CN103508278A - Double-deck elevator - Google Patents
Double-deck elevator Download PDFInfo
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- CN103508278A CN103508278A CN201310231263.9A CN201310231263A CN103508278A CN 103508278 A CN103508278 A CN 103508278A CN 201310231263 A CN201310231263 A CN 201310231263A CN 103508278 A CN103508278 A CN 103508278A
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Abstract
The present invention provides a double-deck elevator, which reduces the impact of the motion of a hydraulic cylinder that is used for correcting positions between elevator cars. A correction apparatus that is used for correcting positions of an upper car and a lower car is extended or retracted through the supply or discharge of hydraulic oil through a hydraulic control apparatus (30) so as to correction the positions of the upper car and the lower car. When the supply of hydraulic oil to the hydraulic cylinder (20) by the hydraulic control apparatus (30) is stopped, after the beginning of motion of decreasing the area of the flow path of the hydraulic oil supplied to the hydraulic cylinder (20), the correction apparatus stops a hydraulic pump (33) from discharging the hydraulic oil to the hydraulic cylinder. In addition, when the discharge of the hydraulic oil from the hydraulic cylinder (20) is stopped, after the beginning of motion of decreasing the area of the flow path of the hydraulic oil discharged from the hydraulic cylinder (20), the correction apparatus cuts off the discharge of the hydraulic oil from the hydraulic cylinder (20) in a prescribed period of time.
Description
Technical field
The present invention relates to a kind of double-deck elevator.
Background technology
Upper car and lower car be connected to each other and integratedly in hoist trunk the double-deck elevator of lifting there is the position regulating function (patent documentation 1) of adjusting position according to the height of each floor.In the prior art, for accommodating the top of the car framework of upper car and lower car, actuating device is being set.And, by actuating device, the pulley Shang position adjustment that is wound on the pulley of the lower surface that is arranged at upper car and is arranged at the lower surface of lower car is rolled or is put down the relative distance of adjusting between upper car and lower car with hoist cable.In addition, because position is adjusted with hoist cable and can be occurred to stretch because the patronage in lift car changes, so also need the relative distance after adjusting to revise.In the prior art, with hydraulic actuating cylinder Deng Shi position adjustment, with rising on the end of hoist cable or declining, revise relative distance.
In addition, disclose the technology that a kind of and double-deck elevator do not have direct correlation in patent documentation 2, it is for driving the general hydraulic circuit of hydraulic actuating cylinder to control flow (patent documentation 2) of hydraulic oil with non-return valve or one-way control valve etc.
Technical literature formerly
Patent documentation
Patent documentation 1: the open patent 2012-046340 of Japan communique
Patent documentation 2: the open patent 2002-106507 of Japan communique
In the prior art, although revise the relative distance between lift car with hydraulic actuating cylinder, while starting due to hydraulic actuating cylinder and while stopping, can producing large impact, so the problem that existence can cause the travelling comfort of lift car to decline.
Summary of the invention
For this reason, the object of the present invention is to provide a kind of double-deck elevator, the impact that it produces in the time of can reducing hydraulic actuating cylinder action.
Solution
In order to address the above problem, the invention provides a kind of double-deck elevator, it has: the car framework of lifting in hoist trunk; Be arranged to can be in car framework the upper car of displacement and lower car along the vertical direction; For adjusting upper car and lower car at the position regulator of car framework Nei position; And correcting device, correcting device is for revising upper car after adjusting by position regulator and the position of lower car, in this double-deck elevator, by hydraulic control device supply hydraulic fluid or exudate force feed, make hydraulic cylinder extension, revise thus the position of upper car and lower car, when stopping from hydraulic control device to hydraulic actuating cylinder supply hydraulic fluid, after the reducing action and start of the area of the stream for to hydraulic actuating cylinder supply hydraulic fluid, be used in the Hydraulic Pump of emitting hydraulic oil to hydraulic actuating cylinder and stop action.
Can be when stopping from hydraulic actuating cylinder exudate force feed, the reducing action and start of the area of the stream for hydraulic oil is discharged from hydraulic actuating cylinder, correcting device at the appointed time cutting-off liquid force feed from the discharge of hydraulic actuating cylinder.
