CN101475130B - Hydraulic time-delay double-stage braking hoister hydraulic station - Google Patents
Hydraulic time-delay double-stage braking hoister hydraulic station Download PDFInfo
- Publication number
- CN101475130B CN101475130B CN2009101031256A CN200910103125A CN101475130B CN 101475130 B CN101475130 B CN 101475130B CN 2009101031256 A CN2009101031256 A CN 2009101031256A CN 200910103125 A CN200910103125 A CN 200910103125A CN 101475130 B CN101475130 B CN 101475130B
- Authority
- CN
- China
- Prior art keywords
- valve
- control valve
- hydraulic
- oil
- directional control
- 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.)
- Expired - Fee Related
Links
Images
Landscapes
- Fluid-Pressure Circuits (AREA)
Abstract
The invention relates to a hydraulic station for a hydraulic delay secondary braking hoister. An electric motor drives an oil pump, an oil passage of the oil pump is connected with a proportional relief valve, and an oil passage of the proportional relief valve is connected with a shuttle valve which is connected with a brake through a first electromagnetic reversing valve; an oil passage of the first electromagnetic reversing valve communicated with the brake is provided with a one-way throttle valve, and two ends of the one-way throttle valve are connected with a power accumulator and a hydraulically operated directional control valve respectively; two ends of a one-way speed control valve are connected with control oil ports of the relief valve and the hydraulically operated directional control valve respectively, and an oil passage of the one-way speed control valve is communicated with an oil passage of the shuttle valve; the relief valve is connected between the oil passage of the electromagnetic reversing valve communicated with the brake and the oil passage of the one-way speed control valve communicated with the electromagnetic reversing valve; and a common oil passage of the one-way speed control valve and the relief valve is connected with a second brake through a third electromagnetic reversing valve. The hydraulic station has simple adjustment to the primary braking pressure, eliminates pressure drop phenomenon when the primary braking oil pressure is delayed, and ensures the reliability of the secondary braking performance.
Description
Technical field
The present invention be more particularly directed to a kind of mine winch, harbour are finished the mine hoist safety braking with hydraulic technique with cable car, cableway etc. hydraulic time-delay double-stage braking hoister hydraulic station that is used for.
Background technology
Various liftings, Transport Machinery adopt hydraulic time-delay double-stage braking to finish usually.Hydraulic time-delay double-stage braking is one of important performance of various liftings, Transport Machinery, there is not two stage braking if wherein be used for the winch of various liftings, Transport Machinery, the winch of fast running then, when running into sudden power, all unexpected band-type brake brakes of drg can make the steel rope shake, and personnel are easy to be bruised in the winch, if the winch steel wire is broken, also can cause great safety misadventure.At present, the gig Hydraulic Station has electrical delay two stage braking and two kinds of forms of hydraulic time-delay double-stage braking.Wherein, the electric control system complexity of electrical delay double-stage braking hoister hydraulic station has and uses inconvenient shortcoming; Hydraulic time-delay double-stage braking hoister hydraulic station has electrical control simple, debugging and advantage easy to maintenance.The working process of the one-level braking of the hydraulic time-delay double-stage braking hoister hydraulic station of producing as: Luoyang Mining Machinery Plant is: when the gig normal operation, its one-level brake circuit pressure is lower than system pressure (being generally 2-3Mpa); When gig had a power failure suddenly, the high pressure oil (being generally 5-6Mpa) of returning from drg joined through change-over valve and one-level brake circuit and realizes that one-level brakes.Yet the effect of the two stage braking of hydraulic time-delay double-stage braking hoister hydraulic station still can not reach perfect condition at present, mainly shows as: (1) one-level braking oil pressure descends bigger in in-service time; (2) owing to the one-level braking oil pressure is finished by reducing valve and by pass valve setting, and the by pass valve pressore setting is greater than reducing valve pressore setting 0.2-0.3Mpa, therefore the adjusting complexity of one-level braking oil pressure need be with reducing valve and by pass valve harmony mutually, and is higher to commissioning staff's technical requirements; (3) one-level braking oil pressure setting is less than 2.5Mpa the time, and its pressurize is relatively poor, causes delay time very short.Particularly the load when winch delivery is big, when the gradient that winch promotes is big, first class pressure need be transferred this moment to such an extent that be lower than 2.5Mpa, the energy storage oil reserve of Hydraulic Station seldom adds that the oil storage of internal system when operation also has leakage, the pressurize delay time of Hydraulic Station is very short, system does not have the one-level braking substantially, when running into sudden power, can make the unexpected band-type brake brake of drg equally, the steel rope shake produces safety misadventure.Therefore, hydraulic time-delay double-stage braking hoister hydraulic station has one-level brake-pressure instability, the shortcoming that the two stage braking performance is bad at present.
