CN102963345B - Driven hydraulic-brake hydraulic system with velocity compensator - Google Patents
Driven hydraulic-brake hydraulic system with velocity compensator Download PDFInfo
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- CN102963345B CN102963345B CN201210514569.0A CN201210514569A CN102963345B CN 102963345 B CN102963345 B CN 102963345B CN 201210514569 A CN201210514569 A CN 201210514569A CN 102963345 B CN102963345 B CN 102963345B
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Abstract
The invention relates to a driven hydraulic-brake hydraulic system with a velocity compensator, which comprises a driven hydraulic-brake hydraulic system. The driven hydraulic-brake hydraulic system with the velocity compensator is characterized in that a branch circuit between a damping inlet and a damping outlet of brake return oil is connected with the velocity compensator; the velocity compensator is a piston-type hydraulic cylinder without a piston rod; one side cavity of a piston of the piston-type hydraulic cylinder is communicated with the damping inlet by a pipeline; a return spring is arranged in the other side cavity of the piston of the piston-type hydraulic cylinder; and the cavity accommodating the return spring is communicated with the damping outlet by a pipeline. The driven hydraulic-brake hydraulic system with the velocity compensator has the benefits that the hydraulic system can effectively shorten brake time and improve safety and reliability; the velocity compensator has a simple structure and is convenient for series and batch production; the driven hydraulic-brake hydraulic system is convenient to install and flexible and reliable to operate; the compensation capacity of the velocity compensator is quantitatively controlled and is very convenient to change; and working performance is not influenced by environmental temperature.
Description
Technical field
The invention belongs to control device for hydraulic brake, be specifically related to passive type hydraulic brake control loop.
Background technology
At present in the brake process of passive type hydraulic brake, because friction lining and the brake disc of drg need to retain certain interval, in each braking procedure, hydraulic actuator piston needs one section of invalid stroke of many operations, eliminate these gaps and extended whole braking time, be unfavorable for the safe handling of equipment.
The large piston of passive type hydraulic brake when braking hydraulic actuating cylinder will complete a total stopping distance △ S under the effect of disk spring, it comprise out of control in braking response process apart from △ S1 (sending the distance that braking maneuver instruction to drg starts to produce mechanism's operation in this one-phase of lock torque from operator) and braking deceleration apart from △ S2 (drg starts to apply lock torque to the distance of this one-phase of kinematic mechanism stop motion).And braking time t mainly contains 3 parts compositions: electrical response t delay time
ea: the time of sending braking maneuver instruction to drg drive control valve dead electricity and starting to move from operator; Mechanical response t delay time
ma: after drg drive control valve dead electricity, drg starts to move the time that starts to produce lock torque to drg; Braking deceleration time t
b: drg starts to apply lock torque to the time of brake off moment.Be total stopping distance △ S=△ S1+ △ S2, braking time t=t
ea+ t
ma+ t
b.Traditional passive type hydraulic brake does not have velocity compensation function, mechanical response time t
macorresponding with braking time t long, braking safety and poor reliability.
Therefore, invent a kind of velocity compensator and become technical barrier urgently to be resolved hurrily to improve the safe reliability of braking.
Summary of the invention
The object of the invention is to invent a kind of velocity compensator, reduce the mechanical response time in passive type hydraulic brake brake process, thereby reduce braking time, improve safety, reliability and the stationarity of drg work.
