KR100781028B1 - Hydraulic Cylinder having a reduction System - Google Patents

Abstract

[Problem] A hydraulic cylinder with a deceleration device that is easy to process due to compact hydraulic pressure, low pressure fluctuations, low energy saving and cooling, low descent control, and compactness is easy to process. to provide.

[Resolution] Hydraulic cylinder having a reduction device is a piston that can slide in a tube of a cylinder, a bottom member installed at one end of the tube, and a supply / discharge port for supplying and supplying hydraulic fluid into the tube. It is provided with a port and a bottom member, and a deceleration device is installed to reduce the speed by contacting the piston near the stroke end when the cylinder is retracted. This hydraulic cylinder is provided with a supply and discharge port between the reduction gears of the piston.

Reduction gear, hydraulic cylinder, piston, bottom member, supply port.

Description

Hydraulic Cylinder with Reduction Device {Hydraulic Cylinder having a reduction System}

BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a cross-sectional view of the shortest size of a hydraulic cylinder having a speed reduction device of an embodiment of the present invention.

Fig. 2 is a sectional view of the first reduction gear portion 2A of the first embodiment.

Fig. 3 is a sectional view of the second deceleration device section 2B in the second embodiment when not in operation.

Fig. 4 is a sectional view of the operation of the second reduction gear unit 2B according to the second embodiment.

Fig. 5 is a sectional view of the third reduction gear portion 2C of the third embodiment.

Fig. 6 is a sectional view of the fourth reduction gear portion 2D of the fourth embodiment.

Fig. 7 is a sectional view of the fifth reduction gear portion 2E of the fifth embodiment.

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Fig. 8 is a sectional view taken along line 2E 'of the application example of the fifth reduction gear unit of the fifth embodiment.

9 is a sectional view of the sixth reduction gear part 2F of the sixth embodiment.

[Code Description of Important Parts of Drawing]

1: hydraulic cylinder with reduction gear
2, 2A, 2B, 2C, 2D, 2E, 2E ', 2F: Reduction Gear

DESCRIPTION OF SYMBOLS 3: Cylinder part 5: First cylinder part 5a: First cylinder tube 5c: Head side hydraulic chamber

5d: Bottom side hydraulic chamber 6: 2nd cylinder part 6a: 2nd cylinder tube

6d: Bottom side hydraulic chamber 7: Ram 13: Check valve 15: Spring
17: bottom member 17a: stepped urine blood (凹形 穴)
19: dispatching port 21, 51, 51A, 51B: receiving base

23, 53, 53A, 53B, 63: hollow cushion member 25: locking bolt

27, 27A: compression spring 29: position detection sensor 54, 54A: check valve

55: snap ring 57: hole 63c: groove Sa, Sb: predetermined gap

Rb, Rc: space C: cushion 77: groove

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydraulic cylinder having a speed reduction device, and more particularly to a hydraulic cylinder having a speed reduction device for use in a hydraulic cylinder type elevator or a hydraulic lifting device that can stop slowly while decelerating near a stroke end.

Background Art Conventionally, a hydraulic cylinder used as a driving source for a hydraulic elevator or a hydraulic lifting device, etc., employs a telescope hydraulic cylinder that expands and contracts in multiple stages. As the telescope-type hydraulic cylinder, for example, a hydraulic cylinder in which a slow stop means, which is a slow device as disclosed in Patent Document 1, is provided.

The hydraulic cylinder includes a first cylinder having a larger diameter, a smaller diameter than the first cylinder, a second cylinder in which a bottom side is slidably accommodated in the first cylinder, and a ram accommodated in the second cylinder. ) On the bottom side, a piston is arranged in the second cylinder to partition the head side hydraulic chamber and the bottom side hydraulic chamber. When the piston reaches the simultaneous stroke end for closing both chambers, the end of the first cylinder is formed. A check valve is provided to open in contact with i).

This bottom plate on the bottom side has an air supply port for supplying and supplying hydraulic oil to the bottom hydraulic chamber via a slow stop means, and a slow stop of the piston of the second cylinder at the stroke end. Slow stop means are installed.

