CN103508278B - Double-deck elevator - Google Patents
Double-deck elevator Download PDFInfo
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- CN103508278B CN103508278B CN201310231263.9A CN201310231263A CN103508278B CN 103508278 B CN103508278 B CN 103508278B CN 201310231263 A CN201310231263 A CN 201310231263A CN 103508278 B CN103508278 B CN 103508278B
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Abstract
The invention provides a kind of double-deck elevator, it reduces the impact for revising during the hydraulic actuating cylinder action of position between lift car.Correcting device for revising the position of upper car and lower car makes hydraulic actuating cylinder (20) stretch by hydraulic control device (30) supply hydraulic fluid or exudate force feed, revises the position of upper car and lower car thus.When stopping from hydraulic control device (30) to hydraulic actuating cylinder (20) supply hydraulic fluid, after the reduction action of the area for the stream to hydraulic actuating cylinder (20) supply hydraulic fluid starts, correcting device makes Hydraulic Pump (33) stop releasing to hydraulic actuating cylinder (20) action of hydraulic oil.In addition, when stopping from hydraulic actuating cylinder (20) exudate force feed, after the reduction action of the area of the stream for being discharged from hydraulic actuating cylinder (20) by hydraulic oil, correcting device is in the discharge of specific time cutting-off liquid force feed from hydraulic actuating cylinder (20).
Description
Technical field
The present invention relates to a kind of double-deck elevator.
Background technology
Upper car and lower car are connected to each other and the double-deck elevator be elevated in hoist trunk integratedly has height according to each floor to adjust the position regulating function (patent documentation 1) of position.In the prior art, actuating device is set on the top of the car frame for accommodating upper car and lower car.Further, by actuating device by be wound on the lower surface being arranged at upper car pulley and be arranged at lower car lower surface pulley on position adjustment hoist cable roll or put down adjustment upper car and lower car between relative distance.In addition, because adjustment hoist cable in position can occur flexible, so also need the relative distance after to adjustment to revise because of the patronage change in lift car.In the prior art, hydraulic actuating cylinder etc. is used to make the end of position adjustment hoist cable to rise or declines to revise relative distance.
In addition, Patent Document 2 discloses a kind of technology not having direct correlation with double-deck elevator, it is for driving in the general hydraulic circuit of hydraulic actuating cylinder the flowing (patent documentation 2) using non-return valve or one-way control valve etc. to carry out hydraulic control oil.
At first technical literature
Patent documentation
Patent documentation 1: Japanese Patent Laid-Open 2012-046340 publication
Patent documentation 2: Japanese Patent Laid-Open 2002-106507 publication
In the prior art, although use hydraulic actuating cylinder revises the relative distance between lift car, due to large impact can be produced, so the problem that existence can cause the travelling comfort of lift car to decline when hydraulic actuating cylinder starts and when stopping.
Summary of the invention
For this reason, the object of the present invention is to provide a kind of double-deck elevator, the impact produced when it can reduce hydraulic actuating cylinder action.
Solution
In order to solve the problem, the invention provides a kind of double-deck elevator, it has: the car frame be elevated in hoist trunk; Being arranged to can the upper car of displacement along the vertical direction in car frame and lower car; For adjusting the position regulator of upper car and the position of lower car in car frame; And correcting device, correcting device is for revising the position of the upper car after being adjusted by position regulator and lower car, in this double-deck elevator, hydraulic cylinder extension is made by hydraulic control device supply hydraulic fluid or exudate force feed, revise the position of upper car and lower car thus, when stopping from hydraulic control device to hydraulic actuating cylinder supply hydraulic fluid, after the reduction action of the area for the stream to hydraulic actuating cylinder supply hydraulic fluid starts, be used in the Hydraulic Pump stopping action of releasing hydraulic oil to hydraulic actuating cylinder.
Can when stopping from hydraulic actuating cylinder exudate force feed, after the reduction action of the area of the stream for being discharged from hydraulic actuating cylinder by hydraulic oil, correcting device is in the discharge of specified time cutting-off liquid force feed from hydraulic actuating cylinder.
