JPH0664446A - Wing opening closing device - Google Patents

Abstract

PURPOSE:To prevent a wing from being twisted, and also prevent other component parts from being damaged by interposing respective pilot check valves for both of ascent drive side branch paths in such a way that mutual communication between both of ascent drive side cylinder chambers is checked CONSTITUTION:Pilot check valves 17 and 27 checking communication with each ascent drive side cylinder chamber 13 and 23 are connected fore and aft to each ascent drive side branch path 15 and 25, and a pilot circuit is connected to a second suction and exhaust path 42. In addition, pressure compensation type flow rate control valves 18 and 28 securing each constant flow rate are disposed at each descent drive side branch path 16 and 26. And when a front and a rear cylinder means 10 and 20 are different in load from each other, the flow of pressure oil from a high side to a lower side is checked by the respective pilot check valves 17 and 27. Moreover, the operating speeds of the front and rear cylinder means 10 and 20 are controlled to be constant by the respective pressure compensation type flow rate control valves 18 and 28. Therefore, a wing is prevented from being twisted.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a wing opening / closing device, and more particularly, to a wing opening / closing device in which a wing is opened / closed by a pair of hydraulic cylinder devices, and is effectively applied to a wing opening / closing device in a wing vehicle, for example. Regarding things.

[0002]

2. Description of the Related Art Generally, a so-called wing vehicle in which left and right side walls of a container are configured to open and close in a gull wing shape is known as a luggage vehicle that facilitates loading and unloading work of a container vehicle.

Conventionally, there is a wing opening / closing device for driving a wing of a wing vehicle to be opened / closed by a hydraulic cylinder device as follows. That is,
In this wing opening / closing device, the upper side of the wing is rotatably supported on the side wall of the container, and a pair of hydraulic pressures are provided before and after the wing is arranged on the front side and the rear side, respectively, on both sides in the rotation axis direction of the container. It is configured to be simultaneously opened and closed by a cylinder device.

A hydraulic circuit for driving and controlling the hydraulic cylinder device before and after this is connected to a supply passage connected to a hydraulic pump, a discharge passage connected to a reservoir, and a supply passage and a discharge passage. And a pair of supply / discharge passages connected to the load port of the directional control valve to control connection with the supply passage and the discharge passage, and branched from one of the supply / discharge passages. A pair of ascending drive side branch passages connected to each of the ascending drive side cylinder chambers of both hydraulic cylinder devices and a pair of ascending drive side cylinder chambers of the two hydraulic cylinder devices respectively branched from the supply / discharge passages. And a pair of descending side branch paths connected to each other.

When pressure oil from the hydraulic pump is simultaneously supplied to the ascending drive side cylinder chambers of the front and rear hydraulic cylinder devices, the front and rear hydraulic cylinder devices synchronously extend, so that the wings rise horizontally. And then open.

When pressure oil from the hydraulic pump is simultaneously supplied to the descending drive side cylinder chambers of the front and rear hydraulic cylinder devices, the front and rear hydraulic cylinder devices are synchronously shortened, so that the wings descend horizontally. And closes.

[0007]

However, in the above-mentioned conventional wing opening / closing device, an error occurs in the synchronization of the ascending operation and the descending operation of the front and rear hydraulic cylinder devices, so that the wing is twisted and the wing and There is a problem that other components are damaged.

An object of the present invention is to provide a wing opening / closing device capable of synchronizing a pair of hydraulic cylinder devices for driving the opening / closing of the wings.

[0009]

