JP2014001018A - Double deck elevator - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce an in-operation shock of a hydraulic cylinder which corrects a position between cars.SOLUTION: A correction device for correcting positions of an upper car and a lower car corrects the positions of the upper car and lower car by expanding and contracting a hydraulic cylinder 20 by application and removal of oil pressure from a hydraulic pressure control device 30. The correction device when stopping supplying the working oil from the hydraulic pressure control device 30 to the hydraulic cylinder 20 stops a hydraulic pump 33 for discharging working oil to the hydraulic cylinder 20 from operating after starting an operation to decrease the area of a flow passage for supplying the working oil to the hydraulic cylinder 20. Further, the correction device when stopping discharging the working oil from the hydraulic cylinder 20 quits discharging the working oil from the hydraulic cylinder 20 in predetermined timing after starting the operation to decrease the area of the flow passage for discharging the working oil from the hydraulic cylinder 20.

Description

  The present invention relates to a double deck elevator.

  A double deck elevator that connects an upper car and a lower car so as to integrally move up and down in the hoistway has a position adjustment function to match the height of each floor (Patent Document 1). In the prior art, a driving device is provided on the upper part of the car frame that accommodates the upper car and the lower car. Then, by driving up and down the position adjusting rope wound around the pulley provided on the lower surface of the upper car and the pulley provided on the lower surface of the lower car by the driving device, the relative position between the upper car and the lower car is increased. The distance is adjusted. Furthermore, since the position adjusting rope expands and contracts depending on the number of passengers in the car, it is necessary to further correct the adjusted relative distance. Therefore, in the prior art, the relative distance is corrected by raising or lowering the end of the position adjusting rope using a hydraulic cylinder or the like.

  Although not a technique directly related to a double deck elevator, a general hydraulic circuit that drives a hydraulic cylinder uses a check valve, a pilot check valve, or the like to control the flow of hydraulic oil (Patent Document 2). ).

JP 2012-046340 A JP 2002-106507 A

  In the prior art, the relative distance between the cars is corrected using a hydraulic cylinder, but there is a problem that the riding comfort of the car is reduced because of the large shock that occurs when the hydraulic cylinder is started and stopped.

  SUMMARY OF THE INVENTION An object of the present invention is to provide a double deck elevator that can reduce a shock that occurs during operation of a hydraulic cylinder.

  In order to solve the above-described problems, a double deck elevator according to the present invention includes a car frame that moves up and down in a hoistway, an upper car and a lower car, and an upper car and a lower car that are provided to be vertically displaceable in the car frame In a double deck elevator comprising a position adjusting device for adjusting a position in a car frame and a correcting device for correcting the positions of an upper car and a lower car adjusted by the position adjusting device, a correcting device Is to correct the position of the upper car and the lower car by expanding and contracting the hydraulic cylinder by supplying and discharging hydraulic pressure from the hydraulic control device. When stopping the supply of hydraulic oil from the hydraulic control device to the hydraulic cylinder, Then, after the operation of reducing the area of the flow path for supplying the hydraulic oil to the hydraulic cylinder is started, the operation of the hydraulic pump for discharging the hydraulic oil to the hydraulic cylinder is stopped.

  When stopping the hydraulic oil discharge from the hydraulic cylinder, the correction device starts the operation of reducing the area of the flow path for discharging the hydraulic oil from the hydraulic cylinder, and then discharges the hydraulic oil from the hydraulic cylinder at a predetermined timing. It can also be blocked.

  According to the present invention, it is possible to reduce a shock during operation of the hydraulic cylinder, and to improve riding comfort.

It is a whole block diagram of a double deck elevator. It is a block diagram of a car frame. It is a block diagram of a hydraulic device. It is a hydraulic circuit diagram of a hydraulic device. It is a time chart which shows operation timing.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the present embodiment, as will be described in detail below, the ride comfort is improved by reducing the shock when the hydraulic cylinder is activated while preventing the natural settling of the hydraulic cylinder.

  The hydraulic device 16 used in the double deck elevator 1 according to the present embodiment includes a hydraulic pump 33 that flows hydraulic oil, an ascending throttle valve 36 and a descending throttle valve 35 that control the maximum flow rate of the hydraulic oil, An electromagnetic proportional valve 34 that controls the flow rate, a shutoff valve 37 that prevents natural discharge of hydraulic oil from the hydraulic cylinder 20, and the hydraulic cylinder 20 are provided.