Invention effect
According to the present invention, the impact produced when can reduce hydraulic actuating cylinder action, can improve the travelling comfort of elevator thus.
Accompanying drawing explanation
Fig. 1 is the integral structure figure of double-deck elevator.
Fig. 2 is the constructional drawing of car frame.
Fig. 3 is the constructional drawing of hydraulic efficiency gear.
Fig. 4 is the hydraulic circuit diagram of hydraulic efficiency gear.
Fig. 5 is the sequential chart representing opening time.
Nomenclature
1: double-deck elevator, 3: main frame, 4: hoist cable, 5: actuating device, 8: upper car, 9: lower car, 14: car position adjustment actuating device, 15: control setup, 16 hydraulic efficiency gear, 17 position adjustment hoist cables, 20: hydraulic actuating cylinder, 20A: hydraulic cylinder piston, 21 boatswain chairs, 24: guide rail, 25: guiding device, 30 hydraulic pressure units, 31: supply line, 33: Hydraulic Pump, 34: electromagnetic proportional valve, 35: decline flow regulating valve, 36: rising flow regulating valve, 37: electromagnetism disconnecting valve, 38: discharge line, 39: by pass valve, 40: fuel tank
Detailed description of the invention
Referring to accompanying drawing, embodiments of the present invention are described.In the present embodiment, as described below, can while preventing hydraulic actuating cylinder from naturally sinking, the impact produced when reducing hydraulic actuating cylinder action, thus the travelling comfort of elevator can be improved.
The hydraulic efficiency gear 16 used in the double-deck elevator 1 of present embodiment has the rising flow regulating valve 36 that makes the Hydraulic Pump 33 of running of hydraulic power oil, the maximum flow of hydraulic control oil and decline flow regulating valve 35, the electromagnetic proportional valve 34 of flow of hydraulic control oil, the disconnecting valve 37 preventing hydraulic oil Natural excrement from hydraulic actuating cylinder 20 and hydraulic actuating cylinder 20.
When making hydraulic actuating cylinder 20 rise, Hydraulic Pump 33 being rotated, to supply line 31 supply hydraulic fluid, making disconnecting valve 37 open simultaneously, hydraulic circuit is switched to opening state.Hydraulic oil in hydraulic circuit increases gradually under the effect of rising flow regulating valve 36 and electromagnetic proportional valve 34 from zero flow.Thereby, it is possible to reduce starting-impact when hydraulic actuating cylinder 20 rises.On the other hand, when making hydraulic actuating cylinder 20 stop, controlling electromagnetic proportional valve 34, making the flow of the hydraulic oil in hydraulic circuit reduce to zero flow gradually.Before hydraulic actuating cylinder 20 stops completely, the slew mode of maintenance medium press pump 33 and the open state of disconnecting valve 37.The stopping that can reducing thus when hydraulic actuating cylinder 20 rises is impacted.
When making hydraulic actuating cylinder 20 decline, the deadweight of load can be utilized to be discharged from hydraulic actuating cylinder by hydraulic oil.Therefore, open disconnecting valve 37, switches to opening state by hydraulic circuit.Hydraulic oil in hydraulic circuit increases gradually under the effect of decline flow regulating valve 35 and electromagnetic proportional valve 34 from zero flow.Thereby, it is possible to reduce starting-impact when hydraulic actuating cylinder 20 declines.On the other hand, when making hydraulic actuating cylinder 20 stop, controlling electromagnetic proportional valve 34, making the flow of the hydraulic oil in hydraulic circuit reduce to zero flow gradually.Before hydraulic actuating cylinder 20 stops completely, disconnecting valve 37 is maintained open state.The stopping that can reducing thus when hydraulic actuating cylinder 20 declines is impacted.