Invention effect
According to the present invention, can reduce the impact producing when hydraulic actuating cylinder moves, can improve thus the travelling comfort of elevator.
Accompanying drawing explanation
Fig. 1 is the integral structure figure of double-deck elevator.
Fig. 2 is the constructional drawing of car framework.
Fig. 3 is the constructional drawing of hydraulic efficiency gear.
Fig. 4 is the hydraulic circuit diagram of hydraulic efficiency gear.
Fig. 5 means the sequential chart of 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
The specific embodiment
Referring to accompanying drawing, embodiments of the present invention are described.In the present embodiment, as described below, can when preventing that hydraulic actuating cylinder from sinking naturally, reduce the impact producing when hydraulic actuating cylinder moves, thereby can improve the travelling comfort of elevator.
The hydraulic efficiency gear 16 using in the double-deck elevator 1 of present embodiment has makes the Hydraulic Pump 33 of running of hydraulic power oil, electromagnetic proportional valve 34, the disconnecting valve 37 that prevents hydraulic oil Natural excrement from hydraulic actuating cylinder 20 and the hydraulic actuating cylinder 20 of the flow of the rising flow regulating valve 36 of the maximum flow of control hydraulic oil and decline flow regulating valve 35, control hydraulic oil.
When making hydraulic actuating cylinder 20 increase, make Hydraulic Pump 33 rotations, to supply line 31 supply hydraulic fluids, make disconnecting valve 37 open simultaneously, hydraulic circuit is switched to opening state.Hydraulic oil in hydraulic circuit starts to increase gradually from zero flow under the effect of rising flow regulating valve 36 and electromagnetic proportional valve 34.Thus, the starting-impact in the time of can reducing hydraulic actuating cylinder 20 rising.On the other hand, when hydraulic actuating cylinder 20 is stopped, controlling electromagnetic proportional valve 34, make the flow of the hydraulic oil in hydraulic circuit reduce to gradually zero flow.Before hydraulic actuating cylinder 20 stops completely, the open state of the slew mode of maintenance medium press pump 33 and disconnecting valve 37.Stopping in the time of can reducing thus hydraulic actuating cylinder 20 rising impacted.
When hydraulic actuating cylinder 20 is declined, can utilize the deadweight of load that hydraulic oil is discharged from hydraulic actuating cylinder.Therefore, open disconnecting valve 37, switches to opening state by hydraulic circuit.Hydraulic oil in hydraulic circuit starts to increase gradually from zero flow under the effect of decline flow regulating valve 35 and electromagnetic proportional valve 34.Thus, the starting-impact in the time of can reducing hydraulic actuating cylinder 20 decline.On the other hand, when hydraulic actuating cylinder 20 is stopped, controlling electromagnetic proportional valve 34, make the flow of the hydraulic oil in hydraulic circuit reduce to gradually zero flow.Before hydraulic actuating cylinder 20 stops completely, disconnecting valve 37 is maintained to open state.Stopping in the time of can reducing thus hydraulic actuating cylinder 20 decline impacted.
By making disconnecting valve 37 in closed condition, state that can maintenance medium cylinder pressure 20.Owing to passing through disconnecting valve 37, the circulation of the hydraulic oil in hydraulic circuit is cut off completely, so hydraulic oil can not discharged from hydraulic actuating cylinder 20.Thus, the natural slippage of hydraulic actuating cylinder 20 can be maintained in fact to zero.
The first embodiment
Fig. 1 is the integral structure figure of double-deck elevator 1.Double-deck elevator 1 has and in main frame 3, one end as car framework of hoist trunk 2 interior liftings, is arranged on main frame 3 and the other end is arranged on main hoisting rope 4 on counterbalanced weight 7, is wound with the actuating device 5 of main hoisting rope 4 and is adjacent to actuating device the deflection sheave 6 arranging.Actuating device 5, such as consisting of electrical motor, retarder and rope sheave etc., by rope sheave is rotated up in the side of regulation, can make main frame 3 liftings by main hoisting rope 4.Upper car 8 and lower car 9 are arranged in main frame 3 can carry out along the vertical direction the mode of displacement in main frame 3.