Technical scheme of the present invention is: a kind of passive type hydraulic brake hydraulic efficiency pressure system of tape speed compensator, comprise passive type hydraulic brake hydraulic efficiency pressure system, passive type hydraulic brake hydraulic efficiency pressure system is by the passive type hydraulic brake connecting with pipeline, oil pump, braking electromagnetic valve, damping, electromagnetic valve boosts, fuel tank, energy storage, manual pump and safety valve form, the import and export P1 of passive type hydraulic brake and leakage hydraulic fluid port T are communicated with system circuit and fuel tank respectively by pipeline, on the pipeline being communicated with fuel tank at the import and export P1 of passive type hydraulic brake, be serially connected with damping and braking electromagnetic valve, between the import of damping and outlet, be connected to a branch road, the oil suction of oil pump is communicated with fuel tank, oil delivery side of pump respectively with safety valve, energy storage, electromagnetic valve boosts, the import and export P1 of manual pump and passive type hydraulic brake is communicated with, the passive type hydraulic brake hydraulic efficiency pressure system that it is characterized in that described tape speed compensator also comprises velocity compensator, velocity compensator is connected on the branch road between damping import and outlet, described velocity compensator is the piston-type hydraulic cylinder of piston-rodless, one side chamber of piston-type hydraulic cylinder piston is communicated with damping inlet ductwork, opposite side is equipped with retracing spring in chamber, the chamber that retracing spring is housed is communicated with damping export pipeline.
The velocity compensator of the passive type hydraulic brake hydraulic efficiency pressure system of a kind of tape speed compensator of the present invention, comprise the piston-type hydraulic cylinder being formed by housing, Combined seal ring of piston, piston, retracing spring, end cap seal circle and end cap, it is characterized in that described housing is tubular, bottom centre position place has the communication port being connected with passive type hydraulic brake hydraulic efficiency pressure system damping inlet ductwork; The inner centre of described end cap is with axle shape platform, axle shape platform centre has the centre hole that connects two ends, the mouth of centre hole end cap outside is the communication port being connected with passive type hydraulic brake hydraulic efficiency pressure system damping export pipeline, end cap seal is connected to shell nozzle end, in end cap, on axle shape platform, has draining mechanism; Described piston is not with piston rod, piston is arranged in housing by Combined seal ring of piston, and the reference position that piston is installed is in the bottom of housing, and described retracing spring is arranged in the housing between piston and end cap, retracing spring one end and piston connect, and the other end and end cap connect.
The velocity compensator of the passive type hydraulic brake hydraulic efficiency pressure system for tape speed compensator of the present invention, it is characterized in that described piston is provided with stroke pin, described stroke pin center has endoporus and the assembling screw that connects both ends of the surface, the external diameter of stroke pin and the endoporus of piston are fixed on piston stroke pin with interference fit, outside stroke pin, between the inner axle shape of end face and end cap you face, distance is s, 0 < s≤p
n* π * d
2/ 4k-S
0, p in formula
nfor velocity compensator overcomes the operation pressure that spring stiffness produces action, d is diameter of piston, the rigidity that k is retracing spring, S
0for initial compression amount after retracing spring assembling, the volume that the corresponding volume of s and piston area will compensate while being braking.
The velocity compensator of the passive type hydraulic brake hydraulic efficiency pressure system for tape speed compensator of the present invention, the guidance mode that it is characterized in that described retracing spring is outer guiding or interior guiding, described outer guiding is that total backlash is 0.8mm～1.0mm between the excircle of retracing spring and inner walls, and retracing spring excircle is led by inner walls; Described interior guiding is on axle shape platform, orienting sleeve to be housed in end cap, orienting sleeve is sleeved on the interior axle shape platform of end cap, orienting sleeve front end stretches in the stroke pin pin-and-hole of piston, orienting sleeve inner circle is sleeved on stroke pin, orienting sleeve aft end face abuts against on end cap, between the stroke pin pin-and-hole bottom surface of front end face and piston, there is s distance, 0 < s≤p
n* π * d
2/ 4k-S
0, p in formula
nfor velocity compensator overcomes the operation pressure that spring stiffness produces action, d is diameter of piston, the rigidity that k is retracing spring, S
0for initial compression amount after retracing spring assembling, retracing spring is placed in outside orienting sleeve, and between the inner periphery of retracing spring and orienting sleeve excircle, total backlash is 0.5mm～0.6mm, by retracing spring inner periphery and orienting sleeve excircle, is led.
