CN102963345A - Driven hydraulic-brake hydraulic system with velocity compensator - Google Patents
Driven hydraulic-brake hydraulic system with velocity compensator Download PDFInfo
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- CN102963345A CN102963345A CN2012105145690A CN201210514569A CN102963345A CN 102963345 A CN102963345 A CN 102963345A CN 2012105145690 A CN2012105145690 A CN 2012105145690A CN 201210514569 A CN201210514569 A CN 201210514569A CN 102963345 A CN102963345 A CN 102963345A
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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 keep certain interval, hydraulic actuator piston needs one section invalid stroke of many operations in each braking procedure, eliminate these gaps and prolonged 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 be finished a total stopping distance △ S under the effect of disk spring, it comprises that out of control in the braking response process sends the distance that braking maneuver instruction to drg begins to produce mechanism's operation in this one-phase of lock torque apart from △ S1(from the operator) and braking deceleration begin to apply lock torque to the distance of this one-phase of kinematic mechanism stop motion apart from △ S2(drg).And braking time t mainly contains 3 parts composition: electrical response t delay time
Ea: send the braking maneuver instruction to drg drive control valve dead electricity and time of beginning to move from the operator; Mechanical response t delay time
Ma: after the drg drive control valve dead electricity, drg begins to move the time that begins to produce lock torque to drg; Braking deceleration time t
b: drg begins 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
bTraditional passive type hydraulic brake does not have the 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 the technical barrier that needs to be resolved hurrily with the safe reliability that improves braking.
Summary of the invention
The objective of the invention is to invent a kind of velocity compensator, reduce the mechanical response time in the 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 that connects 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, the pipeline that is communicated with fuel tank at the import and export P1 of passive type hydraulic brake is 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, the outlet of oil 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 fuel tank with connecting pipeline by braking electromagnetic valve and damping, 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 be connected to the damping import and the outlet between branch road on, described velocity compensator is the piston-type hydraulic cylinder of piston-rodless, one side chamber of piston-type hydraulic cylinder piston is communicated with the damping inlet ductwork, opposite side is equipped with retracing spring in the chamber, and the chamber that retracing spring is housed is communicated with the 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 that is 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, the bottom centre position place has the communication port that is 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 that is connected with passive type hydraulic brake hydraulic efficiency pressure system damping export pipeline, end cap seal is connected to the shell nozzle end, has draining mechanism on the axle shape platform in the end cap; Described piston is not with piston rod, piston is installed in the 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 installed in the housing between piston and the 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 the tape speed compensator of the present invention, it is characterized in that described piston is provided with the 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 the piston stroke pin with interference fit, distance is s between stroke pin outside end face and the inner axle shape of the end cap you face, 0＜s≤p
n* π * d
2/ 4k-S
0, p in the formula
nFor velocity compensator overcomes the operation pressure that spring stiffness produces action, d is diameter of piston, and k is the rigidity of retracing spring, S
0Be initial compression amount after the retracing spring assembling, the volume that the corresponding volume of s and piston area will compensate when being braking.
The velocity compensator of the passive type hydraulic brake hydraulic efficiency pressure system for the 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 namely the retracing spring excircle is led by inner walls; Described interior guiding is on the axle shape platform orienting sleeve to be housed in the end cap, orienting sleeve is sleeved on the interior axle shape platform of end cap, the orienting sleeve front end stretches in the stroke pin pin-and-hole of piston, the orienting sleeve inner circle is sleeved on the stroke pin, the orienting sleeve aft end face abuts against on the end cap, the s distance is arranged, 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 the formula
nFor velocity compensator overcomes the operation pressure that spring stiffness produces action, d is diameter of piston, and k is the rigidity of retracing spring, S
0Be initial compression amount after the retracing spring assembling, retracing spring places outside the orienting sleeve, and total backlash is 0.5mm～0.6mm between the inner periphery of retracing spring and the orienting sleeve excircle, by retracing spring inner periphery and orienting sleeve excircle guiding.
The velocity compensator of the passive type hydraulic brake hydraulic efficiency pressure system for the 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
Nmin3MPa, wherein p
zThe disc brake spring discharges corresponding oil pressure fully when braking for drg.
The velocity compensator of the passive type hydraulic brake hydraulic efficiency pressure system for the tape speed compensator of the present invention, the disc brake spring discharges corresponding oil pressure p fully when it is characterized in that described drg braking
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 the tape speed compensator of the present invention is characterized in that the draining mechanism on the axle shape platform is draining hole or drain pan in the described end cap, 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 the 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, because 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 rapidly admission velocity compensator of the compensation capacity △ V of a part, pushing piston moves right, compression reseting spring compresses the s distance to the right, then compensation capacity △ V=π * d
2S/4.When drg was finished braking, the hydraulic fluid pressure of plunger shaft descended gradually by damping, and pressure drop to regularly, compressed retracing spring gradually pushing piston resets, this part hydraulic oil of compensation capacity △ V is expelled back into fuel tank, returns to the initial position, wait for next brake operating.
