JP2505833Y2 - Lift cylinder lowering control device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION [Industrial field of application] The present invention relates to a lowering control device for a lift cylinder, and is used, for example, for lowering control of a fork of a forklift truck.

[Conventional technology]

Japanese Patent Publication No. 61-14722 discloses a lowering control device having both a function of mitigating an impact at a lowering end of a piston of a lift cylinder and a function of preventing a sudden drop due to damage of hydraulic piping.

As shown in FIGS. 9 and 10, a fixed cylinder 103 is attached to the inside of a block 102 attached to the lower part of a cylinder tube 101, and the movable cylinder 10 is attached to the fixed cylinder 103.
4 is inserted vertically. Also, the movable cylinder 1
A spring 105 that biases 04 upward is provided.

A plurality of openings are provided on the outer periphery of the movable cylinder 104,
The throttle channel 106 is formed by this opening. Also,
On the outer circumference of the fixed cylinder 103, a plurality of openings are provided vertically in parallel, and the openings form the throttle channels 107, 108, and 109.

Further, the block 102 is formed with a connection port 110 for connection with a flow rate control valve for lowering speed control (not shown).

Further, a cylindrical valve body 111 that constitutes a check valve is vertically movably inserted into the lower portion of the fixed cylindrical body 103.
11 is pressed against the plug 115 by the spring 105. Further, a through hole 114 communicating with the lower side of the valve body 111 is formed in the fixed cylindrical body 103.

As a result, the oil chamber 113 below the piston 112 and the flow control valve are connected via the throttle passages 106, 107, 108 and 109.

According to the above configuration, as shown in FIG.
At the time of rising, the pressure oil flows into the lift cylinder through the connection port 110, and this pressure oil reaches the inside of the fixed cylindrical body 103 from the throttle channels 107, 108, 109. Further, since the pressure oil pushes up the valve body 111, the pressure oil reaches the inside of the fixed cylindrical body 103 from the through hole 114.
Then, the pressure oil flows from the inside of the fixed cylinder 103 into the oil chamber 113 through the throttle passage 106 and pushes up the piston 112.

Further, when the piston 112 descends, the pressure oil flows from the oil chamber 113 to the inside of the fixed cylindrical body 103 through the throttle flow passage 106, passes through the throttle flow passages 107, 108 and 109, and is discharged from the connection port 110 to the outside of the lift cylinder. To be done. At this time, the valve body 111 is pressed against the bottom surface of the block 102. Since it is dangerous when the descending speed of the piston 112 is high, the flow rate control valve for connecting the descending speed is provided and the connecting port 110 of the lift cylinder is provided.
The flow rate of oil discharged from is the control flow rate of the flow rate control valve. At this time, the discharged oil is not throttled in the throttle channels 106, 107, 108, 109.

When the piston 112 further descends, the movable cylinder 1
04 will be pushed down. The movable cylinder 104 pushed down sequentially closes the throttle channels 107 and 108, and the oil that has passed through the throttle channel 106 to reach the inside of the fixed cylinder 103 is finally opened 109.
Will be discharged from the lift cylinder only. As a result, the oil discharged from the lift cylinder is throttled, the descending speed of the piston 112 is reduced near the descending end, and impact is prevented from occurring at the descending end.

Further, when the pipe connecting the connection port 110 and the flow rate control valve is damaged, the flow rate of oil discharged from the connection port 110 of the lift cylinder becomes larger than the control flow rate of the flow rate control valve.

Then, the discharged oil is throttled in the throttle passage 106 of the movable tubular body 104, a pressure difference is generated between the upstream side and the downstream side of the throttle portion, and the movable tubular body 104 descends due to this pressure difference. As a result, the movable cylinder 104 that descends reduces the openings of the throttle channels 107 and 108, so that the flow rate of oil discharged from the lift cylinder is reduced, and the piston 112 is prevented from falling suddenly.

[Problems to be solved by the device]

If the descending speed of the lift cylinder is too fast, it is dangerous, but if it is too slow, the work efficiency decreases. Therefore, the descending speed determined by the control flow rate of the descending speed controlling flow control valve is set to a value higher than a certain value until it is decelerated near the descending end to reduce the impact.