In the wing opening / closing device according to the present invention, the upper end side of the wing is rotatably supported by the fixed wall, and the wings are arranged on both sides of the fixed wall in the rotation axis direction. It is configured to be opened and closed simultaneously by a pair of hydraulic cylinder devices,
The drive control hydraulic circuits of both hydraulic cylinder devices include a supply passage connected to the hydraulic supply device, a discharge passage connected to the reservoir, a directional control valve connected to the supply passage and the discharge passage, and this direction. Connected to the load port of the control valve,
A pair of supply / discharge paths whose connection to the supply path and the discharge path is controlled, and a pair of lifts branched from one of the supply / discharge paths and connected to the lift drive side cylinder chambers of the hydraulic cylinder devices. A wing opening / closing device including a drive-side branch passage and a pair of descending-side branch passages branched from the other supply / discharge passage and connected to the descending drive-side cylinder chambers of the hydraulic cylinder devices, respectively. Each pilot check valve on both of the ascending drive side branch path,
The ascending drive side cylinder chambers are respectively provided so as to prevent them from communicating with each other, and the pilot circuits of both pilot check valves are connected to the other supply / discharge path to which the descending drive side branch path is connected. Further, a pressure compensation type flow control valve for controlling a constant flow rate regardless of the pressure fluctuation of each cylinder chamber is provided in at least one of both the descending drive side branch passage and the ascending drive side branch passage. Wing switchgear characterized by being connected to each other.

[0010]

According to the above-mentioned means, when the open and closed states of the wings are maintained, both of the cylinder chambers of both hydraulic cylinder devices are connected to the reservoir via the directional control valve. Has become.

In this state, when loads of different magnitudes are applied to both hydraulic cylinder devices, the ascending drive side cylinder chambers of both hydraulic cylinder devices communicate with each other only in the ascending drive side branch passage. Since it is blocked by each pilot check valve installed respectively,
Both hydraulic cylinder devices are in a state of independently holding a load. Therefore, both hydraulic cylinder devices can always support the wings in a constant horizontal state regardless of the difference in the load applied to the wings.

When the directional control valve is switched when the wing is closed from the open state, both of the descending drive side cylinder chambers are connected to the supply passage via the descending drive side branch passages and one of the supply / discharge passages, respectively. Hydraulic pressure is supplied to each of the descending drive side cylinder chambers.

On the other hand, when the directional control valve is switched, pressure oil is supplied to the pilot circuits of both pilot check valves, so that the flow in the direction opposite to that of both pilot check valves is allowed. As a result, the pressure oil in the ascending drive side cylinder chambers of both hydraulic cylinder devices is discharged to the reservoir through both pilot check valves and direction control valves.

By the above operation, both hydraulic cylinder devices are shortened, so that the wings are lowered and closed. At this time, regardless of the difference in load applied to both ends of the wing, both hydraulic cylinder devices are shortened by the pressure compensation type flow control valve at a constant flow rate, so that the both ends of the wing descend at the same speed. become. Therefore, it is possible to prevent the wings from being twisted or damaged.

[0015]

1 is a circuit diagram showing a wing opening / closing device for a wing vehicle which is an embodiment of the present invention, and FIG. 2 is a perspective view showing the wing vehicle.

In the present embodiment, the wing opening / closing device according to the present invention is mounted on a wing vehicle. This wing car 1 is a container 3 mounted on the bed of a truck 2.
A pair of wings 5 are rotatably supported by a support shaft 4 on the left and right side walls of the container 3, and are installed so as to open and close diagonally upward in a gull wing form.

Since the left and right wings 5, 5 are symmetrically arranged with the same structure,
The wing 5 on the left side will be representatively described.

On the front and rear walls of the container 3, a pair of front and rear hydraulic cylinder devices 10 and 20 are arranged upward, respectively, and the front and rear hydraulic cylinder devices 10 and 20 are rotatably attached to the container 3 on their cylinder sides. It is pivotally attached. The piston rod 11 of the front hydraulic cylinder device 10 is rotatably pivoted to the front end of the wing 5, and the piston rod 21 of the rear hydraulic cylinder device 20 is rotatably pivoted to the rear end of the wing 5. Has been done. Therefore, the wings 5 are driven to open and close by the expansion and contraction operations of the front and rear hydraulic cylinder devices 10 and 20.

The drive of both hydraulic cylinder devices 10 and 20 is controlled by a hydraulic circuit 30 of one system. That is, this hydraulic circuit 30
Includes a supply passage 31 in which a hydraulic pump 32 as a hydraulic supply device is provided, and a discharge passage 34 connected to a reservoir 35. The hydraulic pump 32 is the electric motor 3
It is configured to be rotationally driven by 3. A filter 36 and a relief valve 37 are provided in the discharge passage 34. A relief valve 38 is provided between the supply passage 31 and the discharge passage 34.