The velocity compensator of the passive type hydraulic brake hydraulic efficiency pressure system for tape speed compensator of the present invention, is characterized in that the maximum working pressure (MWP) p of described velocity compensator
nmax< p
z, the minimum working pressure power p of velocity compensator
nmin>3MPa, wherein p
zwhile braking for drg, disc brake spring discharges corresponding oil pressure completely.
The velocity compensator of the passive type hydraulic brake hydraulic efficiency pressure system for tape speed compensator of the present invention, while it is characterized in that described drg braking, disc brake spring discharges corresponding oil pressure p completely
zbetween 9MPa～11MPa, velocity compensator overcomes the operation pressure p that spring stiffness produces action
nbetween 3MPa～7MPa.
The velocity compensator of the passive type hydraulic brake hydraulic efficiency pressure system for tape speed compensator of the present invention, is characterized in that in described end cap, the draining mechanism on axle shape platform is draining hole or drain pan, and draining hole or drain pan communicate with the axle shape platform centre hole of axle.
The velocity compensator of the passive type hydraulic brake hydraulic efficiency pressure system for tape speed compensator of the present invention, is characterized in that described retracing spring is disk spring.
Principle of work of the present invention is: braking electromagnetic valve dead electricity during braking, due to damping convection current quantitative limitation, the hydraulic pressure oil of the large plunger shaft of drg is under the effect of disc spring force, the interim admission velocity compensator rapidly of compensation capacity △ V of a part, promotion piston moves right, compression reseting spring compresses s distance to the right, compensation capacity △ V=π * d
2s/4.When drg completes braking, the hydraulic fluid pressure of plunger shaft declines gradually by damping, and pressure drop to regularly, compressed retracing spring promotes piston reset gradually, this part hydraulic oil of compensation capacity △ V is expelled back into fuel tank, returns to initial position, wait for next brake operating.
In this course, velocity compensator rapid compensation capacity of △ V in absorption brake in the short time after drg receives braking instruction, thereby improve drg running under braking speed, complete as early as possible out of control apart from △ S1, when velocity compensator piston completes after stroke s, absorbed after the hydraulic oil of compensation capacity △ V, drg retro-speed returns to the speed of being controlled by damping substantially completely, like this actv. is shortened to t
matime, also shortened whole braking time t simultaneously.
Suppose the large diameter of piston D of drg, distance out of control is △ S1, desired volume (not considering the factors such as friction lining abrasion loss) the V=π * D that during drg braking, hydraulic oil discharges
2* △ S1/4, compensation capacity is got △ V=V*2/3 left and right, and all the other V*1/3 consider normally by damping hole part, and leave certain surplus.△ V=π * d like this
2s/4=(2* π * D
2* △ S1)/(3*4), can obtain thus: s=2*D
2* △ S1/ (3*d
2).
The position of virgin state piston is positioned at the end of oil-feed side under the effect of retracing spring.As oil-feed lateral pressure oil pressure p ﹥ 4kS
0/ π d
2time, piston 4 compression reseting spring to the right under the effect of pressure oil, the left side oil pocket of a constant volume hydraulic oil admission velocity compensator piston, as oil-feed lateral pressure oil pressure p ﹥ 4k (S
0+ s)/π d
2time, piston 4 will move to right side terminal, the compensation volume △ V=π * d that left side oil pocket enters
2s/4.In formula, k represents the rigidity of retracing spring 6, S
0represent the rear initial compression amount of retracing spring 6 assembling, d represents the diameter of hydraulic braking velocity compensator piston 4, and s represents the range of piston.
If passive type hydraulic brake Hydraulic System Oil pump discharge pressure is p, during drg braking, disc brake spring discharges corresponding oil pressure p completely
z, the service conditions that velocity compensator is effectively necessary is the maximum working pressure (MWP) p of velocity compensator
nmax< p
z, and the minimum working pressure power p of velocity compensator
nmin>3MPa, velocity compensator can suck quantitative energy fast from passive type hydraulic brake when guaranteeing to brake, and can in the short period of time absorbed energy be discharged to oil sump tank through overdamping after end of braking.Conventionally p is 14MPa left and right, p
zat 9MPa～11MPa left and right, p
noperating range can be between 3MPa～7MPa.