On the other hand, if the pipe between the lift cylinder and its flow control valve is damaged, the lift cylinder becomes uncontrollable, so the lowering speed in normal use, that is, the control of the flow control valve It is preferable for safety that the lowering speed is lower than the lowering speed determined by the flow rate, and in the actual use of the forklift truck and the like, the lowering speed is actually set in this way.

However, in the above-described conventional descending speed control device, the descending speed in the case where the pipe is damaged cannot be made smaller than the descending speed in the normal use state, and thus is not sufficient for practical use. .

That is, in the above-mentioned conventional example, when the flow rate of the oil discharged from the lift cylinder becomes excessive due to the damage of the pipe or the like, the movable tubular body 104 once descends due to the pressure difference between the upstream and downstream sides of the throttle flow passage 106 and the throttle flow. The roads 107 and 108 are closed. As a result, the oil that has reached the inside of the fixed cylindrical body 103 through the throttle channel 106 is once discharged from the lift cylinder only through the throttle channel 109, and the discharged oil flow rate is once greatly reduced. .

However, the throttle channel 106 is provided between the oil chamber 113 and the movable cylinder 104.
Because it is in continuous communication with, the movable cylinder 104 rises,
The discharged oil flow rate is at least equal to or higher than the control flow rate of the descending speed control flow rate control valve. This is because if the throttling degree of the throttle passage 106 and the elastic force of the spring 105 are set so that the movable cylindrical body 104 descends at a flow rate lower than the control flow rate of the flow rate control valve, the pipe will be damaged. Even in a normal descending state where there is no such difference, the movable cylindrical body 104 descends, and the throttle channels 107, 108
As a result, the flow rate of the oil discharged from the lift cylinder becomes smaller than the control flow rate of the flow control valve. That is, in the normal use state, the piston 112 cannot be lowered at the lowering speed determined by the control flow rate of the lowering speed control flow control valve. Therefore, in the related art, the descending speed when the pipe is damaged is at least the normal descending speed, which is not preferable for safety.

Furthermore, it is preferable from the safety point of view that the descent rate during sudden drop prevention when the pipe is damaged is lower than the descent rate in the normal state as described above. Since the difference becomes too large and a large impact is generated, for example, there is a possibility that a load collapse may occur. Therefore, it is not preferable that the speed difference before and after the sudden drop prevention becomes too large.

On the other hand, in order to reduce the impact at the descending end of the piston, it is preferable that the descending speed immediately before reaching the descending end is small.

That is, it is desired that the descending speed at the time of preventing a sudden drop when the pipe is damaged is smaller than the descending speed in the normal state and is larger than the descending speed for cushioning the impact at the descending end of the piston. However, the conventional lowering speed control device for a lift cylinder cannot perform such lowering speed control.

An object of the present invention is to provide a lowering control device for a lift cylinder that can solve the above-mentioned problems of the prior art.

[Means for solving the problem]

A feature of the present invention is that a movable body is provided in a lower portion of a cylinder tube so as to be vertically movable and elastically biased upward, and a piston passage is provided through a throttle passage provided in the movable body. In a lowering control device for a lift cylinder, in which a lower oil chamber and a flow rate control valve for lowering speed control are connected, and the degree of throttling of the throttle channel is increased by pushing down a movable body by a piston. Has a first throttle channel and a second throttle channel, and the degree of throttling of the first throttle channel is such that when the flow rate of oil discharged from the lift cylinder becomes larger than the control flow rate of the flow rate control valve, Is set so that the first throttle channel is closed by the lowering of the movable body, and the throttle degree of the second throttle channel is the flow rate of the oil discharged from the lift cylinder when the first throttle channel is closed. Is the control of the flow control valve When the amount is smaller than the amount, it is set so as to restrict the rise of the movable body, and the degree of throttling of the second throttle channel is such that the throttle of all throttle channels immediately before the piston pushes down the movable body and reaches the descending end. It is smaller than degrees.