A directional control valve 40 is connected to the supply passage 31 and the discharge passage 34. In this embodiment, the directional control valve 40 is configured as a 4-port / 3-position / ABR connection / spring center / electromagnetic switching valve. The first supply / discharge path 41 is connected to the A port that is one load port of the directional control valve 40, and the second supply / discharge path 42 is connected to the B port that is the other load port of the directional control valve 40.

The first supply / discharge passage 41 has a throttle valve 4 with a check valve.
3 is interposed, and the check valve of the check valve-equipped throttle valve 43 is configured to prevent the backflow to the load port A. Further, a pilot check valve (hereinafter also referred to as a main pilot check valve) 44 is provided in the second supply / discharge passage 42, and the pilot circuit 44a of the main pilot check valve 44 has a first supply / discharge passage. Direction control valve 40 of throttle valve with check valve 43 in 41
Connected to the side.

On the other hand, the cylinder chamber of the front hydraulic cylinder device 10 is partitioned by the piston 12 into an ascending drive side cylinder chamber 13 and a descending drive side cylinder chamber 14. A front raising drive side branch passage 15 is connected to the raising drive side cylinder chamber 13, and a front side lowering drive side branch passage 16 is connected to the lowering drive side cylinder chamber 14.

Similarly, the cylinder chamber of the rear hydraulic cylinder device 20 is partitioned by the piston 22 into an ascending drive side cylinder chamber 23 and a descending drive side cylinder chamber 24.
In the ascending drive side cylinder chamber 23, the rear ascending drive side branch passage 2 is provided.
5 is connected to the lower drive side cylinder chamber 24, and a rear lower drive side branch path 26 is connected to the lower drive side cylinder chamber 24.

The front upward drive side branch passage 15 and the rear upward drive side branch passage 25 are connected to the first supply / discharge passage 41 on the opposite side of the direction control valve 40 of the check valve-equipped throttle valve 43. Accordingly, the ascending drive side branch paths 15 and 25 are substantially branched from the first supply / discharge path 41.

Similarly, the front descending drive side branch passage 16 and the rear side descending drive side branch passage 26 are respectively connected to the second supply / discharge passage 42 on the side opposite to the direction control valve 40 of the main pilot check valve 44. Thus, the two descending drive side branch paths 16 and 26 are substantially branched from the second supply / discharge path 42.

In the present embodiment, a front pilot check valve 17 is provided in the front ascending drive side branch passage 15 at a position near the front side ascending drive side cylinder chamber 13 at the branch point.
The check valve 17a of the pilot check valve 17 is configured to prevent discharge of the pressure oil from the front rising drive side cylinder chamber 13. The pilot circuit 17b of the front pilot check valve 17 is connected to the directional control valve 40 side of the main pilot check valve 44 in the second supply / discharge passage 42.

Similarly, a rear pilot check valve 27 is provided in the rear upward drive side branch passage 25 at a position close to the rear upward drive side cylinder chamber 23 at the branch point. The check valve 27a of the rear pilot check valve 27 is configured to prevent discharge of pressure oil from the rear rising drive side cylinder chamber 23. Further, the pilot circuit 27b of the rear pilot check valve 27 is provided with the directional control valve 4 of the main pilot check valve 44 in the second supply / discharge passage 42.
It is connected to the 0 side.

A front pressure compensating flow control valve 18 is provided in the front lowering drive side branch passage 16 at a position near the front lowering drive side cylinder chamber 14 at the branch point. The pressure compensation type flow control valve 18 can compensate the pressure fluctuation in the front lowering drive side cylinder chamber 14 and supply the pressure oil from the second supply / discharge passage 42 to the front lowering drive side cylinder chamber 14 at a constant flow rate. Is configured. Therefore, the front hydraulic cylinder device 10 can be shortened at a constant speed regardless of the change in load due to the wings 5 acting on the piston rod 11.