Referring to Fig. 2, the structure of lift car is described.The framed structure of main frame 3 consists of the lower section frame 12 of superposed upper frame 10, bottom, the central frame 11 between upper frame 10 and lower section frame 12 and the longitudinal framing 13 of being arranged to above-mentioned each framework 10,11,12 to connect at the spaced state of above-below direction.
The upside of main frame 3 is provided with actuating device 14 for car position adjustment (hereinafter referred to as " actuating device 14 for the adjustment of position ") as an example of position regulator, control setup 15 and as the hydraulic efficiency gear 16 of an example of correcting device.Control setup 15 is for actuating device 14 and hydraulic efficiency gear 16 for the adjustment of control position.
Position adjustment for example has electrical motor and rope sheave with actuating device 14, and the hoist cable 17 that is arranged on upper car 8 and lower car 9 Shang position adjustment use is wound on this rope sheave.By position adjustment, with actuating device 14, hoist cable 17 is rolled or put down, can make upper car 8 and lower car 9 towards opposite directions displacement.Thus, the relative distance between upper car 8 and lower car 9 is adjusted.
Another part 17B that a part of 17A of the hoist cable 17 of above-mentioned position adjustment use is wound on the hoist cable 17 of the upper car pulley 18AShang， position adjustment use that is arranged at upper car 8 downsides is wound on the lower car pulley 18B that is arranged at lower car 9 downsides.The part 17A end corresponding with upper car 8 in hoist cable 17 remains in hydraulic efficiency gear 16.The part 17B end corresponding with lower car 9 in hoist cable 17 is fixed on central frame 11.As mentioned above, when hoist cable 17 is rolled, upper car 8 is in the interior rising of main frame 3, and meanwhile, lower car 9 is in the interior decline of main frame 3.Thus, the relative distance between upper car 8 and lower car 9 becomes large.On the other hand, when hoist cable 17 is put down, upper car 8 is in the interior decline of main frame 3, and meanwhile, lower car 9 is in the interior rising of main frame 3.Thus, the relative distance between upper car 8 and lower car 9 diminishes.
By making actuating device 14 rotations, the relative distance between upper car 8 and lower car 9 is adjusted.But when 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, by the change of 16 pairs of these relative distances of hydraulic efficiency gear, revise.
Referring to Fig. 3, the structure of hydraulic efficiency gear 16 is described.Hydraulic efficiency gear 16 is broadly divided into mechanism's part and hydraulic circuit part.The structure of following Xian Dui mechanism part describes.Mechanism partly has one or more hydraulic actuating cylinders 20, be arranged on boatswain chair 21 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 use is fixed on boatswain chair 21 via spring 22 and nut 23 etc.
When control setup 15 output climb command, hydraulic pressure unit 30 is to hydraulic actuating cylinder 20 supply hydraulic fluids, 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 output decline instruction, the passage that leads to fuel tank (with reference to Fig. 4) from hydraulic actuating cylinder 20 of hydraulic pressure unit 30 is opened, and under the effect of deadweight, hydraulic oil is discharged from hydraulic actuating cylinder 20.When hydraulic oil is when returning to 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 is dwindled.
In order to make hydraulic actuating cylinder 20 flexible, be provided with hydraulic circuit part.Hydraulic circuit partly has as the hydraulic pressure unit 30 of hydraulic control device and connects hydraulic pressure unit 30 and the supply line 31 of 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, as the electromagnetic proportional valve 34 of solenoid-operated proportional formula direction switch valve, as the rising flow regulating valve 36 of first throttle valve, decline flow regulating valve 35, electromagnetic type disconnecting valve 37 (hereinafter referred to as " disconnecting valve 37 "), discharge line 38, by pass valve 39 and fuel tank 40 as the second flow regulating valve.
Electromagnetic proportional valve 34 has supply position (a), drain position (b) and center position (c), and at screw actuator, according to coming after the instruction action of self-control device 15, the displacement gradually of guiding valve valve body, switches position thus.Supply position (a) is that the hydraulic oil of emitting from Hydraulic Pump 33 is supplied to hydraulic actuating cylinder 20 position, while being positioned at supply position (a), flows to contrary mobile being prevented from this.Drain position (b) is that the hydraulic oil in hydraulic actuating cylinder 20 is turned back to fuel tank 40Nei position, while being positioned at drain position (b), flows to contrary mobile being prevented from this.Center position (c) is the position of forbidding hydraulic oil circulation.