[Action]

According to the configuration of the present invention, in a normal descending state where there is no damage to the piping between the lift cylinder and the flow rate control valve for lowering speed control, the discharge oil flow rate from the lift cylinder is
It becomes the control flow rate of the flow control valve. In this case, the discharged oil is not throttled in the first throttle channel of the movable body, and the movable body does not descend.

When the piston reaches the vicinity of the lower end, it pushes down the movable body. As the movable body descends, the degree of throttling of the throttle passage increases, and the impact at the descending end of the piston is mitigated.

Next, due to damage to the piping between the lift cylinder and the flow rate control valve for lowering speed control, the flow rate of oil discharged from the lift cylinder becomes excessive, and during a sudden drop that exceeds the control flow rate of the flow rate control valve, The discharged oil is throttled in the first throttle passage, and the movable body descends due to the pressure difference between the upstream and downstream sides of the throttle portion.

By closing the first throttle flow path by lowering the movable body, the flow rate of oil discharged from the lift cylinder can be made lower than the control flow rate of the flow rate control valve for lowering speed control, and the lowering speed of the piston can be reduced. It can be decelerated to prevent a sudden drop.

At this time, in the second throttle flow passage, the discharge oil is throttled even if the flow rate of the discharge oil from the lift cylinder is smaller than the control flow rate of the descending speed control flow rate control valve, and the pressure difference between the upstream side and the downstream side of the throttle portion is reduced. As a result, the rise of the movable body is restricted, and the closing of the first throttle channel is maintained.

As a result, the flow rate of oil discharged from the lift cylinder at the time of sudden drop prevention is made smaller than the control flow rate of the flow rate control valve for descending speed control, which is the oil flow rate at the time of normal descending state, and the descending speed at the time of sudden drop prevention It can be smaller than the normal descending speed.

Further, the degree of throttle of the second throttle channel is smaller than the degree of throttle of all the throttle channels immediately before the piston reaches the descending end. This makes it possible to increase the discharge oil flow rate from the lift cylinder in the sudden drop prevention state more than the discharge oil flow rate from the lift cylinder immediately before the descending end of the piston in the normal state. It can be made higher than the descending speed for impact relaxation immediately before the descending end of the piston in the normal state.

[Comparative example]

 First, a comparative example of the present invention will be described with reference to the drawings.

A lift cylinder 1 shown in FIG. 3 is used, for example, for lifting a fork of a forklift truck,
It has a cylinder tube 2 and a piston 3. The lower end of the cylinder tube 2 has a tail block 4 and a plug.
An oil chamber 5 is formed below the piston 3 by being closed by 4a.

A fixed cylinder 6 having an open lower end is inserted and fixed to the tail block 4, and a cylindrical movable body 7 having an open lower end is vertically inserted into the fixed cylinder 6. A coil spring 8 that elastically biases the movable body 7 upward is engaged with the inner peripheral portion of the movable body 7 and the plug 4a.

The right side of the figure shows the state where the piston 3 is located at the lowermost end, and the left side of the figure shows the state where the piston 3 descends and starts contact with the movable body 7. Further, the movable body 7 can be lowered until it comes into contact with the plug 4a.

Then, on the peripheral wall of the movable body 7, a plurality of first openings 9 are provided on the uppermost side, a plurality of second openings 10 are provided below the first opening 9, and a plurality of third openings 11 are provided below the second opening 10. A plurality of fourth openings 12 are formed below the third openings 11. Further, a partition wall 13 is formed inside the movable body 7 between the first opening 9 and the second opening 10 above and below, and a plurality of fifth openings 14 and a single sixth opening 15 are formed in this partition wall 13. Has been done. The upper side of the sixth opening 15 can be opened and closed by a check ball 16.

The second opening 10 and the third opening 11 serve as a first throttle channel, and the fifth opening 14 serves as a second throttle channel.