The slow stopping means has a cushion member in which an upper surface formed in the end plate is opened, and the upper and lower sliding parts are accommodated in the urinary chamber having a distal end portion. The cushion member is a normal part having a tapered orifice of small diameter sequentially on the outer circumferential surface and a flange part protruding from the upper end of the normal part, and the cushion member is placed upward in the spring chamber formed in the normal part. A through hole is opened in the center portion of the simultaneous flange portion in which the compression spring to be pressed is accommodated, and the tip of the pin provided to protrude to the bottom of the urinal chamber is inserted with a gap from below.

The actuating pin is set at a height such that the tip thereof becomes substantially flush with the upper surface of the cushion member when the piston reaches the stroke end and the cushion member is pushed down to the lower limit position by the piston. The check valve is opened by pushing up the check valve at the tip.

Next, the cylinder operation | movement which becomes the said structure is demonstrated. In the case of extending the cylinder, when hydraulic oil is supplied from a port provided in the end plate, the hydraulic oil passes through the spring chamber of the cushion member, flows into the bottom hydraulic chamber of the first cylinder from the through hole, and pushes the piston. The raised simultaneous check valve is closed by the compression spring. As the piston rises, the hydraulic oil in the head-side oil chamber of the first cylinder flows into the hydraulic chamber of the second cylinder, pushes up the ram, and the second cylinder and the ram extend at the same speed.

Next, when contracting the second cylinder and the ram, the hydraulic oil of the bottom side hydraulic chamber of the first cylinder is discharged from the port. As a result, the hydraulic fluid in the bottom side hydraulic chamber of the first cylinder passes through the spring chamber of the cushion member and is discharged from the through hole to the port by the reverse operation during stretching, and the second cylinder and the ram contract. When the piston reaches the stroke end, the cushion member is pushed down by the piston. As the cushion member descends, a narrow gap formed between the outer circumferential surface of the lower tapered cylindrical body and the inner circumferential surface of the distal end portion is tightened and pressurized when the hydraulic oil in the urine flows out into the port. With this, the lowering speed of the piston decreases, and the lowering speed of the piston decreases further as the narrow gap decreases due to the tapered orifice with the lowering. When the piston reaches the stroke end, the piston slows down. Viii)

[Patent Document 1] Japanese Patent Publication No. 2002-155908

By the way, in patent document 1, the whole quantity of hydraulic fluid flows into the bottom hydraulic chamber through the through-hole provided in the spring chamber of the cushion member at the time of expansion and contraction of a cylinder, or discharges it from the bottom side hydraulic chamber to the said port. It is becoming. As a result, the hydraulic resistance is increased, so that the temperature of the hydraulic oil rises and cooling is required, thereby increasing the installation place and equipment costs. In addition, it is necessary to increase the hydraulic pressure at the time of cylinder extension by the share of the hydraulic resistance, which increases the driving energy, or the need to increase the cylinder diameter, which causes a problem of increased cost.

As the cushion member descends, the hydraulic oil in the urinary chamber is discharged to the port in a narrow gap on the taper, but the flow at this time is in the same direction as the hydraulic oil discharged through the through hole and discharged to the port. Iv) joining in increasing places. In addition, the flow velocity from the through hole to the port is further changed by the weight of the elevator or the like. For example, the flow velocity becomes faster as the load weight increases, and the hydraulic pressure in the urinary chamber becomes small because the flow rate sucks the hydraulic oil in the urinary chamber. For this reason, as the load weight increases, the deceleration of the lowering speed of the piston decreases, so that the lowering speed of the piston does not slow down and the shock increases. In addition, since the passage in the spring chamber of the cushion member is changed, there is a problem that the pressure fluctuation is large.

In addition, since the gap between the orifice between the end plate and the cushion member is formed in a tapered shape, there is a problem that the size of the gap is difficult to obtain with high accuracy and the processing cost for securing the degree increases.