Therefore after diameter of piston d determines, the rigidity k of retracing spring is the key of assurance velocity compensator operation pressure, such as in 3MPa～7MPa scope.The length that changes stroke pin can change the volume of compensation.
The invention has the beneficial effects as follows:
1. hydraulic efficiency pressure system can effectively shorten braking time, improves safety, reliability;
2. velocity compensator is simple in structure, is convenient to install applied range;
3. velocity compensator compensation capacity is quantitatively controlled, and change capacity is very convenient;
4. velocity compensator housing and end cap are applicable to adopting cast steel, are convenient to seriation and batch manufacturing;
5. velocity compensator retracing spring guiding is controlled, and serviceability is not subject to the impact of ambient temperature;
6. the product reformation of velocity compensator in easy to use, without electrical control;
7. velocity compensator takes into full account oil draining function, and flexible movements are reliable;
8. velocity compensator sealing adopts low temperature material, and existence temperature-45 ℃～120 ℃, are used
Temperature-30 ℃～100 ℃.
Accompanying drawing explanation
The present invention has four width accompanying drawings.Wherein:
Fig. 1 is the hydraulic efficiency pressure system schematic diagram of the passive type hydraulic brake of tape speed compensator
Fig. 2 is the structural representation of velocity compensator
Fig. 3 is the velocity compensator structural representation of the outer guiding of retracing spring
Fig. 4 is the velocity compensator structural representation of guiding in retracing spring
Drawing reference numeral is described as follows:
1. housing 2. seal ring 3. Combined seal ring of piston 4. piston 5. stroke pin 6. retracing spring 7. end cap seal circle 8. end cap 9. passive type hydraulic brake 10. oil pump 11. braking electromagnetic valve 12. dampings 13. electromagnetic valve 14. fuel tank 15. energy storage 16. hydraulic braking velocity compensator 17. manual pump 18. safety valve 19. orienting sleeves that boost
The specific embodiment
Below in conjunction with the embodiment of accompanying drawing, the invention will be further described.
The passive type hydraulic brake hydraulic efficiency pressure system of tape speed compensator, comprises passive type hydraulic brake hydraulic efficiency pressure system, and passive type hydraulic brake hydraulic efficiency pressure system is by the passive type hydraulic brake 9 connecting with pipeline, oil pump 10, braking electromagnetic valve 11, damping 12, electromagnetic valve 13 boosts, fuel tank 14, energy storage 15, the compositions such as manual pump 17 and safety valve 18, the import and export of passive type hydraulic brake 9 by pipeline successively with braking electromagnetic valve 11, damping 12 serial connection and and fuel tank 14 be communicated with, in the import of damping 12 with between exporting, be connected to a branch road, the oil suction of oil pump 10 is communicated with fuel tank 14, the outlet of oil pump 10 respectively with safety valve 18, energy storage 15, electromagnetic valve 13 boosts, the import of manual pump 17 and passive type hydraulic brake 9 is communicated with, velocity compensator 16 is connected on the branch road between damping 12 imports and outlet, velocity compensator 16 is piston-type hydraulic cylinders of piston-rodless, one side chamber of piston-type hydraulic cylinder piston is communicated with damping 12 inlet ductwork, retracing spring 6 is housed in opposite side chamber, and the chamber that retracing spring is housed is communicated with damping 12 export pipelines.