Similarly, a rear pressure compensating type flow control valve 28 is provided in the rear descending drive side branch passage 26 at a position close to the rear descending drive side cylinder chamber 24 at the branch point. The pressure-compensating flow control valve 28 compensates for pressure fluctuations in the rear descending drive side cylinder chamber 24 and supplies the pressure oil from the second supply / discharge passage 42 to the rear descending drive side cylinder chamber 24 at a constant flow rate. Is configured to be able to. Therefore, the rear hydraulic cylinder device 20 can be shortened at a constant speed regardless of the change in load due to the wings 5 acting on the piston rod 21.

Reference numeral 19 is a throttle valve provided in the front upward drive side branch passage 15, and 29 is a throttle valve provided in the rear upward drive side branch passage 25.

Next, the operation will be described. During traveling of the wing car 1, the wings 5 are kept closed so as to seal the container 3. At this time, the front and rear hydraulic cylinder devices 10 and 20 are maintained in the shortened state, and the directional control valve 40
Is maintained in a neutral position.

In this state, for example, when a negative pressure acts on the wing 5 closed by the passage of an oncoming vehicle and a force that pulls up the piston rods 11 and 21 acts on both hydraulic cylinder devices 10 and 20, The pressure oil tries to escape from the both lower drive side cylinder chambers 14 and 24. However, since the reverse flow is blocked by the main pilot check valve 44 provided in the second supply / discharge path 42, the discharge of the pressure oil from both the descending drive side cylinder chambers 14 and 24 is blocked. Therefore, when the oncoming vehicle passes, the wing 5
Will be prevented from opening accidentally.

When the wings 5 are opened during the operation of loading and unloading the container 3, the directional control valve 40
Is switched to a wing raising operating position in which the P port is connected to the A port and the R port is connected to the B port.

At this wing raising operation position, the pressure oil of the hydraulic pump 32 is supplied to the front rising drive side cylinder chamber 13 and the rear rising drive side cylinder chamber 23 in the supply passage 31 → direction control valve 40 → first supply / discharge passage 41. → Throttle valve with check valve 43
→ Front rise drive side branch passage 15 and rear rise drive side branch passage 25 → Front pilot check valve 17 and rear pilot check valve 27 → Supply through front throttle valve 19 and rear throttle valve 29, respectively .

On the other hand, the pressure oil in the descent drive side cylinder chamber 14 of the front hydraulic cylinder device 10 and the descent drive side cylinder chamber 24 of the rear hydraulic cylinder device 20 is stored in the reservoir 35, and the front descent drive side branch passage 16 and the rear descent are provided. Drive side branch 2
6 → Check valve 18a of front pressure compensation type flow control valve 18
And the check valve 28 of the rear pressure compensation type flow control valve 28
a → second supply / discharge passage 42 → main pilot check valve 44
-> The directional control valve 40 and the discharge passage 34 are discharged respectively.

At this time, the main pilot check valve 44 provided in the second supply / discharge path 42 is in a state in which the reverse flow is allowed because the hydraulic pressure of the first supply / discharge path 41 is introduced by the pilot circuit 44a. ing.

The front and rear hydraulic cylinder devices 10 and 20 are extended by the above-described pressure oil supply operation and discharge operation, so that the wing 5 has both hydraulic cylinder devices 10, 20.
The front and rear are simultaneously raised by 20 piston rods 11 and 21, and are horizontally opened with respect to the container 3.

When the wings 5 are raised to a predetermined opening, the directional control valve 40 is returned to the neutral position. In this state of the neutral position, the same holding state as that at the time of closing described above is created, so that the wing 5 can be kept open at a predetermined opening degree.

When the wings 5 are raised to a predetermined position, the mechanical locking device (not shown) mechanically moves the piston rods 11 and 21 of both hydraulic cylinder devices 10 and 20 or the front and rear of the wings 5. Supported by. Due to the mechanical support by the locking device, the wing 5 and both hydraulic cylinder devices 10 and 20 are reliably and evenly supported in the front-rear direction.

Then, when the opened wing 5 is closed, the directional control valve 40 changes the P port to the B port,
The R port is switched to the wing lowering operating position which is connected to the A port respectively.