SUMMARY OF THE INVENTION The present invention has been made in view of the above problems, and the hydraulic resistance, pressure fluctuations are small, energy saving, cooling unnecessary, and control of the descending speed are ensured and compact. It is an object of the present invention to provide a hydraulic cylinder having this easy deceleration device.

In order to achieve the above object, the first invention of the present application is a piston capable of sliding in a tube of a cylinder, a bottom member and a bottom dispensing port installed on one end side of the tube and supply and supply port for supplying hydraulic oil to the tube, the bottom A hydraulic cylinder having a deceleration device provided on the member and provided with a deceleration device for reducing the speed by contacting the piston near the stroke end when the cylinder contracts, characterized in that a supply and discharge port is provided between the piston and the deceleration device.

In order to achieve the above object, the second invention of the present application is directed to the reduction gear according to claim 1, wherein the reduction gear has a sectional U-shaped pedestal recessed in a recess provided in a bottom member of a cylinder facing the piston, A hollow cushion member inserted in a compact manner so as to be able to slide on a support stand, and a locking bolt attached to the support stand through a hollow cushion member with a predetermined gap, and between the support stand and the hollow cushion member. It characterized in that the spring is installed to keep the support and the hollow cushion member away.

In order to achieve the above object, the third invention of the present application relates to a recessed shape having a step in which a reduction gear is fitted into a recess provided in a bottom member of a cylinder opposite to a piston. The piston can be slidably inserted in two cylindrical portions of the pedestal and the pedestal-shaped pedestal, while tightening the internal hydraulic fluid in one space between the pedestal-shaped pedestal and the piston. The support member and the hollow cushion member are separated between the support member and the hollow cushion member by the decelerating cushion member, the locking means which stops the cushion member from being ejected from the support member, and the support member and the hollow cushion member. It is characterized in that the spring is installed.

In order to achieve the above object, the fourth invention of the present application is the method according to claim 2 or 3, wherein the speed reduction device has a support base and a cushion member inserted into a gap for distributing hydraulic oil. It features. In addition, the reduction device of the fourth invention is inserted into a recess provided in a bottom member of a cylinder whose outer side is opposed to a piston, and has large acupuncture points and small acupuncture points above and below the inside. U-shaped pedestals with a stage with)), and outer and outer diameters of the upper and lower places where sliding is possible in response to large and small acupuncture points. A cushion member having an outer cylindrical portion, a circumferential surface of the large acupuncture points of the pedestal, an annular plane having a stage extending from the large acupuncture points of the pedestal to the small acupuncture points, and inserted into the large acupuncture points of the pedestal. Either the cylindrical portion of the outer diameter portion of the cushion member or the cylindrical portion of the outer diameter portion of the cushion member has a gap so that the hydraulic oil can be extruded from the space formed by the annular plane of the lower portion of the outer diameter of the cushion member and the circumferential surface of the outer diameter of the cushion member. Inserted into the acupuncture points It features.

In order to achieve the above object, the fifth invention of the present application is the method according to claim 2 or 3, wherein the speed reduction device forms a groove for circulating hydraulic oil in the inner diameter portion of the support base to provide a support base and a cushion member inserted therein. It is characterized by having. In order to achieve the above object, the sixth invention of the present application, according to claim 2 or 3, wherein the speed reduction device is formed in the outer diameter portion of the cushion member to form a groove for the distribution of the hydraulic fluid receiving pad and the cushion inserted therein It is characterized by having a member. In addition, the deceleration device of the fifth and sixth inventions has a concave-shaped support base having a stage having a large acupuncture point and a small acupuncture point in the upper part and the lower part of the lower part, and the upper part of the lower part is fitted into the recess provided in the bottom member of the cylinder. And a cushion member having cylindrical portions of large acupuncture points and small acupuncture points in the pedestal, a circumferential surface of the large acupuncture points in the pedestal, an annular plane having a step from the pedestal to the small acupuncture points, and a cushion member inserted into the large acupuncture points of the pedestal. A flow path is formed by a groove in either the cylindrical portion of the outer diameter of the cushion member or the cylindrical portion of the outer diameter of the cushion member so that the working oil can be extruded in the space formed by the annular plane of the lower portion of the outer diameter of the outer diameter of the cushion member. do.
In order to achieve the above object, the seventh invention of this application is the position detection sensor according to any one of claims 1 to 3, wherein the cushion member detects that the cylinder member has returned to a predetermined position at the time of contraction of the cylinder. It is characterized by having. In other words, in the hydraulic cylinder to which the speed reduction apparatus is attached, it has a structure which has a position detection sensor which detects that a cushion member returned to the predetermined position at the time of the largest contraction of a cylinder at the time of expansion.