By making disconnecting valve 37 be in closed condition, can the state of maintenance medium cylinder pressure 20.Owing to passing through disconnecting valve 37, the circulation of the hydraulic oil in hydraulic circuit is completely cut-off, so hydraulic oil can not be discharged from hydraulic actuating cylinder 20.Thereby, it is possible to the natural slippage of hydraulic actuating cylinder 20 is maintained zero in fact.
First embodiment
Fig. 1 is the integral structure figure of double-deck elevator 1.Double-deck elevator 1 to have in hoist trunk 2 main frame 3 as car frame of lifting, one end is arranged on main frame 3 and the other end is arranged on main hoist cable 4 on counterbalanced weight 7, be wound with the actuating device 5 of main hoist cable 4 and be adjacent to actuating device the deflection sheave 6 that arranges.Actuating device 5 is such as made up of electrical motor, retarder and rope sheave etc., by making rope sheave rotate in specified directions, main frame 3 can be elevated by main hoist cable 4.Upper car 8 and lower car 9 are arranged in main frame 3 in the mode can carrying out displacement in main frame 3 along the vertical direction.
Referring to Fig. 2, the structure of lift car is described.The framed structure of main frame 3 is by superposed upper frame 10, at the lower frame 12 of bottom, the central frame 11 between upper frame 10 and lower frame 12 and be arranged to each framework 10,11,12 above-mentioned to connect into form at the longitudinal framing 13 of the spaced state of above-below direction.
The upside of main frame 3 is provided with the hydraulic efficiency gear 16 as the car position adjustment actuating device 14 (hereinafter referred to as " position adjustment actuating device 14 ") of an example of position regulator, control setup 15 and an example as correcting device.Control setup 15 is for control position adjustment actuating device 14 and hydraulic efficiency gear 16.
Position adjustment actuating device 14 such as has electrical motor and rope sheave, and the hoist cable 17 being arranged on the position adjustment in upper car 8 and lower car 9 is wound on this rope sheave.By position adjustment actuating device 14, hoist cable 17 is rolled or put down, upper car 8 and lower car 9 can be made towards opposite directions displacement.Thus, the relative distance between upper car 8 and lower car 9 is adjusted.
A part of 17A of the hoist cable 17 of above-mentioned position adjustment is wound on the upper car pulley 18A that is arranged on the downside of upper car 8, and another part 17B of the hoist cable 17 of position adjustment is wound on the lower car pulley 18B that is arranged on the downside of lower car 9.The end of the part 17A corresponding with upper car 8 in hoist cable 17 remains in hydraulic efficiency gear 16.The end 17B1 of the part 17B corresponding with lower car 9 in hoist cable 17 is fixed on central frame 11.As mentioned above, when being rolled by hoist cable 17, upper car 8 rises in main frame 3, and meanwhile, lower car 9 declines in main frame 3.Thus, the relative distance between upper car 8 and lower car 9 becomes large.On the other hand, when being put down by hoist cable 17, upper car 8 declines in main frame 3, and meanwhile, lower car 9 rises in main frame 3.Thus, the relative distance between upper car 8 and lower car 9 diminishes.
Rotate by making actuating device 14 and the relative distance between upper car 8 and lower car 9 is adjusted.But when the patronage in the patronage in upper car 8 and lower car 9 is inconsistent, the upper car part 17A of hoist cable 17 is different with the stroke of lower car part 17B.Now, the relative distance between upper car 8 and lower car 9 can change.Therefore, revised by the variation of hydraulic efficiency gear 16 to this relative distance.
Referring to Fig. 3, the structure of hydraulic efficiency gear 16 is described.Hydraulic efficiency gear 16 is broadly divided into mechanism section and hydraulic circuit part.Below first the structure of mechanism section is described.Mechanism section has one or more hydraulic actuating cylinder 20, the boatswain chair 21 be arranged on the hydraulic cylinder piston 20A of each hydraulic actuating cylinder 20, be arranged on one or more guiding devices 25 on boatswain chair 21 and for guiding the guide rail 24 of this guiding device 25.The end 17A1 of the top portion cage side of the hoist cable 17 of position adjustment is fixed on boatswain chair 21 via spring 22 and nut 23 etc.
