CN202944328U - Hydraulic system with speed compensator of passive hydraulic brake - Google Patents
Hydraulic system with speed compensator of passive hydraulic brake Download PDFInfo
- Publication number
- CN202944328U CN202944328U CN 201220660377 CN201220660377U CN202944328U CN 202944328 U CN202944328 U CN 202944328U CN 201220660377 CN201220660377 CN 201220660377 CN 201220660377 U CN201220660377 U CN 201220660377U CN 202944328 U CN202944328 U CN 202944328U
- Authority
- CN
- China
- Prior art keywords
- piston
- type hydraulic
- compensator
- passive type
- retracing spring
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Withdrawn - After Issue
Links
Images
Landscapes
- Braking Arrangements (AREA)
Abstract
A hydraulic system with a speed compensator of a passive hydraulic brake comprises the hydraulic system of the passive hydraulic brake, and is characterized in that the speed compensator is connected to a branch between a braking return oil damping inlet and outlet, and is a piston type hydraulic cylinder without a piston rod; one side cavity of the piston type hydraulic cylinder is communicated with a damping inlet pipeline, and a return spring is arranged in the other side cavity; and the side cavity with the return spring is communicated with a damping outlet pipeline. The hydraulic system has the benefits that the hydraulic system can efficiently shorten braking time, and improve safety and reliability; the speed compensator is simple in structure, and facilitates production in series and in batch; the installation is convenient, and the motion is flexible and reliable; the compensation capacity of the speed compensator is quantitatively controlled, so that the change of the capacity is very convenient; and the working performance is free from the influence of environmental temperature.
Description
Technical field
The utility model belongs to control device for hydraulic brake, is 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, in each braking procedure, hydraulic actuator piston needs one section 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 be completed a total stopping distance △ S under the effect of disk spring, it comprises that out of control in the braking response process sends from the operator distance that braking maneuver instruction to drg begins to produce mechanism's operation in this one-phase of lock torque apart from △ S1() 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 compositions: 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 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, a kind of velocity compensator of invention becomes with the safe reliability that improves braking the technical barrier that needs to be resolved hurrily.
Summary of the invention
The purpose of this utility model is a kind of velocity compensator of invention, reduces the mechanical response time in passive type hydraulic brake brake process, thereby reduces braking time, improves safety, reliability and the stationarity of drg work.
the technical solution of the utility model 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, be serially connected with damping and braking electromagnetic valve on the import and export P1 of passive type hydraulic brake and pipeline that fuel tank is communicated with, be connected to a branch road between the import of damping and outlet, 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, 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 described in the utility model, 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 in end cap on axle shape platform; 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 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 the tape speed compensator described in the utility model, 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 piston the stroke pin with interference fit, between stroke pin outside end face and the inner axle shape of 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, 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 described in the utility model, 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 axle shape platform, orienting sleeve to be housed in 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 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 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 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 guiding.
The velocity compensator of the passive type hydraulic brake hydraulic efficiency pressure system for the tape speed compensator described in the utility model 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
zWhen braking for drg, the disc brake spring discharges corresponding oil pressure fully.
The velocity compensator of the passive type hydraulic brake hydraulic efficiency pressure system for the tape speed compensator described in the utility model, when it is characterized in that described drg braking, the disc brake spring discharges corresponding oil pressure p fully
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 described in the utility model, it is characterized in that in described end cap that the draining mechanism on axle shape platform is draining hole or drain pan, 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 described in the utility model is characterized in that described retracing spring is disk spring.
Principle of work of the present utility model 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 the compensation capacity △ V of a part, pushing piston moves right, compression reseting spring compresses the s distance to the right, compensation capacity △ V=π * d
2S/4.When drg was completed braking, the hydraulic fluid pressure of plunger shaft descended gradually by damping, and pressure drop to regularly, compressed retracing spring pushing piston gradually 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 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, after the velocity compensator piston is completed 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 * Dw* △ S1/4 that during the drg braking, hydraulic oil discharges, compensation capacity is got △ V=V*2/3 left and right, all the other V*1/3 consider normally to pass through the damping hole part, and leave certain surplus.△ V=π * d like this
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.In formula, k represents the rigidity of retracing spring 6, S
0Represent the retracing spring 6 rear initial compression amounts of 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 the drg braking, the disc brake spring discharges corresponding oil pressure p fully
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
Nmin3MPa, during with the assurance braking, velocity compensator can suck quantitative energy fast 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 the 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 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 beneficial effects of the utility model are:
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. 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 is controlled, and 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 utility model 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
The utility model is described in further detail below in conjunction with the embodiment of accompanying drawing.