According to the first aspect of the present invention, the hydraulic oil supplied from the hydraulic cylinder is made directly between the supply port and the bottom side hydraulic chamber without passing through the slow stop means as in the conventional example, so that the hydraulic resistance and the pressure fluctuation can be reduced. For this reason, there is no heat generation, etc. of the working oil, and even if a reduction gear is installed, cooling is not required, thereby reducing the equipment cost. In addition, it is not necessary to increase the driving force of the hydraulic resistance share, and it can save energy.

In addition, the oil discharged to the outside from the cushion member at the stroke end joins the flow in which the hydraulic oil flowing from the bottom hydraulic chamber to the supply port is orthogonal. As a result, the pressure in the cushion chamber is less affected by the hydraulic oil flowing from the bottom side oil chamber to the supply and discharge port, and the control of the deceleration speed becomes easy. For this reason, when the load weight is variable, even if a hydraulic cylinder is used in an elevator and a lifting device, it can be stopped at a predetermined position with less impact by lowering the stroke end at a predetermined deceleration speed regardless of the load weight.

According to the second aspect of the invention, a passage through the hollow portion of the cushioning material as in the prior art is not formed, and the passage can be formed in the cushion chamber, so that a pressure receiving portion having a large cross-sectional area is formed, and the reduction device is compactly formed. do.

In addition, since the speed reduction device is formed by a simple support base and a hollow cushion member, it is not necessary to process the tapered diaphragm in the cushion member, which is a large part, so that the parts are easily manufactured and inexpensive.

According to the third aspect of the present invention, the length of the predetermined gap between the cushion member and the support base becomes longer along with the drop of the cushion member, so that the pressure increase rate of the cushion chamber increases with the drop of the cushion member, The deceleration speed can be made larger, and the impact at rest becomes smaller. In addition, a large cushioning effect is obtained because the working oil in the cushion chamber flows out through the adjacent space. In addition, the same effects as those of the first and second inventions are obtained.

According to the fourth aspect of the present invention, when the diaphragm of the cushion member is formed into a cylindrical gap, the processing becomes easy as described above.
According to the fifth and sixth inventions, in the case of forming grooves, variations in the cross-sectional area of the diaphragm portion can be made small, and variations in tightening resistance can be made small, thereby improving the accuracy of the deceleration speed. In addition, even when the groove is formed, the deviation allowable range of the groove is large, so that processing is easy.

When the width and depth of the grooves are changed downward so that the cross-sectional area becomes large for a while, as in the second embodiment, the rate of pressure rise can be increased along with the fall, and the impact upon stopping can be made smaller.

According to the seventh invention, the position detection sensor detects the position of the cushion member and transmits it to a control device (not shown). For example, the position detection sensor detects that the compression spring is extended after the deceleration device is operated, the cushion member is separated from the support stand to a predetermined position, and is returned to the control device (not shown). For this reason, when a cushion member returns to a predetermined position, it can decelerate safely and stop by a reduction gear part in the state which a predetermined function is exhibited. If it does not return, safety measures such as displaying the effect or stopping the operation are taken.

Best Mode for Implementation of the Invention

EMBODIMENT OF THE INVENTION Hereinafter, embodiment of the hydraulic cylinder with a reduction gear which concerns on this invention is described in detail with reference to drawings.

1 is a cross-sectional view at the time of minimizing a hydraulic cylinder having a speed reduction device as an embodiment. 2 to 9 are enlarged views of the reduction gear.