Rising flow regulating valve 36 and decline flow regulating valve 35, between electromagnetic proportional valve 34 and hydraulic actuating cylinder 20, are to be more specifically in series arranged on supply line 31 between electromagnetic proportional valve 34 and disconnecting valve 37.
Rising flow regulating valve 36 is when making hydraulic cylinder piston 20A increase to hydraulic actuating cylinder 20 supply hydraulic fluids, to limit the variable throttle valve of maximum supply flow (flow velocity) use of hydraulic oil.On rising flow regulating valve 36, be set side by side with non-return valve 36A, this non-return valve 36A, when allowing hydraulic oil to flow 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 that the load acting on hydraulic cylinder piston 20A in utilization limits hydraulic oil the variable throttle valve of maximum delivery flow (flow velocity) use of hydraulic oil when hydraulic actuating cylinder 20 is discharged.On decline flow regulating valve 35, be set side by side with non-return valve 35A, this non-return valve 35A, when allowing hydraulic oil to flow 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 in the restriction timesharing by 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, and rising flow regulating valve 36 is arranged on to electromagnetic proportional valve 34 sides, and decline flow regulating valve 35 is arranged on to hydraulic actuating cylinder 20 sides.
Disconnecting valve 37, between electromagnetic proportional valve 34 and hydraulic actuating cylinder 20, is to be more specifically arranged on supply line 31 midway between rising flow regulating valve 36 and hydraulic actuating cylinder 20.Disconnecting valve 37 is for example 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 being communicated with electromagnetic proportional valve 34 and the port that is 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).
At screw actuator, according to coming after the instruction action of self-control device 15, valve body overcomes elastic force and lifts off a seat, and disconnecting valve 37 position is switched to open position (b).Thus, the hydraulic oil from hydraulic actuating cylinder 20 can flow to electromagnetic proportional valve 34.Lead to the discharge line 38 of fuel tank 40 and the discharge port of electromagnetic proportional valve 34 and be connected, the hydraulic oil of discharging from hydraulic actuating cylinder 20 turns back in fuel tank 40 by discharge port and the discharge line 38 of electromagnetic proportional valve 34.
By pass valve 39 is configured to discharge port and the discharge line 38 of connecting fluid press pump 33.By pass valve 39 monitors the drain pressure of Hydraulic Pump 33 as control presssure, when control presssure (oil pressure relief) has surpassed elastic force, by pass valve 39 is discharged to hydraulic oil in fuel tank 40.Thus, the hydraulic fluid pressure in supply line 31 is maintained at the pressure of regulation.
Referring to the sequential chart of Fig. 5 to describing opening time.Figure 5 illustrates and make hydraulic actuating cylinder 20 increase, and after keeping certain hour, the occasion that hydraulic actuating cylinder 20 is declined.First the occasion that makes hydraulic cylinder piston 20A increase to hydraulic actuating cylinder 20 supply hydraulic fluids is described.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 is switched to the signal of supply position (a) and disconnecting valve 37 is switched to the signal of open position (b) from off-position (a) from center position (c).
Thus, the hydraulic oil of emitting from Hydraulic Pump 33, the throttling of rising flow regulating valve 36 part and disconnecting valve 37 flow into hydraulic actuating cylinder 20, rises hydraulic cylinder piston 20A via the non-return valve 35A of electromagnetic proportional valve 34, decline flow regulating valve 35.When hydraulic cylinder piston 20A rises, by boatswain chair 21, mention hoist cable 17 end 17A1, revise thus the relative distance between upper car 8 and lower car 9.The flow of the hydraulic oil in hydraulic circuit starts to increase gradually from zero flow under the effect of rising flow regulating valve 36 and electromagnetic proportional valve 34.Therefore the starting-impact in the time of, can reducing hydraulic actuating cylinder 20 rising.