When control setup 15 exports climb command, hydraulic pressure unit 30 is to hydraulic actuating cylinder 20 supply hydraulic fluid, and the piston 20A of hydraulic actuating cylinder 20 extends thus, boatswain chair 21 under the support of guiding device 25 and guide rail 24 towards upside displacement.Its result, hoist cable 17 is rolled-up, and the relative distance between upper car 8 and lower car 9 increases.
On the other hand, when control setup 15 exports decline instruction, opening from hydraulic actuating cylinder 20 towards the passage of fuel tank (with reference to Fig. 4) of hydraulic pressure unit 30, under the effect of deadweight, hydraulic oil is discharged from hydraulic actuating cylinder 20.When hydraulic oil is from when returning fuel tank by hydraulic actuating cylinder 20, the piston 20A of hydraulic actuating cylinder 20 shortens.Thus, boatswain chair 21 under the support of guiding device 25 and guide rail 24 towards downside displacement.Its result, hoist cable 17 is put down, and the relative distance between upper car 8 and lower car 9 reduces.
In order to make hydraulic actuating cylinder 20 stretch, be provided with hydraulic circuit part.Hydraulic circuit part have as hydraulic control device hydraulic pressure unit 30 and connect the supply line 31 of hydraulic pressure unit 30 and each hydraulic actuating cylinder 20.
Referring to Fig. 4, the structure of hydraulic circuit part is described.Hydraulic pressure unit 30 has Hydraulic Pump 33, the electromagnetic proportional valve 34 as electromagnetic proportional-type direction switch valve, the rising flow regulating valve 36 as first throttle valve, the decline flow regulating valve 35 as second throttle, electromagnetic type disconnecting valve 37 (hereinafter referred to as " disconnecting valve 37 "), discharge line 38, by pass valve 39 and fuel tank 40.
Hydraulic oil according to carrying out the instruction of self-control device 15 from fuel tank 40 aspirated liquid force feed, and is released in supply line 31 from discharge port by Hydraulic Pump 33.Between Hydraulic Pump 33 and hydraulic actuating cylinder 20, be provided with the electromagnetic proportional valve 34 with 4 ports and 3 positions in the midway of supply line 31.Electromagnetic proportional valve 34 is such as configured to the side valve type direction switch valve that spring is positioned at the pattern of central authorities, and switches between three positions (a), (b) and (c) according to the instruction (control signal) carrying out self-control device 15.Thus, electromagnetic proportional valve 34 can while the flow direction of hydraulic control oil, the flow of hydraulic control oil.
Electromagnetic proportional valve 34 has supply position (a), drain position (b) and center position (c), and after screw actuator is according to the instruction action carrying out self-control device 15, the displacement gradually of guiding valve valve body, switches position thus.Supply position (a) is the position hydraulic oil of releasing from Hydraulic Pump 33 being supplied to hydraulic actuating cylinder 20, and when being positioned at supply position (a), the flowing contrary with this flow direction is prevented from.Drain position (b) is the position turned back to by the hydraulic oil in hydraulic actuating cylinder 20 in fuel tank 40, and when being positioned at drain position (b), the flowing contrary with this flow direction is prevented from.Center position (c) is the position of forbidding that hydraulic oil circulates.
Rising flow regulating valve 36 and decline flow regulating valve 35, between electromagnetic proportional valve 34 and hydraulic actuating cylinder 20, are more specifically in series be arranged on supply line 31 between electromagnetic proportional valve 34 and disconnecting valve 37.
Rising flow regulating valve 36 is in the variable throttle valve making the maximum supply flow (flow velocity) of hydraulic cylinder piston 20A rising limit hydraulic oil to hydraulic actuating cylinder 20 supply hydraulic fluid.Rising flow regulating valve 36 is set side by side with non-return valve 36A, and this non-return valve 36A, while permission hydraulic oil flows to fuel tank 40, stops hydraulic oil to flow to hydraulic actuating cylinder 20.Therefore, be supplied to the hydraulic oil of hydraulic actuating cylinder 20 in the restriction timesharing by rising flow regulating valve 36, its maximum flow is subject to the restriction of the area of this throttling part.