Summary of the invention
The purpose of this invention is to provide a kind of hydraulic time-delay double-stage braking hoister hydraulic station, described Hydraulic Station one-level brake-pressure is set up simple, eliminated the pressure decay phenomenon of one-level braking oil pressure during time-lag action, guaranteed the stability of two stage braking performance, two stage braking is more reliable.
Technical scheme of the present invention is: hydraulic time-delay double-stage braking hoister hydraulic station, by the motor-driven oil pump, connect proportional pressure control valve on the oil circuit of oil pump, and proportional pressure control valve is connected with first drg by shuttle valve, first solenoid directional control valve; The oil circuit that first solenoid directional control valve is communicated with drg is provided with one-way throttle valve, and an end of one-way throttle valve is connected with accumulator, and the other end is connected with hydraulicchange-over valve; One end of unidirectional governor valve is connected with by pass valve, and the oil circuit of the other end is communicated with the hydraulic fluid port of hydraulicchange-over valve control spool action; The oil circuit of unidirectional governor valve is communicated with the oil circuit of shuttle valve; By pass valve is connected between oil circuit that first solenoid directional control valve is communicated with first drg and unidirectional governor valve and the oil circuit that first solenoid directional control valve is communicated with; Described first solenoid directional control valve is connected in series by oil circuit with second solenoid directional control valve; Be connected with second drg by the 3rd solenoid directional control valve on the common oil circuit of described unidirectional governor valve and by pass valve; The 3rd solenoid directional control valve and the 4th solenoid directional control valve are by oil circuit and connect.
Connection of the present invention (leading to) all adopts oil circuit to be communicated with (except that being connected of motor and oil pump).
Hydraulic Station service braking of the present invention mainly is made up of the oil circuit that proportional pressure control valve, first, the 3rd solenoid directional control valve are formed, in normal operation, do not work in the hydraulic time-delay double-stage braking loop, when emergency episode (having a power failure or the outage etc. of breaking down of winch circuit) occurring, start safety arrestment, hydraulic pressure time-delay secondary safety arrestment loop works as unexpected full ore deposit.Therefore, two stage braking of the present invention is swift in response, stablizes, and can make the two stage braking performance of hydraulic time-delay double-stage braking hoister hydraulic station reach the ideal curve state, makes the two stage braking more reliable performance, also has debugging simpler, keeps in repair advantage more easily.Thereby improved the safety performance of mine winch, mine hoist, harbour cable car greatly.
Description of drawings
Fig. 1 is the structural representation of hydraulic time-delay double-stage braking hoister hydraulic station of the present invention;
Fig. 2 is one-level braking oil pressure delay time when identical, regulates by pass valve pressure, resulting different one-level brake-pressure diagram of curves;
Fig. 3 is one-level braking oil pressure when identical, regulates governor valve, the one-level brake-pressure diagram of curves of resulting different delayed time time;
Fig. 4 is the one-level braking oil pressure P of JB 3277-91 " mine hoist and mine lift winch Hydraulic Station " standard code and the diagram of curves of one-level braking oil pressure in-service time t.