In this switching operation position (wing lowering operation position), the pressure oil in the ascending drive side cylinder chamber 13 of the hydraulic cylinder device 10 and the ascending drive side cylinder chamber 23 of the rear hydraulic cylinder device 20 is stored in the reservoir 35 and in the front side. Ascending drive side branch 15 and rear ascending drive side branch 25 →
The gas is discharged via the front pilot check valve 17 and the rear pilot check valve 27 → the first supply / discharge passage 41 → the direction control valve 40 → the discharge passage 34.

At this time, both ascending drive side branch paths 15 and 2
Pilot check valve 17 installed in each of 5
Since the hydraulic pressures of the second supply / discharge passage 42 are introduced into pilots 27 and 27 by the pilot circuits 17b and 27b, respectively, the backflow is allowed.

On the other hand, the pressure oil of the hydraulic pump 32 is supplied to the lower drive side cylinder chamber 14 of the front hydraulic cylinder device 10 and the lower drive side cylinder chamber 24 of the rear hydraulic cylinder device 20.
Supply path 31 → directional control valve 40 → second supply / discharge path 42 → main pilot check valve 44 → front side downward drive side branch path 16
And the rear downward drive side branch path 26 → the front side pressure compensation type flow rate control valve 18 and the rear side pressure compensation type flow rate control valve 28, respectively.

At this time, the front pressure-compensating flow control valve 18 and the rear pressure-compensating flow control valve 28 are provided in the front lower drive side branch passage 16 and the rear lower drive side branch passage 26, respectively. Despite the pressure fluctuations in the front-side descent driving-side cylinder chamber 14 and the rear-side descent-driving-side cylinder chamber 24, the pressure oil of the hydraulic pump 32 flows into the front-side descent-driving-side cylinder chamber 14 and the rear-side descent-driving-side cylinder chamber 24, respectively. It will be supplied at a constant flow rate.

Since the hydraulic cylinder devices 10 and 20 at the front and rear are simultaneously shortened at a constant speed by the discharge operation and the supply operation of the pressure oil described above, the wing 5 has piston rods 11 and 21 of both hydraulic cylinder devices 10 and 20. Thus, the front and rear are simultaneously lowered at a constant speed and horizontally closed with respect to the container 3.

The front and rear hydraulic cylinder devices 10, 2
At the time of the descent operation of 0, both ascending drive side branch paths 15 and 25
Since the throttle valves 19 and 29 and the check valve-equipped throttle valve 43 are provided in the first supply / discharge passage 41, respectively, the lowering speed of the wing 5 is sufficiently suppressed. Therefore, the danger due to the sudden lowering of the wing 5 is eliminated.

When the wings 5 are completely closed, the directional control valve 40 is returned to the neutral position, and the original closed state described above is created.

Here, when it is desired to maintain the open state of the wings 5 at an intermediate opening, the following operation is executed. First, the wings 5 are fully opened and mechanically supported by the mechanical locking device. After this, the directional control valve 4
0 is switched to the wing lowering operation position, wing 5
The directional control valve 40 is switched to the neutral position when the desired opening degree is reached.

As described above, even when the open state of the wings 5 is stopped at an intermediate opening and the directional control valve 40 is switched to the neutral position, the wings 5 are moved forward and backward as in the holding state at the time of closing described above. The halfway opened state is maintained by the hydraulic cylinder devices 10 and 20.

By the way, the front and rear hydraulic cylinders are maintained while maintaining the closed state and the midway open state of the wing 5, during the transition of the wing 5 from closed to open, and during the transition of the wing 5 from open to closed. Devices 10 and 20
When different loads are applied to the wing 5 or an error occurs in the synchronous operation between the front and rear hydraulic cylinder devices 10 and 20, the wing 5 is twisted. There is a risk of being damaged.

The following cases can be listed as causes of such a case. The wind pressure acting on the wing 5 becomes irregular before and after,
When different external forces are applied to the wing 5 before and after, or when different amounts of snow are accumulated before and after the wing 5, and when the internal strain of the wing 5 and the resistance of the support shaft are different before and after. , Different loads are applied between the front and rear hydraulic cylinder devices 10 and 20.