Decline flow regulating valve 35 is the variable throttle valve utilizing the load that acts on hydraulic cylinder piston 20A hydraulic oil to be discharged the maximum delivery flow (flow velocity) of limit hydraulic oil from hydraulic actuating cylinder 20.Decline flow regulating valve 35 is set side by side with non-return valve 35A, and this non-return valve 35A, while permission hydraulic oil flows to hydraulic actuating cylinder 20, stops hydraulic oil to flow to fuel tank 40.Therefore, the hydraulic oil of discharging from hydraulic actuating cylinder 20 is by the restriction timesharing of decline flow regulating valve 35, and its maximum flow is subject to the restriction of the area of this throttling part.The setting position of rising flow regulating valve 36 and decline flow regulating valve 35 can be exchanged each other, can be contrary with the occasion shown in Fig. 4, rising flow regulating valve 36 is arranged on electromagnetic proportional valve 34 side, and decline flow regulating valve 35 is arranged on hydraulic actuating cylinder 20 side.
Disconnecting valve 37, between electromagnetic proportional valve 34 and hydraulic actuating cylinder 20, is more specifically the midway being arranged on supply line 31 between rising flow regulating valve 36 and hydraulic actuating cylinder 20.Disconnecting valve 37 is such as configured to two-way electromagnetic valve, has off-position (a) and open position (b).
Off-position (a) is the position of the circulation of cutting-off liquid force feed between electromagnetic proportional valve 34 and hydraulic actuating cylinder 20.When valve body is seated on valve seat, the stream between the port be communicated with electromagnetic proportional valve 34 and the port be communicated with hydraulic actuating cylinder 20 is closed.At ordinary times, disconnecting valve 37 by the elastic force of spring 37A by being pressed in off-position (a).
After screw actuator is according to the instruction action carrying out self-control device 15, valve body overcomes elastic force and lifts off a seat, and the position of disconnecting valve 37 is switched to open position (b).Thus, the hydraulic oil from hydraulic actuating cylinder 20 can flow to electromagnetic proportional valve 34.Discharge line 38 towards fuel tank 40 is connected with the discharge port of electromagnetic proportional valve 34, and the hydraulic oil of discharging from hydraulic actuating cylinder 20 is turned back in fuel tank 40 by the discharge port of electromagnetic proportional valve 34 and discharge line 38.
By pass valve 39 is configured to discharge port and the discharge line 38 of connecting fluid press pump 33.The drain pressure of Hydraulic Pump 33 monitors as control presssure by by pass valve 39, and when control presssure (oil pressure relief) has exceeded elastic force, hydraulic oil is discharged in fuel tank 40 by by pass valve 39.Thus, the hydraulic fluid pressure in supply line 31 is maintained at the pressure of regulation.
Sequential chart referring to Fig. 5 was described opening time.Figure 5 illustrates and make hydraulic actuating cylinder 20 increase, and after maintenance certain hour, make the occasion that hydraulic actuating cylinder 20 declines.First illustrate to hydraulic actuating cylinder 20 supply hydraulic fluid and make the occasion that hydraulic cylinder piston 20A rises.When from Hydraulic Pump 33 to hydraulic actuating cylinder 20 supply hydraulic fluid, control setup 15 is in the actuating signal of very first time T1 output hydraulic pressure pump 33, for electromagnetic proportional valve 34 being switched to the signal of supply position (a) from center position (c) and disconnecting valve 37 being switched to the signal of open position (b) from off-position (a).