Among Fig. 1,1 is coarse filter; 2 is motor; 3 is oil pump; 4 is proportional pressure control valve; 5 is fine filter; 6 is shuttle valve; 7 is unidirectional governor valve; 8 is hydraulicchange-over valve; 9 is by pass valve; 10 is one-way throttle valve; 11 is energy storage; 12,13,14,15 be respectively first, second, third, fourth solenoid directional control valve; 16 is first drg, and 17 is fuel tank, and 18 is second drg.
The specific embodiment
Referring to Fig. 1, hydraulic time-delay double-stage braking hoister hydraulic station of the present invention, motor 2 is electrically connected with oil pump, is used to drive oil pump 3, and the oil inlet end of oil pump connects oily coarse filter 1, is used to filter hydraulic oil.The oil outlet end of oil pump is connected with fine filter 5, further filters hydraulic oil, guarantees to enter the cleanliness level of whole Hydraulic Station hydraulic oil.Connect proportional pressure control valve 4 on the oil circuit of the oil outlet end of oil pump.Hydraulic Station is according to above-mentioned setting, by 2 motors, oil pump, thick fine filter, and proportional pressure control valve, and connect a shuttle valve 6 between on the common oil circuit of 2 proportional pressure control valves and oil pump oil outlet end and form the dual power source double control systems.Shuttle valve is connected with first drg 16 by first solenoid directional control valve 12; First solenoid directional control valve is provided with one-way throttle valve 10 with the oil circuit that first drg 16 is communicated with, one end of one-way throttle valve is connected with accumulator 11, the other end is connected with hydraulicchange-over valve 8, the feed circuit that one-way throttle valve and energy storage are formed directly is communicated with the first drg oil circuit, realizes the repairing voltage stabilizing function of one-level oil pressure.One end of unidirectional governor valve 7 is connected with by pass valve, and the oil circuit of the other end is communicated with the hydraulic fluid port of the control spool action of hydraulicchange-over valve 8, and the time regulating loop that described hydraulicchange-over valve, unidirectional governor valve are formed makes the one-level braking have the regulatory function of delay time.Unidirectional governor valve 7 also is communicated with first solenoid directional control valve, and the oil circuit of unidirectional governor valve 7 is communicated with the oil circuit of shuttle valve.By pass valve 9 is connected between oil circuit that first solenoid directional control valve 12 is communicated with first drg 16 and unidirectional governor valve 7 and the oil circuit that first solenoid directional control valve 12 is communicated with, the by pass valve oil inlet is communicated with the oil circuit of first drg, by pass valve into and out of hydraulic fluid port respectively with being communicated with of first solenoid directional control valve into and out of hydraulic fluid port, realize the voltage regulation function of one-level oil pressure.Described first solenoid directional control valve is connected in series by oil circuit with second solenoid directional control valve 13, makes total system have releasing or keeps the two stage braking function.Be connected with second drg 18 by the 3rd electromagnetic valve 14 on the common oil circuit of described unidirectional governor valve 7 and by pass valve 9.The 3rd electromagnetic valve 14 and the 4th solenoid directional control valve 15 are by oil circuit and connect.
Described second solenoid directional control valve is the solenoid directional control valve that has steady arm.
Described first drg 16 of present embodiment and second drg 18 adopt plate disc brake.
This hydraulic work system principle is as follows: during normal operation, starter motor, hydraulic oil passes through shuttle valve 4 through oil pump 3, make first solenoid directional control valve 12,14 energisings of the 3rd solenoid directional control valve, hydraulic oil enters first drg 16, second drg 18 respectively through solenoid directional control valve 12,14, at this moment the oil that comes out from shuttle valve enters unidirectional governor valve 7 through another branch road, promotes the hydraulicchange-over valve core and moves to left, and closes an oil return line in first drg.Scaling up by pass valve electric current, system pressure raise, and when system pressure during greater than 4Mpa, hydraulic oil overcomes spring force, opens plate disc brake, and winch is started working.In the time will stopping winch, reduce the received current of proportional pressure control valve, control presssure reduces, and plate disc brake is band-type brake under the spring force effect, makes the winch stop motion.At this moment the oil that comes out from oil pump and flow back to fuel tank 17 from the oily passing ratio by pass valve that plate disc brake is returned.