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 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 serial connection and and fuel tank 14 be communicated with, be connected to a branch road in the import of damping 12 with between exporting, 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; 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 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 interior axle shape of end cap 8 platform, 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 housing between piston 4 and 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 it is 0.8mm～1.0mm that the excircle of retracing spring 6 and inner walls keep total backlash, 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, between the interior axle shape you face of end face and end cap, 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
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 completed 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.On axle shape platform, orienting sleeve 19 is housed in end cap, 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, the orienting sleeve inner circle is sleeved on stroke pin 5, orienting sleeve 19 aft end faces abut against on 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 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 arranged in 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 it is 0.5mm～0.6mm that the inner periphery of retracing spring and orienting sleeve excircle keep total backlash, 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 completed 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) 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, be serially connected with damping (12) and braking electromagnetic valve (11) on the import and export P1 of passive type hydraulic brake (9) and pipeline that fuel tank (14) is communicated with, be connected to a branch road between the import of damping (12) and outlet, 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, 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 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 housing between piston (4) and end cap (8), retracing spring (6) one ends and piston connect, and the other end and end cap connect.
3. be used for according to claim 2 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) makes the stroke pin with interference fit, and (5 are fixed on piston (4), 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
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. be used for according to claim 3 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 namely the 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), the orienting sleeve inner circle is sleeved on stroke pin (5), orienting sleeve (19) aft end face abuts against on 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 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) 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 guiding.
5. be used for according to claim 3 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
zWhen braking for drg, the disc brake spring discharges corresponding oil pressure fully.
6. be used for according to claim 5 the velocity compensator of the passive type hydraulic brake hydraulic efficiency pressure system of tape speed compensator, when it is characterized in that described drg braking, the disc brake spring discharges corresponding oil pressure p fully
zBetween 9MPa～11MPa, velocity compensator overcomes the operation pressure p that spring stiffness produces action
nBetween 3MPa～7MPa.
7. be used for according to claim 2 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. be used for according to claim 2 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.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201220660377 CN202944328U (en) | 2012-12-04 | 2012-12-04 | Hydraulic system with speed compensator of passive hydraulic brake |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201220660377 CN202944328U (en) | 2012-12-04 | 2012-12-04 | Hydraulic system with speed compensator of passive hydraulic brake |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN202944328U true CN202944328U (en) | 2013-05-22 |
Family
ID=48420041
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201220660377 Withdrawn - After Issue CN202944328U (en) | 2012-12-04 | 2012-12-04 | Hydraulic system with speed compensator of passive hydraulic brake |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN202944328U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102963345A (en) * | 2012-12-04 | 2013-03-13 | 大连华锐重工集团股份有限公司 | Driven hydraulic-brake hydraulic system with velocity compensator |
-
2012
- 2012-12-04 CN CN 201220660377 patent/CN202944328U/en not_active Withdrawn - After Issue
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102963345A (en) * | 2012-12-04 | 2013-03-13 | 大连华锐重工集团股份有限公司 | Driven hydraulic-brake hydraulic system with velocity compensator |
| CN102963345B (en) * | 2012-12-04 | 2014-10-01 | 大连华锐重工集团股份有限公司 | Driven hydraulic-brake hydraulic system with velocity compensator |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN102963345B (en) | Driven hydraulic-brake hydraulic system with velocity compensator | |
| CN103016934B (en) | Wind-powered lubrication system with pressure buffer | |
| CN113251013B (en) | Electro-hydraulic direct-drive servo closed differential control driving system of stepping lifting mechanism | |
| CN202040145U (en) | Multistage locking cylinder | |
| CN202944328U (en) | Hydraulic system with speed compensator of passive hydraulic brake | |
| CN102003919B (en) | Novel gas-liquid mixed power ejection device | |
| CN212657061U (en) | Water inlet and outlet valve control device of hydraulic dynamometer | |
| CN115853931B (en) | Speed limiting braking control system with adjustable speed limiting value | |
| CN202716864U (en) | Integrated hydraulic unit of automobile braking system | |
| CN109501339B (en) | Hydraulic control system for pressurized oil cylinder of double-layer tire vulcanizer | |
| CN102536924A (en) | Single-hydraulic cylinder single-acting hydraulic system of supercharger | |
| CN203099280U (en) | Wind power lubricating system | |
| CN203926236U (en) | Single pump dual-speed hydraulic system | |
| CN201190704Y (en) | Inside and outside double-drum type hydraulic reinforcement cylinder | |
| CN110578732A (en) | Energy storage type hydraulic cylinder with built-in welded piston rod | |
| CN206290519U (en) | Retractable actuating cylinder hydraulic circuit components | |
| CN202732803U (en) | Spring reset type water turbine oil brake | |
| CN204381151U (en) | Press air cushion jack-up energy manufactures blowing plant | |
| CN201836130U (en) | Energy storage quick release device | |
| CN204822064U (en) | Take aircraft parking brake switch structure of temperature compensating function | |
| CN205154526U (en) | Reciprocating type high pressure water pump of double -cylinder | |
| CN205001264U (en) | High pressure air spring | |
| CN202779687U (en) | Rapid pressurizing injection device of hydraulic machine | |
| CN113062939A (en) | Electro-hydraulic supply device for brake system of unmanned aerial vehicle | |
| CN101968066A (en) | Energy storage rapid discharger |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20130522 Effective date of abandoning: 20141001 |
|
| RGAV | Abandon patent right to avoid regrant |