When the wings 5 are raised and lowered, especially when the wings 5 are lowered, the loads applied to the front and rear hydraulic cylinder devices 10, 20 and the sliding resistance of the front and rear hydraulic cylinder devices are different. As a result, a difference occurs in the flow rate of the pressure oil supplied to the front and rear hydraulic cylinder devices 10 and 20, respectively, so that a stroke difference occurs in the front and rear hydraulic cylinder devices 10 and 20.

When the wing 5 is lowered, if there is a difference in the amount of discharged oil between the front and rear hydraulic cylinder devices 10 and 20, a stroke difference occurs between the front and rear hydraulic cylinder devices 10 and 20.

If the loads acting on the front hydraulic cylinder device 10 and the rear hydraulic cylinder device 20 are different while the wing 5 is maintained in the open state with a halfway opening, the front rising drive side cylinder chamber 13 and When the rear ascending drive side cylinder chamber 23 is in communication, one having a larger cylinder holding pressure, for example, the ascending drive side cylinder chamber 13 on the front hydraulic cylinder device 10 side under a large load,
When the cylinder holding pressure is smaller, for example, pressure oil flows into the ascending drive side cylinder chamber 23 on the rear cylinder device 20 side where a small load is applied, the pressure oil flows between the front and rear hydraulic cylinder devices 10 and 20. Stroke difference will occur.

However, in this embodiment, the front pilot drive valve 17 and the rear pilot drive valve 27 are provided in the front ascending drive side branch passage 15 and the rear side ascending drive side branch passage 25, respectively. Since the rear rising drive side cylinder chambers 23 are respectively provided so as to prevent them from communicating with each other, as described above,
Front hydraulic cylinder device 10 and rear hydraulic cylinder device 20
Even when different loads are applied between and, the ascending drive side of the hydraulic cylinder device to which a large load is applied is moved from the ascending drive side cylinder chamber 13 or 23 of the hydraulic cylinder device to which a small load is applied. Cylinder chamber 23 or 1
No pressure oil will flow into 3.

Therefore, even when different loads are applied between the front hydraulic cylinder device 10 and the rear hydraulic cylinder device 20, a stroke difference occurs between the front and rear hydraulic cylinder devices 10 and 20. There is nothing to do.

For example, when a large load F ₁ is applied to the front hydraulic cylinder device 10 and a small load F ₂ is applied to the rear hydraulic cylinder device 20 with the wings 5 open midway, the front hydraulic cylinder device 10 is driven upward. Pressure oil tries to flow from the side cylinder chamber 13 toward the ascending drive side cylinder chamber 23 of the rear hydraulic cylinder device 20, but the pressure oil is supplied by the pilot check valve 17 provided in the front ascending drive side branch passage 15. Rear rise drive side branch 2
Since the reverse flow in the direction of 5 is blocked, it cannot flow into the rear side ascending drive side cylinder chamber 24.

Further, in this embodiment, a front pressure compensation type flow rate control valve 18 and a rear pressure compensation type flow rate control valve 28 are provided in the front side descending drive side branch passage 16 and the rear side descending drive side branch passage 26, respectively. Therefore, even when different loads are applied between the front and rear hydraulic cylinder devices 10 and 20 when the wings 5 are lowered,
The front and rear hydraulic cylinder devices 10 and 20 can be shortened without causing a stroke difference.

That is, the front side pressure compensation type flow control valve 18
A constant flow rate of pressure oil is supplied to the front lowering drive side cylinder chamber 14, and a constant flow rate of pressure oil is supplied to the rear side lowering drive side cylinder chamber 24 by the rear side pressure compensation type flow control valve 28. Therefore, the front hydraulic cylinder device 1
0 and the hydraulic cylinder device 20 on the rear side are shortened at the same constant speed. Therefore,
It is possible to prevent the wing 5 from being twisted or damaged.

According to the above embodiment, the following effects can be obtained. When the opened state of the wing 5 is held by the front and rear cylinder devices 10 and 20, it is possible to prevent a screw from being generated.