  When the hydraulic cylinder 20 is raised, the hydraulic pump 33 is rotated to supply hydraulic oil to the supply line 31, and at the same time, the shutoff valve 37 is opened to switch the hydraulic circuit to the open state. The hydraulic oil in the hydraulic circuit gradually increases from zero flow rate by the action of the up throttle valve 36 and the electromagnetic proportional valve 34. Thereby, the starting shock at the time of the raise of the hydraulic cylinder 20 can be reduced. Further, when the hydraulic cylinder 20 is stopped, the electromagnetic proportional valve 34 is controlled to gradually reduce the hydraulic oil in the hydraulic circuit to zero flow rate. The rotation state of the hydraulic pump 33 and the open state of the shutoff valve 37 are maintained until the hydraulic cylinder 20 is completely stopped. As a result, the stop shock when the hydraulic cylinder 20 is raised can be reduced.

  When the hydraulic cylinder 20 is lowered, the hydraulic oil can be discharged from the hydraulic cylinder by the weight of the load. Therefore, the shutoff valve 37 is opened, and the hydraulic circuit is switched to the open state. The hydraulic oil in the hydraulic circuit gradually increases from zero flow rate by the action of the down throttle valve 35 and the electromagnetic proportional valve 34. Thereby, the starting shock when the hydraulic cylinder 20 is lowered can be reduced. Further, when the hydraulic cylinder 20 is stopped, the electromagnetic proportional valve 34 is controlled to gradually reduce the hydraulic oil in the hydraulic circuit to zero flow rate. The shut-off valve 37 is kept open until the hydraulic cylinder 20 is completely stopped. Thereby, the stop shock when the hydraulic cylinder 20 is lowered can be reduced.

  The state of the hydraulic cylinder 20 can be maintained by closing the shutoff valve 37. Since the shutoff valve 37 completely shuts off the flow of the hydraulic oil in the hydraulic circuit, the hydraulic oil is not discharged from the hydraulic cylinder 20 and the natural descent amount of the hydraulic cylinder 20 is maintained at substantially zero. be able to.

  FIG. 1 is an overall configuration diagram of a double deck elevator 1. The double deck elevator 1 includes a main frame 3 as a “car frame” that moves up and down in the hoistway 2, a main rope 4 having one end attached to the main frame 3 and the other end attached to a counterweight 7, and a main rope 4. A wound driving device 5 and a deflecting wheel 6 disposed adjacent to the driving device 5 are provided. The drive device 5 includes, for example, an electric motor, a speed reducer, a sheave, and the like, and raises and lowers the main frame 3 via the main rope 4 by rotating the sheave in a predetermined direction. An upper car 8 and a lower car 9 are attached to the main frame 3 so as to be displaceable in the vertical direction within the main frame 3.

  The car configuration will be described with reference to FIG. The frame structure of the main frame 3 includes an upper frame 10 positioned at the upper portion, a lower frame 12 positioned at the lower portion, an intermediate frame 11 positioned between the upper frame 10 and the lower frame 12, and the frames 10, 11, 12 And an upright frame 13 provided so as to be connected in a state of being separated in the vertical direction.

  Also, on the upper side of the main frame 3, an example of a “position adjustment device”, a car position adjustment drive device 14 (hereinafter, position adjustment drive device 14), a control device 15, and an example of a “correction device”. A hydraulic device 16 is provided. The control device 15 controls the position adjusting drive device 14 and the hydraulic device 16.

  The position adjusting drive device 14 includes, for example, an electric motor and a sheave, and a rope 17 for position adjustment attached to the upper car 8 and the lower car 9 is wound around the sheave. When the position adjusting drive device 14 winds up or down the rope 17, the upper car 8 and the lower car 9 are displaced in directions opposite to each other. Thereby, the relative distance between the upper car 8 and the lower car 9 is adjusted.

  A part 17 </ b> A of the position adjusting rope 17 is wound around an upper car pulley 18 </ b> A provided on the lower side of the upper car 8. The other part 17B of the rope 17 is wound around a lower car pulley 18B provided on the lower side of the lower car 9. The end of the portion 17 </ b> A corresponding to the upper car 8 in the rope 17 is held in the hydraulic device 16. The end of the portion 17 </ b> B corresponding to the lower car 9 of the rope 17 is fixed to the intermediate frame 11. As described above, when the rope 17 is wound up, the upper car 8 moves up in the main frame 3, and at the same time, the lower car 9 moves down in the main frame 3. As a result, the relative distance between the upper car 8 and the lower car 9 increases. On the other hand, when the rope 17 is unwound, the upper car 8 moves down in the main frame 3 and at the same time, the lower car 9 moves up in the main frame 3. As a result, the relative distance between the upper car 8 and the lower car 9 is reduced.