Velocity compensator comprises the piston-type hydraulic cylinder being comprised of housing 1, Combined seal ring of piston 3, piston 4, retracing spring 6, end cap seal circle 7 and end cap 8, housing 1 is tubular, and bottom centre position place has the communication port being connected with passive type hydraulic brake hydraulic efficiency pressure system damping 12 inlet ductwork; The inner centre of end cap 8 is with axle shape platform, the centre hole that connects two ends is opened in axle shape platform centre, the mouth of centre hole end cap outside is the communication port being connected with passive type hydraulic brake hydraulic efficiency pressure system damping 12 export pipelines, end cap 8 is sealedly connected on housing 1 open end, on the interior axle shape of end cap 8 platform, have draining mechanism, draining mechanism on axle shape platform is draining hole or drain pan, and draining hole or drain pan communicate with the axle shape platform centre hole of axle; Piston 4 is not with piston rod, piston 4 is arranged in housing by Combined seal ring of piston 3, and the reference position that piston is installed is in the bottom of housing, and retracing spring 6 is arranged in the housing between piston 4 and end cap 8, retracing spring 6 one end and piston connect, and the other end and end cap connect.
Embodiment 1 is the embodiment that velocity compensator adopts the dish-shaped retracing spring of outer guiding.As shown in Figure 3.Retracing spring 6 is belleville spring, and the excircle of retracing spring 6 and inner walls keep
alwaysgap is 0.8mm～1.0mm, by the clearance control realization of inner walls and retracing spring excircle, retracing spring is led.Piston 4 is provided with stroke pin 5, stroke pin 5 centers have the hole that connects both ends of the surface, stroke pin 5 external diameters are identical with axle shape platform external diameter in end cap, stroke pin 5 is fixedly mounted on piston 4 and connects in the pin-and-hole of face center with retracing spring 6, in end face and end cap, between axle shape you face, distance is s, 0 < s≤p
n* π * d
2/ 4k-S
0, p in formula
nfor velocity compensator overcomes the operation pressure that spring stiffness produces action, p
noperating range can be between 3MPa～7MPa, and d is piston 4 diameters, and k is the rigidity of retracing spring 6, S
0for initial compression amount after retracing spring 6 assemblings.As the braking oil pressure p of passive type hydraulic brake value >p
ntime, velocity compensator can complete compensation to greatest extent.
Embodiment 2 is embodiment of the dish-shaped retracing spring of guiding in velocity compensator adopts.As shown in Figure 4.Piston is provided with the stroke pin identical with embodiment 1.In end cap, on axle shape platform, orienting sleeve 19 is housed, orienting sleeve 19 is sleeved on the interior axle shape of end cap 8 platform, orienting sleeve 19 front ends stretch in the stroke pin pin-and-hole of piston 4, orienting sleeve inner circle is sleeved on stroke pin 5, orienting sleeve 19 aft end faces abut against on end cap 8, have s distance 0 < s≤p between the stroke pin pin-and-hole bottom surface of front end face and piston
n* π * d
2/ 4k-S
0, p in formula
nfor velocity compensator overcomes the operation pressure that spring stiffness produces action, p
noperating range can be between 3MPa～7MPa, and d is piston 4 diameters, and k is the rigidity of retracing spring 6, S
0for initial compression amount after retracing spring 6 assemblings, retracing spring is arranged in the housing between piston and end cap, retracing spring one end and piston connect, the other end and end cap connect, retracing spring 6 is placed in outside orienting sleeve 19, retracing spring 6 is disk springs, and the inner periphery of retracing spring and orienting sleeve excircle keep
alwaysgap is 0.5mm～0.6mm, by the clearance control realization of orienting sleeve excircle and retracing spring inner periphery, retracing spring is led.As the braking oil pressure p of passive type hydraulic brake value >p
ntime, velocity compensator can complete compensation to greatest extent.