Learn the oil circuit realization that this Hydraulic Station service braking partly mainly is made up of proportional pressure control valve 4, solenoid directional control valve 12,14 from the above mentioned.The hydraulic time-delay double-stage braking loop is inoperative when normal operation.
The hydraulic time-delay double-stage braking loop is mainly used in the safety arrestment of winch when emergency episode (having a power failure or the outage etc. of breaking down of winch circuit as unexpected full ore deposit) occurring in operational process, the hydraulic time-delay double-stage braking oil circuit realization that hydraulic pressure time-delay secondary safety arrestment loop partly is made up of unidirectional governor valve 7, hydraulicchange-over valve 8, by pass valve 9, one-way throttle valve 10, energy storage 11, solenoid directional control valve 12,13.
The effect of hydraulic pressure time-delay secondary safety arrestment is, when the winch emergency power off, oil pump shuts down, system pressure reduces to zero, solenoid directional control valve 12,14 outages, in two groups of drgs (first drg and second drg), oil in the II group oil pipe is got back to fuel tank by solenoid directional control valve 14, the second drg band-type brake that links to each other with II group oil pipe, with 1/2 braking force braking, the oil pressure in the drg that another is organized with the I oil pipe links to each other is stopped up by the 4DT of solenoid directional control valve 13, can not oil sump tank, be higher than the fluid of first class pressure part, flow back to fuel tank from by pass valve 9, first drg that links to each other with I group oil pipe is under the first class pressure effect, be in the lagging state, do not play brake action, when winch after reducing running velocity under the second drg effect of II group oil pipe or after slowly coming to a complete stop, the oil pressure of one-level braking is at this moment got back to fuel tank by hydraulicchange-over valve 8, the first drg brake sticking brake of I group oil pipe is checked winch safety.And the commutation of hydraulicchange-over valve is to promote spool by spring to move to right, and by the unidirectional governor valve control spool time length that moves to right, thus control reversing time.Fuel tank is connected in commutation from the winch sudden power to hydraulicchange-over valve, is called the two stage braking delay time during this period of time.Regulate the governor valve openings of sizes, scalable two stage braking delay time.
The effect of each valve is as follows in the hydraulic time-delay double-stage braking loop:
(1) function of by pass valve is to regulate one-level oil pressure pressure.By regulating this valve, can obtain different one-level oil pressure force value (see figure 2)s.During normal operation, the by pass valve inlet and outlet pressure equates that by pass valve is inoperative, when sudden power, and the vanishing immediately of by pass valve delivery pressure, at this moment the pressure in the oil pipe I is the pressure that by pass valve is set.One-level braking oil pressure value generally is made as 2-3Mpa.
(2) hydraulicchange-over valve and unidirectional governor valve make up, and finish the delay function of system's one-level oil pressure, close unidirectional governor valve, and the native system one-level oil pressure dwell time can reach more than one minute; Governor valve reaches maximum, and the dwell time is about 0.3 second.Regulate governor valve, can obtain different one-level oil pressure in-service time (see figure 3)s.Its in-service time is to be set up by governor valve.Its principle is: the two ends of being controlled the hydraulicchange-over valve spool by unidirectional governor valve and spring respectively.When system's normal operation, pressure oil is entered by unidirectional governor valve, promotes hydraulicchange-over valve and closes, and brake pipe I oil circuit and fuel tank are disconnected.When emergency braking occurring, the outage of full ore deposit, system pressure disappears, oil pipe I is in one-level oil pressure state, and spring promotes the hydraulicchange-over valve spool and moves to right, and passes through t second, behind system shutdown, hydraulicchange-over valve is opened by spring, and brake pipe I oil circuit pressure is reduced to zero and finished two stage braking.