  The relative distance between the upper car 8 and the lower car 9 is adjusted through the rotation of the driving device 14, but depending on the difference between the number of passengers in the upper car 8 and the number of passengers in the lower car 9, the upper car portion 17 </ b> A of the rope 17. The amount of expansion / contraction of the lower cage portion 17B is different. Accordingly, the relative distance between the upper car 8 and the lower car 9 varies. Therefore, the fluctuation of the relative distance is corrected by the hydraulic device 16.

  The configuration of the hydraulic device 16 will be described with reference to FIG. The hydraulic device 16 can be roughly divided into a mechanism part and a hydraulic circuit part. First, the structure of the mechanism unit will be described. The mechanism includes one or more hydraulic cylinders 20, a suspension plate 21 attached to the cylinder rod 20A of each hydraulic cylinder 20, one or more guide devices 25 provided on the suspension plate 21, and a guide device. And a guide rail 24 for guiding 25. An end portion 17A1 on the upper cage side of the position adjusting rope 17 is fixed to the suspension plate 21 via a spring 22, a nut 23, and the like.

  When an increase command is issued from the control device 15, the hydraulic unit 30 supplies hydraulic oil to the hydraulic cylinder 20. As a result, the rod 20 </ b> A of the hydraulic cylinder 20 extends, and the suspension plate 21 is displaced upward while being supported by the guide device 25 and the guide rail 24. As a result, the rope 17 is pulled up and the relative distance between the upper car 8 and the lower car 9 is increased.

  On the contrary, when a lowering command is issued from the control device 15, the hydraulic unit 30 opens a passage from the hydraulic cylinder 20 to the oil tank (see FIG. 4) so that the hydraulic oil can be discharged from the hydraulic cylinder 20 by its own weight. To. When the hydraulic oil is returned from the hydraulic cylinder 20 to the oil tank, the rod 20A of the hydraulic cylinder 20 is contracted. Accordingly, the suspension plate 21 is displaced downward while being supported by the guide device 25 and the guide rail 24. As a result, the rope 17 is lowered and the relative distance between the upper car 8 and the lower car 9 is reduced.

  In order to expand and contract the hydraulic cylinder 20, a hydraulic circuit unit is provided. The hydraulic circuit section includes a hydraulic unit 30 as a “hydraulic control device”, and a supply pipe 31 that connects the hydraulic unit 30 and each hydraulic cylinder 20.

  The configuration of the hydraulic circuit unit will be described with reference to FIG. The hydraulic unit 30 includes a hydraulic pump 33, an electromagnetic proportional valve 34 as an “electromagnetic proportional directional switching valve”, an up throttle valve 36 as a “first throttle valve”, and a downward throttle as a “second throttle valve”. A valve 35, an electromagnetic shut-off valve 37 (hereinafter referred to as a shut-off valve 37), a discharge pipe 38, a relief valve 39, and an oil tank 40 are provided.

  The hydraulic pump 33 sucks hydraulic oil from the oil tank 40 in accordance with a command from the control device 15 and discharges the hydraulic oil into the supply pipe 31 from the discharge port. An electromagnetic proportional valve 34 at a 4-port 3 position is provided in the middle of the supply line 31 between the hydraulic pump 33 and the hydraulic cylinder 20. The electromagnetic proportional valve 34 is configured as, for example, a spring center type spool type direction switching valve, and switches the positions (a), (b), and (c) in accordance with a command (control signal) from the control device 15. It has become. Thereby, the electromagnetic proportional valve 34 can control the flow direction of hydraulic fluid and the flow rate of hydraulic fluid simultaneously.

  The electromagnetic proportional valve 34 has a supply position (a), a discharge position (b), and a neutral position (c). When the solenoid is actuated by a command from the control device 15, the spool valve body is gradually displaced. Then the position is switched. The supply position (a) is a position for supplying hydraulic oil discharged from the hydraulic pump 33 toward the hydraulic cylinder 20, and a flow in the opposite direction is prevented. The discharge position (b) is a position for returning the hydraulic oil in the hydraulic cylinder 20 to the oil tank 40, and the flow in the opposite direction is prevented. The neutral position (c) is a position for prohibiting the flow of hydraulic oil.