Claims (8)
1. the passive type hydraulic brake hydraulic efficiency pressure system of a tape speed compensator, comprise passive type hydraulic brake hydraulic efficiency pressure system, passive type hydraulic brake hydraulic efficiency pressure system is by the passive type hydraulic brake (9) connecting with pipeline, oil pump (10), braking electromagnetic valve (11), damping (12), electromagnetic valve (13) boosts, fuel tank (14), energy storage (15), manual pump (17) and safety valve (18) form, the import and export P1 of passive type hydraulic brake (9) and leakage hydraulic fluid port T are communicated with system circuit and fuel tank (14) respectively by pipeline, on the pipeline being communicated with fuel tank (14) at the import and export P1 of passive type hydraulic brake (9), be serially connected with damping (12) and braking electromagnetic valve (11), between the import of damping (12) and outlet, be connected to a branch road, the oil suction of oil pump (10) is communicated with fuel tank (14), the outlet of oil pump (10) respectively with safety valve (18), energy storage (15), electromagnetic valve (13) boosts, the import and export P1 of manual pump (17) and passive type hydraulic brake (9) is communicated with, the passive type hydraulic brake hydraulic efficiency pressure system that it is characterized in that described tape speed compensator also comprises velocity compensator (16), velocity compensator (16) is connected on the branch road between damping (12) import and outlet, described velocity compensator (16) is the piston-type hydraulic cylinder of piston-rodless, one side chamber of piston-type hydraulic cylinder piston is communicated with damping (12) inlet ductwork, retracing spring (6) is housed in opposite side chamber, the chamber that retracing spring is housed is communicated with damping (12) export pipeline.
2. the velocity compensator for the passive type hydraulic brake hydraulic efficiency pressure system of a kind of tape speed compensator described in claim 1, comprise the piston-type hydraulic cylinder being formed by housing (1), Combined seal ring of piston (3), piston (4), retracing spring (6), end cap seal circle (7) and end cap (8), it is characterized in that described housing (1) is tubular, bottom centre position place has the communication port being connected with passive type hydraulic brake hydraulic efficiency pressure system damping (12) inlet ductwork; The inner centre of described end cap (8) is with axle shape platform, the centre hole that connects two ends is opened in axle shape platform centre, the mouth of centre hole end cap outside is the communication port being connected with passive type hydraulic brake hydraulic efficiency pressure system damping (12) export pipeline, end cap (8) is sealedly connected on housing (1) open end, on the interior axle shape of end cap (8) platform, has draining mechanism; Described piston (4) is not with piston rod, piston (4) is arranged in housing by Combined seal ring of piston (3), the reference position that piston is installed is in the bottom of housing, described retracing spring (6) is arranged in the housing between piston (4) and end cap (8), retracing spring (6) one end and piston connect, and the other end and end cap connect.
3. according to claim 2 for the velocity compensator of the passive type hydraulic brake hydraulic efficiency pressure system of tape speed compensator, it is characterized in that described piston (4) is provided with stroke pin (5), described stroke pin (5) center has endoporus and the assembling screw that connects both ends of the surface, the endoporus of the external diameter of stroke pin (5) and piston (4) is fixed on piston (4) stroke pin (5) with interference fit, between stroke pin (5) outside end face and the inner axle shape of end cap (8) you face, distance is s, 0 < s≤p
n* π * d
2/ 4k-S
0, p in formula
nfor velocity compensator overcomes the operation pressure that spring stiffness produces action, d is piston (4) diameter, and k is the rigidity of retracing spring (6), S
0for initial compression amount after retracing spring (6) assembling, the volume that the corresponding volume of s and piston (4) area will compensate while being braking.