A plurality of communication holes 17 are formed in the peripheral wall of the fixed cylinder 6, and a connection port 18 is formed in the tail block 4 so as to communicate with the communication hole 17. A pipe 19 shown by a broken line in the drawing is connected to the connection port 18, and the lift cylinder 1 is connected to the flow rate control valve 20 for lowering speed control, the switching valve 21, and the pump 22 via the pipe 19. The pump 22 discharges the pressure oil from the tank 23. The switching valve 21 has a rising state in which the pressure oil discharged from the pump 22 is sent to the lift cylinder 1, a descending state in which the oil discharged from the lift cylinder 1 is drained to the tank 23, and a neutral state in which the flow of oil is stopped. It can be switched to and. The flow rate control valve 20 for controlling the descending speed is
The pressure oil discharged from the pump 22 through the switching valve 21 is supplied to the lift cylinder without being throttled, and the oil discharged from the lift cylinder 1 is throttled so as to have a constant control flow rate.

In the lift cylinder 1, when the switching valve 21 is lowered, the piston 3 descends and the oil in the oil chamber 5 first moves through the second opening 10, the third opening 11, and the fifth opening 14 of the movable body 7. It reaches the inside of the body 7, and from the communication hole 17 of the fixed cylinder 6 to the connection port 18
Is discharged through. The flow rate of oil discharged from the lift cylinder 1 is the control flow rate of the flow rate control valve 20 as described above, and the piston 3 descends at a speed determined by this control flow rate.

When the piston 3 reaches the vicinity of the lower end, the movable body 7
Press down. Then, the movable body 7 descends and the second opening 10
The third opening 11 and the third opening 11 are gradually closed by the peripheral wall of the fixed cylinder 6, and finally the oil is discharged to the outside of the shift cylinder only through the fifth opening 14. As a result, the piston 3 is decelerated when reaching the vicinity of the descending end, and the impact at the descending end is relieved.

Next, when the switching valve 21 is raised, the pressure oil is released from the connection port 18
Through the communication hole 17 of the fixed barrel 6 to the inside of the movable body 7, and pushes up the check ball 16 to make the first opening from the sixth opening 15.
The oil reaches the oil chamber 5 through the opening 9 and the piston 3 is lifted.

Next, when the flow rate of oil discharged from the lift cylinder 1 exceeds the control flow rate of the flow rate control valve 20 and becomes excessive due to damage to the pipe 19 between the connection port 18 and the flow rate control valve 20, etc. The discharged oil is throttled at the third opening 11. Due to the pressure difference between the upstream and downstream of the throttle portion, the movable body 7 descends until it comes into contact with the plug 4a. That is, the throttling degree of the first throttle passage, which is determined by the opening areas of the second opening 10 and the third opening 11, becomes larger when the flow rate of oil discharged from the lift cylinder 1 becomes larger than the control flow rate of the flow rate control valve 20. Is set to descend.

As a result, when the movable body 7 descends, the second opening 10 and the third opening 11 are closed by the fixed cylinder 6, and the oil in the oil chamber 5 is discharged from the lift cylinder 1 only through the fifth opening 14. Therefore, the sudden drop of the piston 3 is prevented. At this time, the flow rate of oil discharged from the lift cylinder 1 through only the fifth opening 14 is made smaller than the control flow rate, and
The discharged oil is throttled at the opening 14, and the movable body 7 is prevented from rising by the pressure difference between the upstream and downstream sides of the throttle portion.

As a result, in the case where the pipe 19 is damaged, the descending speed of the piston 3 is made smaller than the normal descending speed determined by the control flow rate of the flow rate control valve 20, and safety is improved.

〔Example〕

 Embodiments of the present invention will be described below with reference to the drawings.

The lift cylinder 1 shown in FIG. 1 relates to the first embodiment of the present invention, and the difference from the comparative example is that the seventh opening 25 is formed in the peripheral wall of the movable body 7. The seventh opening 25 connects the portion above the partition wall 13 inside the movable body 7 and the outside of the movable body 7.

When the movable body 7 is located at the rising end, the radially outer end of the seventh opening 25 is located inside the oil chamber 5. Further, when the movable body 7 is pushed down by the piston 3, the radially outer end of the seventh opening 25 is closed by the fixed cylinder 6, as shown on the right side in the figure. When the movable body 7 is located at the lower end,
As shown on the left side in the figure, the radially outer end of the seventh opening 25 is located in the inner circumferential groove 26 of the fixed barrel 6. The inner peripheral groove 26 is communicated with the connection port 18 through the communication hole 17.