  The ascending throttle valve 36 and the descending throttle valve 35 are located between the electromagnetic proportional valve 34 and the hydraulic cylinder 20, more specifically, located between the electromagnetic proportional valve 34 and the shutoff valve 37, and in series with the supply pipe 31. Is provided.

  The rising throttle valve 36 is a variable throttle valve for limiting the maximum supply flow rate (flow velocity) of hydraulic oil when hydraulic oil is supplied to the hydraulic cylinder 20 to raise the cylinder rod 20A. The ascending throttle valve 36 is provided with a check valve 36A in parallel for permitting the flow toward the oil tank 40 and preventing the flow toward the hydraulic cylinder 20. Accordingly, the hydraulic oil supplied to the hydraulic cylinder 20 passes through the throttle portion of the ascending throttle valve 36, and the maximum flow rate is limited by the area of the throttle portion.

  The descending throttle valve 35 is a variable throttle valve for limiting the maximum discharge flow rate (flow velocity) of the hydraulic oil when the hydraulic oil is discharged from the hydraulic cylinder 20 using a load applied to the cylinder rod 20A. The descending throttle valve 35 is provided with a check valve 35 </ b> A in parallel for permitting the flow toward the hydraulic cylinder 20 and preventing the flow toward the oil tank 40. Therefore, the hydraulic oil discharged from the hydraulic cylinder 20 passes through the throttle portion of the descending throttle valve 35, and the maximum flow rate is limited by the area of the throttle portion. The installation positions of the up throttle valve 36 and the down throttle valve 35 may be reversed. Contrary to the example shown in FIG. 4, the up throttle valve 36 may be provided on the electromagnetic proportional valve 34 side, and the down throttle valve 35 may be provided on the hydraulic cylinder 20 side.

  The shut-off valve 37 is located between the electromagnetic proportional valve 34 and the hydraulic cylinder 20, more specifically between the throttle valve 36 and the hydraulic cylinder 20, and is provided in the middle of the supply line 31. The shut-off valve 37 is configured, for example, as a two-way electromagnetic valve, and includes a cutoff position (a) and an opening position (b).

  The shut-off position (a) shuts off the flow of hydraulic oil between the electromagnetic proportional valve 34 and the hydraulic cylinder 20. When the valve body is seated on the valve seat, the flow path between the port communicating with the electromagnetic proportional valve 34 and the port communicating with the hydraulic cylinder 20 is closed. Normally, the spring 37A is biased so as to be in the blocking position (a) by the spring force.

  When the solenoid is actuated by a command from the control device 15, the valve element is separated from the valve seat against the spring force and switched to the open position (b). As a result, the hydraulic oil from the hydraulic cylinder 20 can flow toward the electromagnetic proportional valve 34. A discharge pipe 38 leading to the oil tank 40 is connected to the discharge port of the electromagnetic proportional valve 34, and the hydraulic oil discharged from the hydraulic cylinder 20 is returned to the oil tank 40.

  The relief valve 39 is provided so as to connect the discharge port of the hydraulic pump 33 and the discharge pipe 38. The relief valve 39 monitors the discharge pressure of the hydraulic pump 33 as a pilot pressure, and discharges hydraulic oil to the oil tank 40 when the pilot pressure (relief pressure) exceeds the spring force. Thereby, the hydraulic oil pressure in the supply pipeline 31 is maintained at a predetermined pressure.

  The operation timing will be described with reference to the timing chart of FIG. FIG. 5 shows a case where the hydraulic cylinder 20 is lowered after the hydraulic cylinder 20 is raised and held. First, the case where hydraulic oil is supplied to the hydraulic cylinder 20 to raise the cylinder rod 20A will be described. When supplying hydraulic oil from the hydraulic pump 33 to the hydraulic cylinder 20, the control device 15 includes an operation signal for the hydraulic pump 33 and a signal for switching the electromagnetic proportional valve 34 from the neutral position (c) to the supply position (a). A signal for switching the shutoff valve 37 from the shut-off position (a) to the open position (b) is output at the first timing T1.

  As a result, the hydraulic oil discharged from the hydraulic pump 33 flows into the hydraulic cylinder 20 via the electromagnetic proportional valve 34, the check valve 35 </ b> A of the descending throttle valve 35, the throttle portion of the rising throttle valve 36, and the shutoff valve 37. Then, the cylinder rod 20A is raised. As the cylinder rod 20A rises, the suspension plate 21 pulls up the end 17A1 of the rope 17 to correct the relative distance between the upper car 8 and the lower car 9. The flow rate of the hydraulic oil in the hydraulic circuit is gradually increased from zero by the ascending throttle valve 36 and the electromagnetic proportional valve 34. Therefore, the starting shock when the hydraulic cylinder 20 is raised can be reduced.