Thus, the hydraulic oil of releasing from Hydraulic Pump 33 flows into hydraulic actuating cylinder 20 via the non-return valve 35A of electromagnetic proportional valve 34, decline flow regulating valve 35, the throttling part of rising flow regulating valve 36 and disconnecting valve 37, makes hydraulic cylinder piston 20A increase.When hydraulic cylinder piston 20A rises, mentioned the end 17A1 of hoist cable 17 by boatswain chair 21, revise the relative distance between upper car 8 and lower car 9 thus.The flow of the hydraulic oil in hydraulic circuit increases gradually under the effect of rising flow regulating valve 36 and electromagnetic proportional valve 34 from zero flow.Therefore, it is possible to reduce starting-impact when hydraulic actuating cylinder 20 rises.
The occasion that the rising of hydraulic actuating cylinder 20 is stopped below being described, namely stopping the occasion from Hydraulic Pump 33 to hydraulic actuating cylinder 20 supply hydraulic fluid.Now, first control setup 15 exports signal electromagnetic proportional valve 34 being turned back to center position (c) from supply position (a) at the second time T2.Thus, along with guiding valve is towards center position (c) displacement gradually, flow path area reduces gradually.Before the rising of hydraulic actuating cylinder 20 stops completely (=T2-T3), keep the slew mode (operating state) of Hydraulic Pump 33 and the open position (b) of disconnecting valve 37.
Because the flow of the hydraulic oil in hydraulic circuit reduces to zero gradually, so the impact when rising that can reduce hydraulic actuating cylinder 20 stops.After the rising of hydraulic actuating cylinder 20 stops, control setup 15 is at the danger signal of the 3rd time T3 output hydraulic pressure pump 33 and the signal for disconnecting valve 37 to be switched to off-position (a) from open position (b).Due to disconnecting valve 37 flat time remained on off-position (a) by elastic force, so stop disconnecting valve 37 solenoidal energising after, the position of disconnecting valve 37 is switched to off-position (a) from open position (b).
Above the action between rising stage of hydraulic actuating cylinder 20 is illustrated.After the position of disconnecting valve 37 is switched to off-position (a), hydraulic oil is stoped from the discharge of hydraulic actuating cylinder 20, so the position of hydraulic actuating cylinder 20 is maintained.
Below the action between the decrement phase of hydraulic actuating cylinder 20 is described.Owing to having the Gravitative Loads of load on hydraulic actuating cylinder 20, so there is no need when making hydraulic actuating cylinder 20 decline to make Hydraulic Pump 33 action.Only disconnecting valve 37 need be switched to open position (b), and further electromagnetic proportional valve 34 be switched to drain position (b), the hydraulic oil in hydraulic actuating cylinder 20 just can be made to turn back in fuel tank 40.
When making hydraulic actuating cylinder 20 decline, control setup 15 exports at the 4th time T4 and is used for electromagnetic proportional valve 34 to be switched to the signal of drain position (b) and the signal for disconnecting valve 37 to be switched to open position (b) from off-position (a) from center position (c).Thus, the hydraulic oil in hydraulic actuating cylinder 20 is discharged in fuel tank 40 via the throttling part of the non-return valve 36A of disconnecting valve 37, rising flow regulating valve 36, decline flow regulating valve 35, electromagnetic proportional valve 34 and discharge line 38.Because the guiding valve valve body of electromagnetic proportional valve 34 moves to drain position (b) gradually, so under the effect of electromagnetic proportional valve 34 and decline flow regulating valve 35, the flow of the hydraulic oil of discharging from hydraulic actuating cylinder 20 is started from scratch and is increased gradually.Its result, can reduce starting-impact when hydraulic actuating cylinder 20 declines.
The occasion declined is stopped making hydraulic actuating cylinder 20, namely stop the occasion from hydraulic actuating cylinder 20 exudate force feed, control setup 15 exports the signal being used for electromagnetic proportional valve 34 being switched to center position (c) from drain position (b) at the 5th time T5, make the flow of the hydraulic oil of hydraulic circuit reduce to zero gradually.Further, before hydraulic actuating cylinder 20 stops completely (=T5-T6), disconnecting valve 37 is remained on open position (b).After hydraulic actuating cylinder 20 stops completely, control setup 15 exports the signal being used for disconnecting valve 37 being switched to off-position (a) from open position (b) at the 6th time T6.Thereby, it is possible to reduce impact when hydraulic actuating cylinder 20 decline stops.