In Fig. 1, the hydraulic cylinder 1 (hereinafter referred to as hydraulic cylinder 1) having the reduction gear of the embodiment is mainly a second reduction gear portion 2B, which is an example of the reduction gear portion 2, and the cylinder portion 3; The cylinder part 3 is formed in substantially the same shape as the conventional structure. However, the speed reduction device part 2 of FIG. 1 has shown the 2nd speed reduction device part 2B of 2nd Example of FIG. 3, FIG.

The cylinder portion 3 has a large diameter of the first cylinder portion 5 and a smaller diameter than the first cylinder portion 5 and the bottom side slides in the first cylinder portion 5. The 2nd cylinder part 6 accommodated in this possibility and the ram part 7 accommodated in the 2nd cylinder part 6 at one end side are comprised.

The 2nd cylinder part 6 is provided in the bottom side, and the piston 9 is arrange | positioned so that sliding is possible in the 1st cylinder tube 5a of the 1st cylinder part 5. The piston 9 is screwed to the second cylinder tube 6a of the second cylinder portion 6, and the inside of the first cylinder portion 5 is connected to the head side hydraulic chamber 5c and the bottom. It is partitioned by the side hydraulic chamber 5d. The piston 9 is formed with a hole 11 for communicating the head side hydraulic chamber 5c of the first cylinder portion 5 and the bottom side hydraulic chamber 6d of the second cylinder portion 6.

Moreover, the check valve 13 is arrange | positioned in the center part of the piston 9 so that it may pressurize toward the bottom side by the spring 15, and the check valve 13 is a 1st cylinder part 5 normally. The bottom side hydraulic chamber 5d of the () is closed and the bottom side hydraulic chamber 6d of the second cylinder part 6 are closed. In addition, the check valve 13 has a second reduction gear which will be described later when the second cylinder portion 6 reaches the stroke end, the tip of which is provided in the bottom side hydraulic chamber 5d of the first cylinder portion 5. It is comprised so that it may contact and open the locking bolt 25 of the part 2B.

The bottom member 17 is screwed to the first cylinder tube 5a on the bottom side of the first cylinder portion 5, and the end of the bottom member 17 is directed toward the piston 9 side. A shape blood 17a is provided. The deceleration unit 2 of the embodiment described later is inserted into the yaw blood 17a. In addition, the bottom member 17 supplies hydraulic fluid to the bottom side hydraulic chamber 5d of the first cylinder portion 5 between the piston 9 and the reduction apparatus 2 from the upper side of the reduction apparatus portion 2. A supply / discharge port 19 is installed.

Next, the first reduction gear unit 2A of the first embodiment will be described in FIG. The first reduction gear portion 2A is a recessed shape in which the end of the bottom member 17 is indented to the small diameter side of the recessed blood 17a, and the receiving stand 21 and the receiving stand 21 having a cross-sectional shape. A predetermined gap Sa with respect to the hollow cushion member 23 (hereinafter referred to as the cushion member 23) and the hollow hole 23a in which the hollow cushion 23 is slidably inserted in the center and the hollow hole 23a is perforated. Compression is inserted into the pressing member to press the cushion member 23 in the falling direction against the locking bolt 25 and the support base 21 is screwed to the simultaneous support base 21 through the cushion member 23. It is comprised by the spring 27.

In the first reduction gear 2A of the first embodiment, the compression spring 27 penetrates through the simultaneous locking bolt 25 inserted into the hollow portion of the cushion member 23, and one end thereof is supported by 21, the other end is in contact with the cushion member 23 to separate the support base 21 and the cushion member 23. The bolt head 25a of the locking bolt 25 is immersed in the center of the blood 23b provided on the piston 9 side from the center of the cushion member 23, and the bolt head when the cushion member 23 is operated. The upper surface 25b of 25a and the upper surface 23c of the cushion member 23 are formed to be located in substantially the same plane.