Since it is possible to prevent the variation in the supply flow rate and the discharge flow rate of the pressure oil to the front and rear cylinder devices 10 and 20, and the variation due to the change in the flow rate over time, it is possible to prevent the variation between the front and rear cylinder devices 10 and 20. The accuracy of synchronization can be improved.

By ensuring the synchronization of the front and rear cylinder devices 10 and 20 when the wing 5 is raised and lowered, the wing 5 can be prevented from being twisted, and therefore the wing 5 and other parts are prevented from being damaged. can do.

FIG. 3 is a circuit diagram showing a wing opening / closing device which is Embodiment 2 of the present invention.

The second embodiment differs from the first embodiment in that
The front side pressure compensation type flow control valve 18A is provided on the ascending drive side cylinder chamber 13 side of the pilot check valve 17 in the front side ascending drive side branch passage 15 from the ascending drive side cylinder chamber 13 regardless of the pressure fluctuation of the ascending drive side cylinder chamber 13. Is installed so as to control the discharge flow rate of the pressure oil at a constant level. Similarly, the rear side pressure compensation type flow rate control valve 28A is provided on the rear side ascending drive side branch passage 25 for ascending drive side cylinder On the chamber 23 side, the ascending drive side cylinder chamber 23
The point is that the discharge flow rate of the pressure oil from the ascending drive side cylinder chamber 23 is controlled to be constant regardless of the pressure fluctuation.

In the second embodiment, in the shortening operation of the front and rear hydraulic cylinder devices 10 and 20, when the pressure oil is discharged from the ascending drive side cylinder chamber 13 of the front hydraulic cylinder device 10, the front pressure compensating flow rate is set. Control valve 18
Since the discharge flow rate is controlled to be constant by A, the descending speed of the piston rod 11 is controlled to a constant speed. Similarly, the rear hydraulic cylinder device 2
When the pressure oil is discharged from the ascending drive side cylinder chamber 23 of 0, the rear side pressure compensation type flow rate control valve 28A controls so that the discharge flow rate becomes constant, so that the descending speed of the piston rod 21 is a constant speed. Will be controlled by.

Therefore, according to the second embodiment, as in the first embodiment, when the wings 5 are lowered, different loads are applied between the front and rear hydraulic cylinder devices 10 and 20. Even if there is, the front and rear hydraulic cylinder devices 10 and 20 can be shortened without causing a stroke difference. Therefore, even when different loads are applied between the front and rear hydraulic cylinder devices 10 and 20, the wing 5 can be prevented from being twisted or damaged.

FIG. 4 is a circuit diagram showing a wing opening / closing device which is Embodiment 3 of the present invention.

The third embodiment differs from the first embodiment in that
In addition to the pressure-compensated flow control valves 18 and 28 being provided in the descending drive-side branch passages 16 and 26, respectively, the front side pressure-compensating flow control valve 18A is used in the pilot check in the front-side ascending drive-side branch passage 15. The valve 17 is provided on the ascending drive side cylinder chamber 13 side so as to control the discharge flow rate of the pressure oil from the ascending drive side cylinder chamber 13 to be constant regardless of the pressure fluctuation of the ascending drive side cylinder chamber 13. Similarly, the rear pressure compensation type flow control valve 28A is connected to the pilot check valve 27 in the front rising drive side branch passage 25.
To the ascending drive side cylinder chamber 23 side regardless of the pressure fluctuation of the ascending drive side cylinder chamber 23.
It is provided so as to control the discharge flow rate of the pressure oil from No. 3 to be constant.

In the third embodiment, in the shortening operation of the front and rear hydraulic cylinder devices 10 and 20, the supply oil flow rate and the discharge oil flow rate of the front hydraulic cylinder device 10 are controlled by the front pressure compensation type flow control valves 18 and 18A. Since the piston rod 11 is controlled to be constant, the descending speed of the piston rod 11 is controlled to be constant. Similarly, since the supply oil flow rate and the discharge oil flow rate of the rear hydraulic cylinder device 20 are controlled to be constant by the rear pressure compensation type flow control valves 28 and 28A, the descending speed of the piston rod 21 is constant. It will be controlled by speed.