The first embodiment and the comparative example have the following functional differences. First, in the comparative example, only the fifth opening 14 is used as the second throttle flow passage, and the descending speed for cushioning the impact immediately before reaching the lowermost end of the piston 3 in the normal descending state, and the damage of the pipe 19 The descending speed of the piston 3 when the sudden drop is prevented by the above is the same because both are determined only by the flow rate of the discharged oil passing through the fifth opening 14.

On the other hand, in the first embodiment, the fifth opening 14 and the seventh
When the opening 25 and the second throttle flow path are formed, the piston 3 is prevented from suddenly falling than the descending speed for impact mitigation immediately before reaching the lowermost end of the piston 3 in the normal descending state. The descending speed of has been increased.

That is, according to the lift cylinder 1 of the first embodiment, when an excessive flow rate is discharged from the lift cylinder 1 due to breakage of the pipe 19, the second opening 10,
Due to the pressure difference between the upstream and downstream sides of the third opening 11, the movable body 7
Goes down to the lowest position. Then, when the movable body 7 reaches the lowermost position, in the present embodiment, the seventh opening 25 communicates with the connection port 18 as described above, so that the oil in the oil chamber 5 becomes the fifth
It is discharged to the outside of the lift cylinder 1 through the opening 14 and the seventh opening 25.

On the other hand, in the normal descending state, the movable body 7 descends only by pushing down the piston 3,
The movable body 7 does not reach the lowermost end even when the lower end reaches the lowermost end, and the seventh opening 25 is closed by the fixed cylinder 6
It is said that it does not communicate with 18.

As a result, the descending speed of the piston 3 immediately before reaching the bottom end of the piston 3 in the normal descending state is determined only by the discharge oil flow rate passing through the fifth opening 14, whereas the descending speed of the piston 3 when the sudden drop is prevented. Is the fifth opening 14 and the seventh opening 25
It depends on the flow rate of the discharged oil through the. That is, the fifth opening
The throttle degree of the second throttle channel constituted by 14 and the seventh opening 25 is only that of the fifth aperture 14 which is the entire throttle channel immediately before the piston 3 pushes down the movable body 7 and reaches the lower end in the normal state. It is smaller than the aperture.

As described above, the descending speed of the piston 3 when the sudden drop is prevented is made higher than the final descending speed for cushioning the impact at the descending end of the piston 3 during the normal descending, so that the before and after the sudden drop is prevented. It is possible to prevent the impact from occurring by reducing the speed difference, and to reduce the speed at the descending end of the piston 3 in the normal descending as much as possible to improve the impact absorbing function.

 Others are the same as the comparative example, and the same parts are denoted by the same reference numerals.

The lift cylinder 1 shown in FIG. 2 relates to the second embodiment of the present invention. The difference from the first embodiment is that the fixed cylinder 6 is not provided.
The movable body 7 is inserted directly into the tail block 4 so as to be vertically movable, and the communication function between the inside of the movable body 7 and the connection port 18 is achieved by the inner circumferential groove 30 of the tail block 4. The right side of the figure shows the movable body 7 at the lowermost position, and the left side of the figure shows the movable body 7 pushed down by the piston 3.

 Others are the same as those in the first embodiment, and the same portions are denoted by the same reference numerals.

The lift cylinder 1 shown in FIGS. 4 to 6 shows a third embodiment of the present invention.

The lift cylinder 1 includes a cylinder tube 2 and a piston 3, the lower end of the cylinder tube 2 is closed by a tail block 4 and a plug 4a, and an oil chamber 5 is formed below the piston 3. Its tail block 4
A cylindrical movable body 7 having an open lower end is vertically inserted into the movable body 7. A spring 8 for urging the movable body 7 upward is engaged with the inner peripheral portion of the movable body 7 and the plug 4a.