(3) one-way throttle valve and energy storage combination realizes giving the one-level braking oil pressure to leak the function of repairing.Because the native system energy storage communicates with brake piping, during normal operation, the energy storage oil pressure is identical with system oil pressure.One-way throttle valve is housed before the energy storage, and when system entered one-level braking oil pressure situation, energy storage pressure was higher than the pressure in the one-level brake circuit, there is pressure reduction before and after the one-way throttle valve, regulate the flow regulating valve openings of sizes, can make the repairing amount equal dredge oil amount, to keep the one-level brake-pressure invariable.
(4) solenoid directional control valve 13 of band detent mechanism and solenoid directional control valve 12 combinations realize removing or keeping the two stage braking function.As: when the cage that the mine is used is worked in well, the 4DT of first solenoid directional control valve, 12 second solenoid directional control valves energising, system possesses the two stage braking function.When cage arrived well head, one side winch passing ratio spill valve decompression was braked and is slowed down, if at this moment run into sudden power, and can be without two stage braking.At this moment, do not have an accident if do not remove the two stage braking cage just might go out well head.Can not adopt two stage braking when therefore, the winch cage is to well head.The 3DT energising of system's second solenoid directional control valve, the two stage braking function is then removed in the 4DT outage.
Hydraulic Station test result and Fig. 2, Fig. 3 gained curve according to the manufacturing of this hydraulic delay two-stage brake hydraulic principle fit like a glove.
Fig. 4 is the one-level braking oil pressure P of JB 3277-91 " mine hoist and mine lift winch Hydraulic Station " standard code and the diagram of curves of one-level braking oil pressure in-service time t.JB 3277-91 standard code Δ P must not be greater than 0.3Mpa, and Δ P1 must not be greater than 5% of Pmax.The general value of Pmax is 6.3Mpa or 11Mpa, 14Mpa.Because the gig Hydraulic Station of each manufacturer production is to reach the invariable perfect condition of one-level brake-pressure from principle, oil pressure can descend in standard in the one-level brake action time so standard allows.Hydraulic time-delay double-stage braking hoister hydraulic station of the present invention changes this situation, makes first class pressure and delay time curve reach perfect condition.
Though the present invention discloses as above with preferred embodiment; right its is not in order to limit the present invention; any person of ordinary skill in the field; without departing from the spirit and scope of the invention; when can doing a little change and improvement, so the present invention's protection domain is as the criterion when looking the claim person of defining.
Claims (5)
1. a hydraulic time-delay double-stage braking hoister hydraulic station by the motor-driven oil pump, connects proportional pressure control valve on the oil circuit of oil pump, and proportional pressure control valve is connected with first drg by shuttle valve, first solenoid directional control valve; First solenoid directional control valve is provided with one-way throttle valve with the oil circuit that first drg is communicated with, and an end of one-way throttle valve is connected with energy storage, and the other end is connected with hydraulicchange-over valve; One end of unidirectional governor valve is connected with by pass valve, and the oil circuit of the other end is communicated with the hydraulic fluid port of hydraulicchange-over valve control spool action; The oil circuit of unidirectional governor valve is communicated with the oil circuit of shuttle valve; By pass valve is connected between oil circuit that first solenoid directional control valve is communicated with first drg and unidirectional governor valve and the oil circuit that first solenoid directional control valve is communicated with; Described first solenoid directional control valve is connected in series by oil circuit with second solenoid directional control valve; Be connected with second drg by the 3rd solenoid directional control valve on the common oil circuit of described unidirectional governor valve and by pass valve; The 3rd solenoid directional control valve and the 4th solenoid directional control valve are by oil circuit and connect.
