo force application mechanism A.
Referring to Figure 12, described is the closed loop power value control system calcspar of Hydrauservo System, the circle on a figure left side is represented one " summing point ", promptly input or command signal are compared with force feedback signal, the error signal that exists is delivered in the servoamplifier, servoamplifier produces a proportional signal of error signal with input to electrohydraulic servo valve, and electrohydraulic servo valve is again according to the action of signal controlling cylinder.
Claims (2)
1. the dynamic calibration device of drum reaction braking checkout stand based on hydraulic servo mainly is made up of hydraulic servo force application apparatus (A), buffer damping mechanism (B), transfer beam mechanism (C), force measuring machine (D) and support frame mechanism (E),
It is characterized in that, described hydraulic servo force application apparatus (A) comprises Hydraulic Station (F) and force application mechanism (G) two parts, said Hydraulic Station (F) comprising: be fixedly connected on the motor (1) on the fuel tank cap (5), filtrator (7), integrated package (8), accumulator (13) and pouring orifice screen pack (14), connect on the dish (2) by being bolted to motor, and the hydraulic pump (4) that links to each other with motor (1) by shaft coupling (3), one end links to each other with integrated package (8) by oily steel pipe, the retaining valve (11) that the other end links to each other with threeway (12) by oily steel pipe, the tensimeter (10) that links to each other with integrated package (8) by oily steel pipe, be installed in the liquid level thermometer (15) on the side of oil box (6), by being bolted to the surplus valve (9) on the integrated package (8), described fuel tank cap (5) is connected on the oil box (6) by screw retention, one end of threeway (12) is connected with accumulator (13) by oily steel pipe, and the other end links to each other with electrohydraulic servo valve (29) in the force application mechanism (G) by flexible pipe;
Described force application mechanism (G) is mainly by oil cylinder assembly (H), oscillating bearing (33), electrohydraulic servo valve (29) and contiguous block (30) are formed, described oil cylinder assembly (H) is connected with middle link slot steelframe (57) bolt in the support frame mechanism (E) by oscillating bearing (33), described electrohydraulic servo valve (29) is by being bolted on the contiguous block (30), advancing of contiguous block (30), oil-out links to each other by the threeway (12) in flexible pipe and the Hydraulic Station (F) and the oil return opening of oil box (6) respectively, and electrohydraulic servo valve (29) two ends are connected with oil cylinder rear flange (31) with oil cylinder forward flange (23) in the oil cylinder assembly (H) by steel pipe (26) respectively.
2. a kind of dynamic calibration device of drum reaction braking checkout stand according to claim 1 based on hydraulic servo, it is characterized in that, described oil cylinder assembly (H) is made up of oil cylinder (28) and piston rod (20), oil cylinder forward flange (23) is fixedlyed connected with (28) by thru-bolt (27) with oil cylinder rear flange (31), afterbody bearing pin Connection Block (32) is fixedlyed connected with oil cylinder rear flange (31) by bolt, piston rod (20) is assemblied in oil cylinder (28) lining, and fixedly connected with piston (21) by clamp nut (22), an end of piston rod (20) links to each other with spring contiguous block (35) in the buffer damping mechanism (B) by screw thread.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010102575096A CN101943626B (en) | 2010-08-19 | 2010-08-19 | Dynamic calibration device of counter-force roller braking bench based on hydraulic servo |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010102575096A CN101943626B (en) | 2010-08-19 | 2010-08-19 | Dynamic calibration device of counter-force roller braking bench based on hydraulic servo |
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| CN101943626A true CN101943626A (en) | 2011-01-12 |
| CN101943626B CN101943626B (en) | 2012-08-08 |
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| CN2010102575096A Expired - Fee Related CN101943626B (en) | 2010-08-19 | 2010-08-19 | Dynamic calibration device of counter-force roller braking bench based on hydraulic servo |
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Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN102768117A (en) * | 2012-07-03 | 2012-11-07 | 浙江江兴汽车检测设备有限公司 | Portable dynamic wheel type calibrator for roller opposite force type automobile brake inspection bench |
| CN105043664A (en) * | 2015-08-21 | 2015-11-11 | 中国工程物理研究院总体工程研究所 | Calibration device for special high-temperature force measurement sensor |
| CN106404401A (en) * | 2016-08-31 | 2017-02-15 | 北京精密机电控制设备研究所 | Zero-position locking test device and test method for servo mechanism |
| CN106908233A (en) * | 2017-03-17 | 2017-06-30 | 西北工业大学 | The cabin door lock reliability test of varying load loading can be realized |
| CN109738117A (en) * | 2019-02-01 | 2019-05-10 | 广东省计量科学研究院（华南国家计量测试中心） | A kind of drum reaction brake test bench device for dynamically detecting |
| CN113804458A (en) * | 2021-09-03 | 2021-12-17 | 广州计量检测技术研究院 | Motor vehicle dynamic braking performance calibration device and calibration system |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN102768117A (en) * | 2012-07-03 | 2012-11-07 | 浙江江兴汽车检测设备有限公司 | Portable dynamic wheel type calibrator for roller opposite force type automobile brake inspection bench |
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| CN106404401A (en) * | 2016-08-31 | 2017-02-15 | 北京精密机电控制设备研究所 | Zero-position locking test device and test method for servo mechanism |
| CN106404401B (en) * | 2016-08-31 | 2019-04-09 | 北京精密机电控制设备研究所 | A kind of servo mechanism zero-bit lock test device and test method |
| CN106908233A (en) * | 2017-03-17 | 2017-06-30 | 西北工业大学 | The cabin door lock reliability test of varying load loading can be realized |
| CN109738117A (en) * | 2019-02-01 | 2019-05-10 | 广东省计量科学研究院（华南国家计量测试中心） | A kind of drum reaction brake test bench device for dynamically detecting |
| CN109738117B (en) * | 2019-02-01 | 2023-08-15 | 广东省计量科学研究院（华南国家计量测试中心） | Dynamic detection device for roller counter-force type braking inspection bench |
| CN113804458A (en) * | 2021-09-03 | 2021-12-17 | 广州计量检测技术研究院 | Motor vehicle dynamic braking performance calibration device and calibration system |
| CN113804458B (en) * | 2021-09-03 | 2023-06-30 | 广州计量检测技术研究院 | Dynamic braking performance calibration device and calibration system for motor vehicle |
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