  A case where the rising of the hydraulic cylinder 20 is stopped, that is, a case where the supply of hydraulic oil from the hydraulic pump 33 to the hydraulic cylinder 20 is stopped will be described. In this case, the control device 15 first outputs a signal for returning the electromagnetic proportional valve 34 from the supply position (a) to the neutral position (c) at the second timing T2. As a result, the spool valve is gradually displaced toward the neutral position (c), and the flow passage area gradually decreases. Until the ascent of the hydraulic cylinder 20 stops completely (= T2-T3), the rotation state (operation state) of the hydraulic pump 33 and the open position (b) of the shut-off valve 37 are maintained.

  As a result, the flow rate of the hydraulic oil in the hydraulic circuit gradually decreases until it reaches zero, so that the shock when stopping the rise of the hydraulic cylinder 20 can be reduced. After the ascent of the hydraulic cylinder 20 stops, the control device 15 outputs a stop signal of the hydraulic pump 33 and a signal for switching the shutoff valve 37 from the open position (b) to the shut-off position (a) at the third timing T3. To do. Since the shut-off valve 37 is always urged to be in the shut-off position (a) by the spring force, if the energization to the solenoid of the shut-off valve 37 is stopped, the shut-off position (b) is changed from the open position (b) Switch to a).

  The above is the operation during the rising period of the hydraulic cylinder 20. When the shut-off valve 37 is switched to the shut-off position (a), the hydraulic oil 20 is prevented from being discharged from the hydraulic cylinder 20, so that the position of the hydraulic cylinder 20 is maintained.

  Next, the operation during the lowering period of the hydraulic cylinder 20 will be described. Since the weight of the load is applied to the hydraulic cylinder 20, it is not necessary to operate the hydraulic pump 33 to lower the hydraulic cylinder 20. The hydraulic oil in the hydraulic cylinder 20 can be returned to the oil tank 40 simply by switching the shut-off valve 37 to the open position (b) and further switching the electromagnetic proportional valve 34 to the discharge position (b).

  When the hydraulic cylinder 20 is lowered, the control device 15 switches a signal for switching the electromagnetic proportional valve 34 from the neutral position (c) to the discharge position (b) and the shutoff valve 37 from the shut-off position (a) to the open position ( The signal for switching to b) is output at the fourth timing T4. As a result, the hydraulic oil in the hydraulic cylinder 20 passes through the shutoff valve 37, the check valve 36 </ b> A of the ascending throttle valve 36, the throttle portion of the descending throttle valve 35, the electromagnetic proportional valve 34, and the discharge pipe 38. To be discharged. Here, since the spool valve body of the electromagnetic proportional valve 34 gradually moves to the discharge position (b), the flow rate of the hydraulic oil discharged from the hydraulic cylinder 20 is gradually increased from zero by the electromagnetic proportional valve 34 and the descending throttle valve 35. To increase. As a result, it is possible to reduce the starting shock when the hydraulic cylinder 20 is lowered.

  When stopping the descent of the hydraulic cylinder 20, that is, when stopping the hydraulic oil discharge from the hydraulic cylinder 20, a signal for switching the electromagnetic proportional valve 34 from the discharge position (b) to the neutral position (c) is the fifth. Output at timing T5 and gradually reduce the flow rate of hydraulic fluid in the hydraulic circuit until it becomes zero. The shutoff valve 37 is kept at the open position (b) until the hydraulic cylinder 20 is completely stopped (= T5-T6). When the hydraulic cylinder 20 is completely stopped, a signal for switching the shut-off valve 37 from the open position (b) to the shut-off position (a) is output at the sixth timing T6. As a result, shock when stopping the lowering of the hydraulic cylinder 20 can be reduced.

  When the current position of the hydraulic cylinder 20 is maintained, the shut-off valve 37 is always set at the shut-off position (a), so that the amount of natural descent due to the load applied to the hydraulic cylinder 20 can be maintained at zero.

  According to the present embodiment configured as described above, since the shock at the time of starting and stopping of the hydraulic cylinder 20 for correcting the relative distance between the cars can be reduced, the riding comfort can be improved.

  In addition, this invention is not limited to the Example mentioned above. A person skilled in the art can make various additions and changes within the scope of the present invention.