2. hydraulic time-delay double-stage braking hoister hydraulic station according to claim 1 is characterized in that: the by pass valve oil inlet is communicated with the oil circuit of first drg, by pass valve into and out of hydraulic fluid port respectively with being communicated with of first solenoid directional control valve into and out of hydraulic fluid port.
3. hydraulic time-delay double-stage braking hoister hydraulic station according to claim 1 is characterized in that: one-way throttle valve directly is communicated with the first drg oil circuit with the feed circuit that energy storage is formed.
4. hydraulic time-delay double-stage braking hoister hydraulic station according to claim 1 is characterized in that: the time regulating loop that described hydraulicchange-over valve, unidirectional governor valve are formed, be connected first solenoid directional control valve into and out of hydraulic fluid port.
5. hydraulic time-delay double-stage braking hoister hydraulic station according to claim 1 is characterized in that: described the 3rd solenoid directional control valve is the two Electrical heads change-over valves that have steady arm.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009101031256A CN101475130B (en) | 2009-01-22 | 2009-01-22 | Hydraulic time-delay double-stage braking hoister hydraulic station |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009101031256A CN101475130B (en) | 2009-01-22 | 2009-01-22 | Hydraulic time-delay double-stage braking hoister hydraulic station |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101475130A CN101475130A (en) | 2009-07-08 |
| CN101475130B true CN101475130B (en) | 2010-09-22 |
Family
ID=40835925
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2009101031256A Expired - Fee Related CN101475130B (en) | 2009-01-22 | 2009-01-22 | Hydraulic time-delay double-stage braking hoister hydraulic station |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN101475130B (en) |
Families Citing this family (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102601674A (en) * | 2012-03-22 | 2012-07-25 | 上海三一精机有限公司 | Power-off protection loop for static pressure workbench |
| CN102734353B (en) * | 2012-06-27 | 2015-03-25 | 中联重科股份有限公司 | Brake hydraulic station, brake device, lifting equipment and engineering machinery |
| CN103573729A (en) * | 2013-11-19 | 2014-02-12 | 贵阳高原矿山机械股份有限公司 | Mine hoist hydraulic station |
| CN103671323A (en) * | 2013-12-05 | 2014-03-26 | 柳工无锡路面机械有限公司 | Open vibration valve with electric proportional control function and pressure compensation function and used for road roller |
| DE102014206461A1 (en) * | 2014-04-03 | 2015-10-08 | Thyssen Krupp Elevator Ag | Elevator with a braking device |
| CN104196927B (en) * | 2014-08-08 | 2018-04-27 | 徐州五洋科技股份有限公司 | A kind of Disc Brakes of Downward Belt Conveyor control device |
| CN104595287B (en) * | 2014-11-24 | 2017-02-22 | 慕泽跃 | Energy-reclaiming constant deceleration hydraulic station |
| CN104912865B (en) * | 2015-06-26 | 2016-10-26 | 徐州大恒测控技术有限公司 | A kind of mechanical delay two stage braking manual emergency oil return apparatus and method |
| CN105605037A (en) * | 2016-03-02 | 2016-05-25 | 湖州优创科技有限公司 | Hydraulic station for small lifters |
| CN108547811A (en) * | 2017-08-04 | 2018-09-18 | 常州爱上学教育科技有限公司 | Using the electrohydraulic servo proportional commutation speed governing valve of Servo Control Board, valve core position sensor |
| CN108298452B (en) * | 2018-01-26 | 2019-11-01 | 太原理工大学 | Elevator list damper brake group redundant hydraulic control loop |
| CN109707673A (en) * | 2019-02-26 | 2019-05-03 | 江苏力源液压机械有限公司 | A kind of manual/auto integrated two-way rotary shaft hydraulic braking system |
| CN114151390A (en) * | 2021-12-08 | 2022-03-08 | 中国铁建重工集团股份有限公司 | Hydraulic braking system of bearing test bed |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN85103780A (en) * | 1985-05-08 | 1986-11-05 | 洛阳矿山机器厂 | Hydraulic delay two-stage brake hydraulic station |