In this course, velocity compensator rapid compensation capacity of △ V in the absorption brake in the short time after drg receives braking instruction, thereby improve drg running under braking speed, finish as early as possible out of control apart from △ S1, after the velocity compensator piston is finished stroke s, after namely having absorbed the hydraulic oil of compensation capacity △ V, the drg retro-speed returns to the speed of being controlled by damping substantially fully, like this actv. is shortened 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 hydraulic oil discharges during the drg braking
2* △ S1/4, compensation capacity is got about △ V=V*2/3, and all the other V*1/3 consider normally by the damping hole part, and leave certain surplus.Such △ V=π * d
2S/4=(2* π * D
2* △ S1)/(3*4), can get 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
2The time, 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 is as oil-feed lateral pressure oil pressure p ﹥ 4k(S
0+ s)/π d
2The time, piston 4 will move to the right side terminal, the compensation volume △ V=π * d that the left side oil pocket enters
2S/4.K represents the rigidity of retracing spring 6, S in the formula
0Represent the rear initial compression amount of retracing spring 6 assemblings, 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, the disc brake spring discharges corresponding oil pressure p fully during the drg braking
z, the service conditions that then 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
Nmin3MPa, velocity compensator can suck quantitative energy fast during with the assurance braking from the passive type hydraulic brake, and can in the short period of time the energy that absorbs be discharged oil sump tank through overdamping after end of braking.Usually p is about 14MPa, p
zAbout 9MPa～11MPa, p then
nOperating range can be between 3MPa～7MPa.
Therefore after diameter of piston d determined, the rigidity k of retracing spring was the key of assurance velocity compensator operation pressure, such as in 3MPa～7MPa scope.The length that changes the 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 applied range is installed;
3. the velocity compensator compensation capacity is quantitatively controlled, and the change capacity is very convenient;
4. velocity compensator housing and end cap are fit to adopt cast steel, are convenient to seriation and batch manufacturing;
5. velocity compensator retracing spring guiding control, serviceability is not subjected to the impact of ambient temperature;
6. the product reformation of velocity compensator in easy to use need not electrical control;
7. velocity compensator takes into full account oil draining function, and flexible movements are reliable;
8. low temperature material is adopted in velocity compensator sealing, existence temperature-45 ℃～120 ℃, serviceability temperature-30 ℃～100 ℃.
Description of drawings
The present invention has four width of cloth accompanying drawings.Wherein:
Fig. 1 is the hydraulic efficiency pressure system scheme drawing 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 the retracing spring
Drawing reference numeral is described as follows:
1. housing 2. seal rings 3. Combined seal ring of pistons 4. pistons 5. stroke pins 6. retracing springs 7. end cap seal circles 8. end caps 9. passive type hydraulic brakes 10. oil pumps 11. braking electromagnetic valves 12. dampings 13. electromagnetic valve 14. fuel tanks 15. energy storages 16. hydraulic braking velocity compensators 17. manual pumps 18. safety valves 19. orienting sleeves that boost
The specific embodiment
The invention will be further described below in conjunction with the embodiment of accompanying drawing.
The 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 9 that connects 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 is connected in series also and fuel tank 14 is communicated with, 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 of manual pump 17 and passive type hydraulic brake 9 is communicated with, velocity compensator 16 be connected to damping 12 imports and the outlet between branch road on, 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 the 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 that is 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 the bottom centre position place has the communication port that is connected with passive type hydraulic brake hydraulic efficiency pressure system damping 12 inlet ductwork; End cap 8 inner centres are 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 that is 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, have draining mechanism on the end cap 8 interior axle shape platforms, draining mechanism on the 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 installed in the 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 installed in the housing between piston 4 and the end cap 8, retracing spring 6 one ends 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
AlwaysThe gap 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 the 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, distance is s between the interior axle shape you face of end face and end cap, 0＜s≤p
n* π * d
2/ 4k-S
0, p in the 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
0Be initial compression amount after retracing spring 6 assemblings.When the braking oil pressure p of passive type hydraulic brake value〉p
nThe time, velocity compensator can be finished to greatest extent compensation.
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.On the axle shape platform orienting sleeve 19 is housed in the end cap, orienting sleeve 19 is sleeved on the end cap 8 interior axle shape platforms, orienting sleeve 19 front ends stretch in the stroke pin pin-and-hole of piston 4, the orienting sleeve inner circle is sleeved on the stroke pin 5, orienting sleeve 19 aft end faces abut against on the end cap 8, and s distance 0＜s≤p is arranged between the stroke pin pin-and-hole bottom surface of front end face and piston
n* π * d
2/ 4k-S
0, p in the 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
0Be initial compression amount after retracing spring 6 assemblings, retracing spring is installed in the housing between piston and the end cap, retracing spring one end and piston connect, the other end and end cap connect, retracing spring 6 places outside the orienting sleeve 19, retracing spring 6 is disk springs, and the inner periphery of retracing spring and orienting sleeve excircle keep
AlwaysThe gap is 0.5mm～0.6mm, by the clearance control realization of orienting sleeve excircle and retracing spring inner periphery retracing spring is led.When the braking oil pressure p of passive type hydraulic brake value〉p
nThe time, velocity compensator can be finished to greatest extent compensation.