Below explanation makes the occasion that the rising of hydraulic actuating cylinder 20 stops, and namely stops the occasion from Hydraulic Pump 33 to hydraulic actuating cylinder 20 supply hydraulic fluids.Now, first control setup 15 turns back to electromagnetic proportional valve 34 signal of center position (c) in the second time T 2 outputs from supply position (a).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 in the time of can reducing the rising of hydraulic actuating cylinder 20 and stop.After the rising of hydraulic actuating cylinder 20 stops, control setup 15 is at the danger signal of the 3rd time T 3 output hydraulic pressure pumps 33 with for disconnecting valve 37 is switched to the signal of off-position (a) from open position (b).Because disconnecting valve 37 is remained on off-position (a) by elastic force when flat, so after the solenoidal energising that stops disconnecting valve 37, disconnecting valve 37 position is switched to off-position (a) from open position (b).
Above the action between the rising stage of hydraulic actuating cylinder 20 is illustrated.In disconnecting valve 37 position, be switched to after off-position (a), hydraulic oil is stoped from the discharge of hydraulic actuating cylinder 20, so hydraulic actuating cylinder 20 position 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 to make Hydraulic Pump 33 actions when hydraulic actuating cylinder 20 is declined.Only disconnecting valve 37 need be switched to open position (b), and further electromagnetic proportional valve 34 be switched to drain position (b), just can make the hydraulic oil in hydraulic actuating cylinder 20 turn back in fuel tank 40.
When hydraulic actuating cylinder 20 is declined, control setup 15 in the 4th time T 4 outputs for electromagnetic proportional valve 34 is switched to the signal of drain position (b) and for disconnecting valve 37 is switched to the signal of open position (b) from off-position (a) from center position (c).Thus, the hydraulic oil in hydraulic actuating cylinder 20 via the non-return valve 36A of disconnecting valve 37, rising flow regulating valve 36, the throttling of decline flow regulating valve 35 part, electromagnetic proportional valve 34 and discharge line 38 be discharged in fuel tank 40.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 increased gradually.Its result, the starting-impact in the time of can reducing hydraulic actuating cylinder 20 decline.
Make hydraulic actuating cylinder 20 stop the occasion declining, namely stop from the occasion of hydraulic actuating cylinder 20 exudate force feeds, control setup 15 for electromagnetic proportional valve 34 is switched to the signal of center position (c) from drain position (b), makes the flow of the hydraulic oil of hydraulic circuit reduce to gradually zero in the 5th time T 5 outputs.And, before hydraulic actuating cylinder 20 stops completely (=T5-T6), disconnecting valve 37 is remained on to open position (b).After hydraulic actuating cylinder 20 stops completely, control setup 15 is used for disconnecting valve 37 to be switched to from open position (b) signal of off-position (a) in the 6th time T 6 outputs.Thus, can reduce the impact that hydraulic actuating cylinder 20 declines while stopping.
During due to current location at maintenance medium cylinder pressure 20, disconnecting valve 37 must be positioned at off-position (a), so the natural slippage that the load load by acting on hydraulic actuating cylinder 20 can be caused maintains zero.
According to the present embodiment with said structure, when the relative distance of revising between lift car, the impact when can reduce hydraulic actuating cylinder 20 startings and stopping, therefore can improving the travelling comfort of elevator.
The present invention is not restricted to the described embodiments.Those skilled in the art can carry out various appending and change etc. within the scope of the invention.
Claims (4)
1. a double-deck elevator, it has: the car framework of lifting in hoist trunk; Be arranged to can be in described car framework upper car and the lower car of displacement along the vertical direction; For adjusting described upper car and described lower car at the position regulator of described car framework Nei position; And correcting device, described correcting device is for revising described upper car after adjusting by described position regulator and the position of described lower car, and described double-deck elevator is characterised in that,
Described correcting device makes hydraulic cylinder extension by hydraulic control device supply hydraulic fluid or exudate force feed, revises thus the position of described upper car and described lower car,
When stopping from described hydraulic control device to described hydraulic actuating cylinder supply hydraulic fluid, after the reducing action and start of the area of the stream for to described hydraulic actuating cylinder supply hydraulic fluid, be used in the Hydraulic Pump of emitting hydraulic oil to described hydraulic actuating cylinder and stop action.