4. according to claim 3 for the velocity compensator of the passive type hydraulic brake hydraulic efficiency pressure system of tape speed compensator, the guidance mode that it is characterized in that described retracing spring (6) is outer guiding or interior guiding, described outer guiding is that total backlash is 0.8mm～1.0mm between the excircle of retracing spring (6) and housing (1) inwall, and retracing spring excircle is led by inner walls; Described interior guiding is on axle shape platform, orienting sleeve (19) to be housed in end cap, orienting sleeve (19) is sleeved on the interior axle shape of end cap (8) platform, orienting sleeve (19) front end stretches in the stroke pin pin-and-hole of piston (4), orienting sleeve inner circle is sleeved on stroke pin (5), orienting sleeve (19) aft end face abuts against on end cap (8), between the stroke pin pin-and-hole bottom surface of front end face and piston, there is s distance, 0 < s≤p
n* π * d
2/ 4k-S
0, p in formula
nfor velocity compensator overcomes the operation pressure that spring stiffness produces action, d is piston (4) diameter, and k is the rigidity of retracing spring (6), S
0for initial compression amount after retracing spring (6) assembling, retracing spring (6) is placed in outside orienting sleeve (19), between the inner periphery of retracing spring (6) and orienting sleeve (19) excircle, total backlash is 0.5mm～0.6mm, by retracing spring inner periphery and orienting sleeve excircle, is led.
5. according to claim 3 for the velocity compensator of the passive type hydraulic brake hydraulic efficiency pressure system of tape speed compensator, it is characterized in that the maximum working pressure (MWP) p of described velocity compensator
nmax< p
z, the minimum working pressure power p of velocity compensator
nmin>3MPa, wherein p
zwhile braking for drg, disc brake spring discharges corresponding oil pressure completely.
6. according to claim 5 for the velocity compensator of the passive type hydraulic brake hydraulic efficiency pressure system of tape speed compensator, while it is characterized in that described drg braking, disc brake spring discharges corresponding oil pressure p completely
zbetween 9MPa～11MPa, velocity compensator overcomes the operation pressure p that spring stiffness produces action
nbetween 3MPa～7MPa.
7. according to claim 2 for the velocity compensator of the passive type hydraulic brake hydraulic efficiency pressure system of tape speed compensator, it is characterized in that the draining mechanism on the interior axle shape of described end cap (8) platform is draining hole or drain pan, draining hole or drain pan communicate with the axle shape platform centre hole of axle.
8. according to claim 2 for the velocity compensator of the passive type hydraulic brake hydraulic efficiency pressure system of tape speed compensator, it is characterized in that described retracing spring (6) is disk spring.
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|---|---|---|---|
| CN201210514569.0A CN102963345B (en) | 2012-12-04 | 2012-12-04 | Driven hydraulic-brake hydraulic system with velocity compensator |
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|---|---|---|---|
| CN201210514569.0A CN102963345B (en) | 2012-12-04 | 2012-12-04 | Driven hydraulic-brake hydraulic system with velocity compensator |
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| CN102963345B true CN102963345B (en) | 2014-10-01 |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN103174834A (en) * | 2013-04-10 | 2013-06-26 | 玉林市川迪机器制造有限公司 | Sealing device of excavator tension track oil cylinder |
| CN104006024A (en) * | 2014-06-12 | 2014-08-27 | 苏州劳灵精密机械有限公司 | Single-action tension cylinder |
| CN107192540A (en) * | 2016-03-15 | 2017-09-22 | 北京强度环境研究所 | Band net compensator pipe-line system stiffness characteristics experimental rig |
| DE102017117422A1 (en) * | 2017-08-01 | 2019-02-07 | Knorr-Bremse Systeme für Schienenfahrzeuge GmbH | Passive memoryless hydraulic brake system |
| CN111169454B (en) * | 2018-11-13 | 2021-07-20 | 宝沃汽车（中国）有限公司 | Vehicle braking assisting method and device, controller and vehicle |
| CN113389829B (en) * | 2021-06-10 | 2022-09-30 | 徐州徐工矿业机械有限公司 | Mining dump truck and brake automatic compensator, brake and braking method thereof |
| CN115143213B (en) * | 2022-06-17 | 2023-06-23 | 中航西安飞机工业集团股份有限公司 | Pollution isolation device and pollution isolation method for hydraulic brake system |
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| US3751919A (en) * | 1970-05-04 | 1973-08-14 | Shiber Samuel | Hydraulic power brake booster motor |
| US3785393A (en) * | 1971-05-07 | 1974-01-15 | Dba Sa | Fluid power braking and steering system |
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