Therefore, according to the third embodiment, as in the first embodiment, when the wings 5 are lowered, different loads are applied between the front and rear hydraulic cylinder devices 10 and 20. Even if there is, the front and rear hydraulic cylinder devices 10 and 20 can be shortened without causing a stroke difference. Therefore, even when different loads are applied between the front and rear hydraulic cylinder devices 10 and 20, the wing 5 can be prevented from being twisted or damaged.

[0071]

As described above, according to the present invention,
Since the pair of hydraulic cylinder devices can be operated in synchronization and the inflow of pressure oil from one hydraulic cylinder device to the other hydraulic cylinder device can be prevented, the wing is twisted, and the wings and other It is possible to prevent damage to the components.

[Brief description of drawings]

FIG. 1 is a circuit diagram showing a wing opening / closing device for a wing car that is an embodiment of the present invention.

FIG. 2 is a perspective view showing a wing car.

FIG. 3 is a circuit diagram showing a wing opening / closing device that is Embodiment 2 of the present invention.

FIG. 4 is a circuit diagram showing a wing opening / closing device that is Embodiment 3 of the present invention.

[Explanation of symbols]

1 ... Wing vehicle, 2 ... Truck, 3 ... Container, 4 ... Support shaft, 5 ... Wing, 10 ... Front hydraulic cylinder device, 11
... piston rod, 12 ... piston, 13 ... front rising drive side cylinder chamber, 14 ... front falling drive side cylinder chamber, 1
5 ... Front rising drive side branch passage, 16 ... Front side descending drive side branch passage, 17 ... Pilot check valve, 17a ... Check valve, 17b ... Pilot circuit, 18, 18A ... Front side pressure compensation type flow control valve, 18a ... Check valve , 19 ... Front throttle valve, 20 ... Rear hydraulic cylinder device, 21 ... Piston rod, 22 ... Piston, 23 ... Rear rising drive side cylinder chamber, 24 ... Rear falling drive side cylinder chamber, 25 ... Rear rising drive Side branch passage, 26 ... Rearward descent drive side branch passage, 27 ... Pilot check valve, 27a ... Check valve, 27b ... Pilot circuit, 28, 28A ... Rear pressure compensation type flow control valve, 29 ... Rear throttle valve, 30 ... Hydraulic circuit, 31 ... Supply path, 32 ... Hydraulic pump, 33 ... Electric motor, 34 ... Discharge path, 35 ... Reservoir, 36 ... Filter, 37 ... Relief valve, 38 ... Relief valve 40 ... directional control valve, 41 ... first
Supply / discharge passage, 42 ... Second supply / discharge passage, 43 ... Throttle valve with check valve, 44 ... Pilot check valve, 44a ... Pilot circuit.

Claims (1)

[Claims] 1. An upper end side of a wing is rotatably supported by a fixed wall, and the wing is simultaneously opened and closed by a pair of hydraulic cylinder devices arranged on both sides of the fixed wall in the rotational axis direction. The drive control hydraulic circuits of both hydraulic cylinder devices are configured to have a supply passage connected to the hydraulic supply device, a discharge passage connected to the reservoir, and a direction in which the supply passage and the discharge passage are connected. A control valve, a pair of supply / discharge passages connected to the load port of the directional control valve and controlled to connect to the supply passage and the discharge passage, and one of the supply / discharge passages branched from the supply / discharge passages. Of the ascending drive side cylinder chambers, and a pair of the ascending drive side branch passages and the other supply / discharge passages, which are branched from the other supply / discharge passages, respectively, A wing opening / closing device having a pair of descending side branch paths connected to each of them, wherein each pilot check valve in both of the ascending drive side branch paths prevents the ascending drive side cylinder chambers from communicating with each other. And the pilot circuits of both pilot check valves are connected to the other supply / discharge path to which the descending drive side branch path is connected, and both of the descending drive side branch paths are connected. A wing opening / closing device, wherein a pressure compensation type flow control valve for controlling a constant flow rate regardless of pressure fluctuations in the cylinder chambers is connected to at least one of the rising drive side branch passage and the rising drive side branch passage. .