In addition, the peripheral wall of the movable body 7 has a plurality of upper openings at the top.
40, a plurality of intermediate openings 41 are formed below the upper opening 40, and a plurality of lower openings 42 are formed below the intermediate opening 41. An upper end opening 43 is formed in the upper wall of the movable body 7.

In the present embodiment, the intermediate opening 41 and the lower opening 42 serve as the first throttle passage, and the upper end opening 43 serves as the second throttle passage.

A connection port 18 is formed in the tail block 4. A pipe 19 is connected to the connection port 18 as in the comparative example, and the lift cylinder 1 is connected to the flow control valve 20, the switching valve 21, the pump 22, and the tank 23 via the pipe 19.

Further, the tail block 4 is formed with a through hole 44 which communicates the oil chamber 5 with the inner side of the movable body 7. The through hole 44 can be opened and closed by a check ball 45. A spring 46 for urging the closing direction of 44 is provided.

In the lift cylinder 1, when the switching valve 21 is lowered in the state shown in FIG. 6, the piston 3 is lowered and the oil in the oil chamber 5 is filled with the upper end opening 43, the upper opening 40, and the intermediate opening 4
1, through the lower opening 42 to reach the inside of the movable body 7,
Emitted through 8. The flow rate of oil discharged from the lift cylinder 1 is used as the control flow rate of the flow rate control valve 20, and the piston 3 descends at a speed determined by this control flow rate.

When the piston 3 reaches the vicinity of the lower end, it contacts the upper surface of the movable body 7 to close the upper end opening 43 and push down the movable body 7 as shown in FIG. Then, the movable body 7
Descends, the middle opening 41 and the lower opening 42 are gradually closed by the inner peripheral surface of the tail block 4, and finally the upper opening.
The oil in the oil chamber 5 is discharged to the outside of the shift cylinder only through 40. As a result, the piston 3 is decelerated when reaching the vicinity of the descending end, and the impact at the descending end of the piston 3 shown in FIG. 5 is alleviated.

Next, when the switching valve 21 is raised, the pressure oil flowing from the connection port 18 pushes the check ball 45 to reach the oil chamber 5 from the through hole 44, whereby the piston 3 rises.

Next, when the discharge oil flow rate from the lift cylinder 1 exceeds the control flow rate of the flow rate control valve 20 and becomes excessive due to breakage of the pipe 19 between the connection port 18 and the flow rate control valve 20, the intermediate portion opening 41
The discharged oil is throttled in the lower opening 42, and the movable body 7 descends to the bottom end position until it comes into contact with the bottom surface of the plug 4a due to the pressure difference between the upstream and downstream sides of the throttle portion. That is, the throttling degree of the first throttle flow passage, which is determined by the opening areas of the intermediate portion opening 41 and the lower opening 42, becomes larger when the flow rate of oil discharged from the lift cylinder 1 becomes larger than the control flow rate of the flow rate control valve 20.
Is set to be lowered.

As a result, when the movable body 7 is at the lowermost position, the upper opening 40, the intermediate opening 41, and the lower opening 42 are closed.
The oil in the oil chamber 5 is discharged to the outside of the lift cylinder 1 only through the upper end opening 43, so that the piston 3 is prevented from dropping suddenly.

At this time, the lift cylinder 1 through only the upper end opening 43
The flow rate of oil discharged from is smaller than the control flow rate of the flow rate control valve 20, and the oil discharged is throttled at the upper end opening 43,
The movable body 7 is prevented from rising by the pressure difference between the upstream and downstream sides of the throttle portion.

As a result, when the pipe 19 is damaged, the descending speed of the piston 3 is made smaller than the normal descending speed determined by the control flow rate of the flow rate control valve 20, and safety is improved.

Further, in this embodiment, the opening area of the upper end opening 43 is made larger than the opening area of the upper opening 40.

As a result, the descending speed of the piston 3 in the normal descending state immediately before reaching the bottom end of the piston 3 is determined by the discharge oil flow rate passing through the upper opening 40, whereas the descending speed of the piston 3 when the sudden drop is prevented is the upper end. Since it is determined by the discharge oil flow rate passing through the part opening 43, the throttling degree of the second throttle channel constituted by the upper end opening 43 is in a normal state immediately before the piston 3 pushes down the movable body 7 and reaches the descending end. It is made smaller than the degree of throttling of the upper opening 40 which is the entire throttling channel.