Due to when the current location of maintenance medium cylinder pressure 20, disconnecting valve 37 must be positioned at off-position (a), so the natural slippage caused by the loading load acted on hydraulic actuating cylinder 20 can be maintained zero.
According to the present embodiment with said structure, when revising the relative distance between lift car, impact when hydraulic actuating cylinder 20 starts and stops can being reduced, therefore, it is possible to improve the travelling comfort of elevator.
The present invention is not restricted to the described embodiments.Those skilled in the art can carry out various adding and change etc. within the scope of the invention.
Claims (3)
1. a double-deck elevator, it has: the car frame be elevated in hoist trunk; Being arranged to can the upper car of displacement along the vertical direction in described car frame and lower car; For adjusting the position regulator of described upper car and the position of described lower car in described car frame; And correcting device, described correcting device is for revising the position of the described upper car after being adjusted by described position regulator and described lower car, and the feature of described double-deck elevator is,
Described correcting device makes hydraulic cylinder extension by hydraulic control device supply hydraulic fluid or exudate force feed, revises the position of described upper car and described lower car thus,
When stopping from described hydraulic control device to described hydraulic actuating cylinder supply hydraulic fluid, after the reduction action of the area for the stream to described hydraulic actuating cylinder supply hydraulic fluid starts, be used in the Hydraulic Pump stopping action of releasing hydraulic oil to described hydraulic actuating cylinder,
Described correcting device utilizes on the flexible end being used in a side of the position adjustment hoist cable of the relative distance adjusted between described upper car and described lower car of described hydraulic actuating cylinder and rises or decline,
Described hydraulic control device has:
Connect the supply line of described Hydraulic Pump and described hydraulic actuating cylinder;
Electromagnetic proportional-type direction switch valve, described electromagnetic proportional-type direction switch valve is arranged on the midway of described supply line, there is supply position, drain position and center position, described supply position allows hydraulic oil flow to described hydraulic actuating cylinder from described Hydraulic Pump but stop the position of hydraulic oil reverse flow, described drain position allows hydraulic oil flow to fuel tank from described hydraulic actuating cylinder but stop the position of hydraulic oil reverse flow, and described center position is the position of forbidding that hydraulic oil flows between described Hydraulic Pump and described hydraulic actuating cylinder; And
Electromagnetic type disconnecting valve, described electromagnetic type disconnecting valve is arranged between described electromagnetic proportional-type direction switch valve and described hydraulic actuating cylinder, there is off-position and open position, described off-position is the position that cutting-off liquid force feed flows between described electromagnetic proportional-type direction switch valve and described hydraulic actuating cylinder, described open position is the position allowing hydraulic oil to flow between described electromagnetic proportional-type direction switch valve and described hydraulic actuating cylinder
By exporting to described hydraulic control device the control setup that control signal controls the action of described hydraulic control device,
When starting from described Hydraulic Pump to described hydraulic actuating cylinder supply hydraulic fluid, export for making the signal of described Hydraulic Pump action, for described electromagnetic proportional-type direction switch valve being switched to the signal of described supply position from described center position and being used for described electromagnetic type disconnecting valve to be switched to from described off-position the signal of described open position in the very first time
When stopping from described Hydraulic Pump to described hydraulic actuating cylinder supply hydraulic fluid, the signal making described electromagnetic proportional-type direction switch valve turn back to described center position from described supply position is exported in the second time, after this export for the signal that makes described Hydraulic Pump stop and for described electromagnetic type disconnecting valve to be switched to the signal of described off-position from described open position in the 3rd time
When from described hydraulic actuating cylinder exudate force feed, export in the 4th time and be used for described electromagnetic proportional-type direction switch valve being switched to the signal of described drain position from described center position and being used for described electromagnetic type disconnecting valve to be switched to from described off-position the signal of described open position
When stopping from described hydraulic actuating cylinder exudate force feed, export the signal being used for described electromagnetic proportional-type direction switch valve being switched to described center position from described drain position in the 5th time, after this export the signal described electromagnetic type disconnecting valve being switched to described off-position from described open position in the 6th time.