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) that connects 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, the pipeline that is communicated with fuel tank (14) at the import and export P1 of passive type hydraulic brake (9) is 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 fuel tank (14) with connecting pipeline by braking electromagnetic valve (11) and damping (12), 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) be connected to damping (12) import and the outlet between branch road on, 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 the opposite side chamber, and the chamber that retracing spring is housed is communicated with damping (12) export pipeline.
2. velocity compensator that is used for the passive type hydraulic brake hydraulic efficiency pressure system of the described a kind of tape speed compensator of claim 1, comprise the piston-type hydraulic cylinder that is 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, the bottom centre position place has the communication port that is 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 that is 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, has draining mechanism on the interior axle shape of end cap (8) platform; Described piston (4) is not with piston rod, piston (4) is installed in the 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 installed in the housing between piston (4) and the end cap (8), retracing spring (6) one ends and piston connect, and the other end and end cap connect.
3. the velocity compensator of described passive type hydraulic brake hydraulic efficiency pressure system for the tape speed compensator according to claim 2, 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 the piston (4) stroke pin (5) with interference fit, distance is s between stroke pin (5) outside end face and the inner axle shape of end cap (8) the you face, 0＜s≤p
n* π * d
2/ 4k-S
0, p in the 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
0Be initial compression amount after retracing spring (6) assembling, the volume that the corresponding volume of s and piston (4) area will compensate when being braking.
4. the velocity compensator of described passive type hydraulic brake hydraulic efficiency pressure system for the tape speed compensator according to claim 3, 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 namely the retracing spring excircle is led by inner walls; Described interior guiding is on the axle shape platform orienting sleeve (19) to be housed in the 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), the orienting sleeve inner circle is sleeved on the stroke pin (5), orienting sleeve (19) aft end face abuts against on the end cap (8), the s distance is arranged, 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 the 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
0Be initial compression amount after retracing spring (6) assembling, retracing spring (6) places outside the orienting sleeve (19), total backlash is 0.5mm～0.6mm between the inner periphery of retracing spring (6) and orienting sleeve (19) excircle, by retracing spring inner periphery and orienting sleeve excircle guiding.
5. the velocity compensator of described passive type hydraulic brake hydraulic efficiency pressure system for the tape speed compensator according to claim 3 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
zThe disc brake spring discharges corresponding oil pressure fully when braking for drg.
6. the velocity compensator of described passive type hydraulic brake hydraulic efficiency pressure system for the tape speed compensator according to claim 5, the disc brake spring discharges corresponding oil pressure p fully when it is characterized in that described drg braking
zBetween 9MPa～11MPa, velocity compensator overcomes the operation pressure p that spring stiffness produces action
nBetween 3MPa～7MPa.
7. the velocity compensator of described passive type hydraulic brake hydraulic efficiency pressure system for the tape speed compensator according to claim 2, 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. the velocity compensator of described passive type hydraulic brake hydraulic efficiency pressure system for the tape speed compensator according to claim 2 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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|---|---|---|---|
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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 |
| CN110997432A (en) * | 2017-08-01 | 2020-04-10 | 克诺尔轨道车辆***有限公司 | Passive reservoir-free hydraulic brake system |
| CN111169454A (en) * | 2018-11-13 | 2020-05-19 | 宝沃汽车（中国）有限公司 | Vehicle braking assisting method and device, controller and vehicle |
| CN113389829A (en) * | 2021-06-10 | 2021-09-14 | 徐州徐工矿业机械有限公司 | Mining dump truck and brake automatic compensator, brake and braking method thereof |
| CN115143213A (en) * | 2022-06-17 | 2022-10-04 | 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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| 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 |
| CN110997432A (en) * | 2017-08-01 | 2020-04-10 | 克诺尔轨道车辆***有限公司 | Passive reservoir-free hydraulic brake system |
| CN110997432B (en) * | 2017-08-01 | 2023-03-28 | 克诺尔轨道车辆***有限公司 | Passive reservoir-free hydraulic brake system |
| CN111169454A (en) * | 2018-11-13 | 2020-05-19 | 宝沃汽车（中国）有限公司 | Vehicle braking assisting method and device, controller and vehicle |
| CN113389829A (en) * | 2021-06-10 | 2021-09-14 | 徐州徐工矿业机械有限公司 | Mining dump truck and brake automatic compensator, brake and braking method thereof |
| CN115143213A (en) * | 2022-06-17 | 2022-10-04 | 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 |
| 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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| CN102963345B (en) | 2014-10-01 |
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