| CN2769240Y (en) * | 2005-02-27 | 2006-04-05 | 江苏永丰机械有限责任公司 | Hydraulic system for portal crane |
| CN1854532A (en) * | 2005-04-18 | 2006-11-01 | 卡特彼勒公司 | Electro-hydraulic system for fan driving and brake charging |
| CN200974743Y (en) * | 2006-10-21 | 2007-11-14 | 江苏永丰机械有限责任公司 | Energy-saving tower machine hydraulic stepless change control system |
-
2009
- 2009-01-22 CN CN2009101031256A patent/CN101475130B/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN85103780A (en) * | 1985-05-08 | 1986-11-05 | 洛阳矿山机器厂 | Hydraulic delay two-stage brake hydraulic station |
| CN2769240Y (en) * | 2005-02-27 | 2006-04-05 | 江苏永丰机械有限责任公司 | Hydraulic system for portal crane |
| CN1854532A (en) * | 2005-04-18 | 2006-11-01 | 卡特彼勒公司 | Electro-hydraulic system for fan driving and brake charging |
| CN200974743Y (en) * | 2006-10-21 | 2007-11-14 | 江苏永丰机械有限责任公司 | Energy-saving tower machine hydraulic stepless change control system |
Also Published As
| Publication number | Publication date |
|---|---|
| CN101475130A (en) | 2009-07-08 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN101475130B (en) | Hydraulic time-delay double-stage braking hoister hydraulic station | |
| CN104925685B (en) | A kind of winch hydraulic system that cable is led by stepless time adjustment constant tensile control | |
| CN110219836B (en) | Safety switching braking constant-speed-reduction hydraulic system and braking method for elevator | |
| CN102910550B (en) | Winch emergency pay-off module | |
| CN108706463B (en) | Hydraulic control system of crane | |
| US11958718B2 (en) | Multi-channel impact-resistant intelligent-constant-deceleration hydraulic braking system | |
| CN103613021B (en) | Winch hydraulic control system and engineering machinery | |
| CN110027984B (en) | Hydraulic system of large-load hoister | |
| CN108217376B (en) | A kind of proportional pressure control valve perseverance deceleration safety arrestment redundant hydraulic station and its control method | |
| CN203463385U (en) | Energy-saving hoisting system of hydraulic crane | |
| CN201660396U (en) | Hydraulic station of hydraulic delay braking hoisting machine | |
| CN108557675B (en) | A kind of safety arrestment redundancy perseverance deceleration hydraulic station and its control method | |
| CN108180187B (en) | safe braking series-parallel connection redundancy secondary braking hydraulic station and control method thereof | |
| CN108249339B (en) | A kind of perseverance deceleration safety arrestment redundant hydraulic station and its control method | |
| CN210565392U (en) | Safety conversion braking constant speed reduction hydraulic system of elevator | |
| CN203476861U (en) | Emergency power system and hoisting mechanism and hoisting equipment comprising same | |
| CN201580876U (en) | Hydraulic station device for mine hoister | |
| CN102734353B (en) | Brake hydraulic station, brake device, lifting equipment and engineering machinery | |
| CN202082175U (en) | Hydraulic control system and concrete pumping system equipped with same | |
| CN112833060B (en) | Special balance valve set for aerial ladder vehicle, hydraulic control system and control method of special balance valve set | |
| CN109896461B (en) | High-reliability and high-safety large-load hoister braking system and method | |
| CN204778576U (en) | Stopper hydraulic control unit | |
| CN103129919B (en) | Electro-hydraulic control system of disc type braking device of mine belt conveyor | |
| CN211474556U (en) | Anchor hank equipment integrated control ware | |
| CN211004339U (en) | Multichannel anti-impact intelligent constant-deceleration hydraulic braking system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20100922 Termination date: 20140122 |