2. double-deck elevator as claimed in claim 1, is characterized in that,
When stopping from described hydraulic actuating cylinder exudate force feed, the reducing action and start of the area of the stream for hydraulic oil is discharged from described hydraulic actuating cylinder, described correcting device at the appointed time cutting-off liquid force feed from the discharge of described hydraulic actuating cylinder.
3. the double-deck elevator as described in claim 1 or 2, is characterized in that,
Described correcting device utilizes the flexible position adjustment that is used in the relative distance of adjusting between described upper car and described lower car of described hydraulic actuating cylinder with rising on the Yi Fang end of hoist cable or declining,
Described hydraulic control device has:
The supply line that connects described Hydraulic Pump and described hydraulic actuating cylinder;
Solenoid-operated proportional formula direction switch valve, described solenoid-operated proportional formula direction switch valve is arranged on described supply line midway, there is supply position, drain position and center position, described supply position is to allow hydraulic oil to flow to described hydraulic actuating cylinder but the position of prevention hydraulic oil reverse flow from described Hydraulic Pump, described drain position is to allow hydraulic oil to flow to fuel tank but the position that stops hydraulic oil reverse flow from described hydraulic actuating cylinder, and described center position is to forbid hydraulic oil mobile position between described Hydraulic Pump and described hydraulic actuating cylinder; And
Electromagnetic type disconnecting valve, described electromagnetic type disconnecting valve is arranged between described solenoid-operated proportional formula direction switch valve and described hydraulic actuating cylinder, there is off-position and open position, described off-position is cutting-off liquid force feed mobile position between described solenoid-operated proportional formula direction switch valve and described hydraulic actuating cylinder, described open position is to allow hydraulic oil mobile position between described solenoid-operated proportional formula direction switch valve and described hydraulic actuating cylinder
By control the control setup of the action of described hydraulic control device to described hydraulic control device output control signal,
When starting from described Hydraulic Pump to described hydraulic actuating cylinder supply hydraulic fluid, in very first time output for making the signal of described Hydraulic Pump action, for described solenoid-operated proportional formula direction switch valve is switched to the signal of described supply position and for described electromagnetic type disconnecting valve is switched to the signal of described open position from described off-position from described center position
When stopping from described Hydraulic Pump to described hydraulic actuating cylinder supply hydraulic fluid, in the second time, output makes described solenoid-operated proportional formula direction switch valve from described supply position, turn back to the signal of described center position, after this in the 3rd time output for the signal that makes described Hydraulic Pump and stop and for described electromagnetic type disconnecting valve is switched to the signal of described off-position from described open position
When from described hydraulic actuating cylinder exudate force feed, in the 4th time output for described solenoid-operated proportional formula direction switch valve is switched to the signal of described drain position and for described electromagnetic type disconnecting valve is switched to the signal of described open position from described off-position from described center position
When stopping from described hydraulic actuating cylinder exudate force feed, in the output of the 5th time, for described solenoid-operated proportional formula direction switch valve is switched to the signal of described center position from described drain position, after this in the 6th time, output is switched to the signal of described off-position by described electromagnetic type disconnecting valve from described open position.
4. double-deck elevator as claimed in claim 3, is characterized in that,
On described supply line, be provided with first throttle valve and the second flow regulating valve, described first throttle valve and the second throttling valve are positioned between described solenoid-operated proportional formula direction switch valve and described electromagnetic type disconnecting valve, described first throttle valve is defined as the oil mass that is supplied to the hydraulic oil of described hydraulic actuating cylinder the first oil mass of regulation, and described the second flow regulating valve is defined as the oil mass of the hydraulic oil of discharging from described hydraulic actuating cylinder the second oil mass of regulation.
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 true CN103508278A (en) | 2014-01-15 |
| CN103508278B 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 |
|---|---|
| JP (1) | JP2014001018A (en) |
| CN (1) | CN103508278B (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
Families Citing this family (2)
| 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 |
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 |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2014001018A (en) | 2014-01-09 |
| CN103508278B (en) | 2015-12-09 |
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Granted publication date: 20151209 |