Therefore, the descending speed of the piston 3 when the sudden drop is prevented is made higher than the final descending speed for cushioning the impact at the descending end of the piston 3 in the normal descending. As a result, the difference in speed before and after the sudden drop prevention is reduced to prevent an impact from occurring, and the speed at the descending end of the piston 3 in the normal descending is minimized to improve the impact absorbing function. .

Although the upper end opening 43 is integrally formed with the movable body 7 in the above-described embodiment, the movable body 7 has a cylindrical shape with an upper opening as shown in FIGS. 7 and 8. A step portion 47 may be formed on the inner circumference of the upper end, and an orifice plate 48 having an upper end portion opening 43 may be placed on the step portion 47 and detachably attached via a snap ring 49. Accordingly, by exchanging the orifice plate 48, the opening area of the upper end opening 43 can be changed, and the descending speed of the piston 3 at the time of preventing a sudden drop can be adjusted. For example, the lift cylinder 1 is used for a forklift truck of a different model. In such a case, the set value of the opening area of the upper end opening 43 differs depending on the model, but the movable body 7 can be shared because only the orifice plate 48 needs to be replaced.

[Effect of device]

According to the lowering control device of the lift cylinder according to the present invention, it has both the shock absorbing function at the lower end of the piston and the function of preventing a sudden drop due to breakage of hydraulic piping, and moreover, the descending speed of the piston at the time of preventing a sudden drop is It can be made smaller than the descending speed determined by the control flow rate of the descending speed controlling flow rate control valve in the normal state, which is suitable for practical use.

Furthermore, since the piston's descending speed during sudden drop prevention can be made higher than the final descending speed for cushioning the impact at the piston's descending end during normal operation, the impact due to the large speed difference before and after sudden drop prevention can occur. It is possible to prevent the above, and to reduce the final lowering speed of the piston during the normal lowering as much as possible to improve the shock absorbing function at the lowering end.

[Brief description of drawings]

1 is a sectional view of a lift cylinder according to a first embodiment of the present invention, FIG. 2 is a sectional view of a lift cylinder according to a second embodiment, and FIG. 3 is a sectional view of a lift cylinder according to a comparative example. 4 to 6 are sectional views of the lift cylinder according to the third embodiment in different states, FIG. 7 is a sectional view showing a modified example of the movable body, and FIG. 8 is a movable body shown in FIG. FIG. 9, FIG. 9 and FIG. 10 are sectional views of the conventional lift cylinder in different states. 1 ... Lift cylinder, 2 ... Cylinder tube, 3 ... Piston, 5 ... Oil chamber, 7 ... Movable body, 10 ... Second opening, 11 ... Third
Opening, 14 ... Fifth opening, 20 ... Flow control valve, 25 ... Seventh opening,
40 ... Top opening, 41 ... Middle opening, 42 ... Bottom opening, 43 ... Top opening.

Claims (1)

(57) [Scope of utility model registration request] 1. A movable body is provided below a cylinder tube so as to be vertically movable and elastically urged upward.
The oil chamber below the piston and the flow rate control valve for descending speed control are connected via the throttle channel provided in this movable body, and the throttle degree of the throttle channel is increased by pushing down the movable body by the piston. In the descending control device for a lift cylinder, the throttle channel has a first throttle channel and a second throttle channel, and the throttle degree of the first throttle channel is the discharge oil flow rate from the lift cylinder. When it becomes larger than the control flow rate of the flow control valve, it is set to lower the movable body,
Due to the lowering of the movable body, the first throttle channel is closed, and the throttle degree of the second throttle channel is such that the flow rate of the oil discharged from the lift cylinder is the control flow rate of the flow control valve. Is set so as to restrict the rise of the movable body, and the throttling degree of the second throttle channel is the throttling degree of all throttle channels immediately before the piston pushes down the movable body to reach the descending end. A lowering control device for a lift cylinder, which is smaller than the above.