2. double-deck elevator as claimed in claim 1, is characterized in that,
When stopping from described hydraulic actuating cylinder exudate force feed, after the reduction action of the area of the stream for being discharged from described hydraulic actuating cylinder by hydraulic oil, described correcting device is in the discharge of specified time cutting-off liquid force feed from described hydraulic actuating cylinder.
3. double-deck elevator as claimed in claim 1, is characterized in that,
Described supply line is provided with first throttle valve and second throttle, described first throttle valve and second throttle are between described electromagnetic proportional-type direction switch valve and described electromagnetic type disconnecting valve, the oil mass of the hydraulic oil being supplied to described hydraulic actuating cylinder is defined as the first oil mass of regulation by described first throttle valve, and the oil mass of the hydraulic oil of discharging from described hydraulic actuating cylinder is defined as the second oil mass of regulation by described second throttle.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2012135483A JP2014001018A (en) | 2012-06-15 | 2012-06-15 | Double deck elevator |
| JP2012-135483 | 2012-06-15 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103508278A CN103508278A (en) | 2014-01-15 |
| CN103508278B true CN103508278B (en) | 2015-12-09 |
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ID=49891788
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201310231263.9A Expired - Fee Related CN103508278B (en) | 2012-06-15 | 2013-06-09 | Double-deck elevator |
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| Country | Link |
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| JP (1) | JP2014001018A (en) |
| CN (1) | CN103508278B (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2016003696A (en) * | 2014-06-16 | 2016-01-12 | 日本機器鋼業株式会社 | Safety device of hydraulic elevator |
| US11137000B2 (en) * | 2014-10-10 | 2021-10-05 | MEA Inc. | Self-contained energy efficient hydraulic actuator system |
| CN105293257A (en) * | 2015-10-13 | 2016-02-03 | 张忠海 | Numerically-control hydraulic muting type household elevator |
| KR102174745B1 (en) * | 2020-04-06 | 2020-11-05 | 주식회사 이노제스트 | Calibration system for torque measuring apparatus |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1258632A (en) * | 1998-12-14 | 2000-07-05 | Lg产电株式会社 | Hydraulic elevator system |
| CN101864722A (en) * | 2010-06-21 | 2010-10-20 | 厦工(三明)重型机器有限公司 | Vibratory roller and stable vibration start and vibration stop method adopted by same |
| CN102259815A (en) * | 2011-05-17 | 2011-11-30 | 陈海波 | Start and stop control device and control method of self-travelling overhead working truck |
| CN102381614A (en) * | 2010-08-30 | 2012-03-21 | 株式会社日立制作所 | Double-deck elevator |
-
2012
- 2012-06-15 JP JP2012135483A patent/JP2014001018A/en active Pending
-
2013
- 2013-06-09 CN CN201310231263.9A patent/CN103508278B/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1258632A (en) * | 1998-12-14 | 2000-07-05 | Lg产电株式会社 | Hydraulic elevator system |
| CN101864722A (en) * | 2010-06-21 | 2010-10-20 | 厦工(三明)重型机器有限公司 | Vibratory roller and stable vibration start and vibration stop method adopted by same |
| CN102381614A (en) * | 2010-08-30 | 2012-03-21 | 株式会社日立制作所 | Double-deck elevator |
| CN102259815A (en) * | 2011-05-17 | 2011-11-30 | 陈海波 | Start and stop control device and control method of self-travelling overhead working truck |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2014001018A (en) | 2014-01-09 |
| CN103508278A (en) | 2014-01-15 |
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