  1: double deck elevator, 3: main frame, 4: rope, 5: driving device, 8: upper car, 9: lower car, 14: driving device for car position adjustment, 15: control device, 16: hydraulic device, 17 : Position adjusting rope, 20: Hydraulic cylinder, 20A: Cylinder rod, 21: Suspension plate, 24: Guide rail, 25: Guide device, 30: Hydraulic unit, 31: Supply line, 33: Hydraulic pump, 34: Electromagnetic Proportional valve, 35: Down throttle valve, 36: Up throttle valve, 37: Electromagnetic shut-off valve, 38: Discharge pipe, 39: Relief valve, 40: Oil tank.

Claims (4)

A car frame that moves up and down in the hoistway, an upper car and a lower car provided to be vertically displaceable in the car frame, and the position of the upper car and the lower car in the car frame. In a double deck elevator comprising a position adjustment device and a correction device for correcting the positions of the upper car and the lower car adjusted by the position adjustment device,
The correction device includes:
Correcting the positions of the upper car and the lower car by expanding and contracting the hydraulic cylinder by supplying and discharging hydraulic pressure from the hydraulic control device;
When stopping the supply of the hydraulic oil from the hydraulic control device to the hydraulic cylinder, the hydraulic oil is supplied to the hydraulic cylinder after starting the operation of reducing the area of the flow path for supplying the hydraulic oil to the hydraulic cylinder. Stop the operation of the hydraulic pump for discharging
A double deck elevator characterized by that. The correction device, when stopping the hydraulic oil discharge from the hydraulic cylinder, starts the operation of reducing the area of the flow path for discharging the hydraulic oil from the hydraulic cylinder, and then from the hydraulic cylinder at a predetermined timing. Shut off hydraulic oil discharge,
The double deck elevator according to claim 1. The correction device raises or lowers one end portion of a position adjusting rope used for adjusting the relative distance between the upper car and the lower car by using expansion and contraction of the hydraulic cylinder,
The hydraulic control device includes:
A supply line connecting the hydraulic pump and the hydraulic cylinder;
An electromagnetic proportional directional control valve provided in the middle of the supply pipe, wherein a supply position that permits the flow of hydraulic oil from the hydraulic pump to the hydraulic cylinder and prevents a reverse flow; and from the hydraulic cylinder An electromagnetic proportional directional switch having a discharge position that allows the flow of hydraulic oil to the oil tank and prevents reverse flow, and a neutral position that prohibits the flow of hydraulic oil between the hydraulic pump and the hydraulic cylinder A valve,
An electromagnetic shut-off valve provided between the electromagnetic proportional directional switching valve and the hydraulic cylinder, and a shut-off position that blocks the flow of hydraulic oil between the electromagnetic proportional directional switching valve and the hydraulic cylinder; An electromagnetic shut-off valve having an open position that permits the flow of hydraulic oil between the electromagnetic proportional direction switching valve and the hydraulic cylinder;
With
A control device for controlling the operation by outputting a control signal to the hydraulic control device,
When starting hydraulic oil supply from the hydraulic pump to the hydraulic cylinder, a signal for operating the hydraulic pump, a signal for switching the electromagnetic proportional directional switching valve from the neutral position to the supply position, A signal for switching the electromagnetic shutoff valve from the shut-off position to the open position at a first timing;
When stopping the hydraulic oil supply from the hydraulic pump to the hydraulic cylinder, after outputting a signal for returning the electromagnetic proportional directional switching valve from the supply position to the neutral position at a second timing, the hydraulic pump And a signal for switching the electromagnetic shutoff valve from the open position to the shut-off position at a third timing,
When the hydraulic oil is discharged from the hydraulic cylinder, a signal for switching the electromagnetic proportional directional switching valve from the neutral position to the discharge position and the electromagnetic shutoff valve are switched from the shut-off position to the open position. A signal for output at the fourth timing,
When stopping the hydraulic oil discharge from the hydraulic cylinder, after outputting a signal for switching the electromagnetic proportional direction switching valve from the discharge position to the neutral position at the fifth timing, the electromagnetic shut-off valve is Outputting a signal for switching from the opening position to the blocking position at a sixth timing;
The double deck elevator according to claim 1. The supply line is located between the electromagnetic proportional direction switching valve and the electromagnetic shutoff valve, and limits the amount of hydraulic oil supplied to the hydraulic cylinder to a predetermined first oil amount. And a first throttle valve for limiting the amount of hydraulic oil discharged from the hydraulic cylinder to a predetermined second oil amount,
The double deck elevator according to claim 3.

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