In addition, in the first reduction gear unit 2A, a cushion chamber C is provided between the support base 21 and the cushion member 23, and hydraulic oil is stored therein. The hydraulic fluid is supplied to the cushion chamber C when the cushion member 23 is close to the support base 21, that is, when the piston 9 contacts the cushion member 23 and descends again to approach the support base 21. To increase the pressure. At the same time, the working oil is tightened by the gap Sa and flows out to the outer bottom side hydraulic chamber 5d to slow down the speed of the cushion member 23 with respect to the support base 21.

The hydraulic oil which flowed out outside is joined by the flow which the flow of hydraulic fluid which flows from the bottom side hydraulic chamber 5d to the supply-discharge port 19 is orthogonal. The hydraulic oil flowing out of the gap Sa collides with the bolt head 25a, and then flows to the bottom side hydraulic chamber 5d with a slow flow rate. For this reason, the pressure of the cushion chamber C is less likely to be affected by the hydraulic oil flowing through the supply and discharge port 19 in the bottom side hydraulic chamber 5d, and the control of the deceleration speed is facilitated.

The locking bolt 25 is formed when the piston 9 reaches the stroke end and the cushion member 23 is pushed down to the lower limit position by the piston 9, that is, the bolt head 25a is flush with the upper surface of the cushion member 23. When the surface is almost coplanar, the bolt head 25a pushes the tip of the check valve 13 to open the check valve 13.

For this reason, it connects between the bottom side hydraulic chamber 5d of the 1st cylinder part 5, and the bottom side hydraulic chamber 6d of the 2nd cylinder part 6 via the check valve 13, and the 2nd The hydraulic oil of the bottom side hydraulic chamber 6d of the cylinder portion 6 is discharged to the supply and discharge port 19 via the bottom side hydraulic chamber 5d of the first cylinder portion 5.

1, a position detection sensor 29 for detecting the position of the cushion member 23 is attached to the bottom member 17, as shown in FIG. The position detection sensor 29 detects the position of the cushion member 23 and transmits it to a control device (not shown). For example, the position detection sensor 29 detects whether the cushion member 23 is in a predetermined position and transmits it to a control device (not shown).

The predetermined position is whether or not the cushion member 23 returns to the predetermined position, which means that the compression spring 27 extends, and the support base 21 and the cushion member 23 are separated from the predetermined position. Is detected. For this reason, when returning to a predetermined position, it has shown that the reduction gear part 2 is in the state which can exhibit a predetermined | prescribed function, and can safely decelerate and stop.

Next, the operation of the hydraulic cylinder 1 as the first embodiment will be described. As shown in Fig. 1, when the piston 9 is stopped at the stroke end, the simultaneous check valve 13 is pushed down by the locking bolt 25 so that the cushion member 23 is pushed down by the piston 9 to the lower limit position. It is pushed up and opened.

In this state, when the hydraulic cylinder 1 is extended, the hydraulic oil is supplied from the supply / discharge port 19 installed in the bottom member 17 to flow into the bottom hydraulic chamber 5d of the first cylinder portion 5. Push up the piston (9). As a result, the simultaneous check valve 13 at which the piston 9 is raised is closed by the compression spring 27.

As the piston 9 rises, the hydraulic oil of the head side hydraulic chamber 5c of the first cylinder part 5 flows into the bottom hydraulic chamber 6d of the second cylinder part 6 from the hole 11 of the piston 9. Inflow to the () and pushes up the ram (7) upwards. Since the cross-sectional area of the ram portion 7 and the cross section of the head side hydraulic chamber 5c are formed substantially the same, the piston 9 and the ram portion 7 rise at a relatively same speed, and the second cylinder portion 6 and the ram portion (7) is extended in two stages.

Next, when shrinking the second cylinder portion 6 and the ram portion 7, the hydraulic oil of the bottom side hydraulic chamber 5d of the first cylinder portion 5 is discharged from the supply and discharge port 19. For this reason, the hydraulic fluid in the bottom side hydraulic chamber 5d of the 1st cylinder part 8 discharges from the said supply port 19 by the reverse operation | movement at the time of extension, and a 2nd cylinder and a ram contract. When the piston 9 reaches near the stroke end, the cushion member 23 is pushed by the piston 9.

When the cushion member 23 is lowered against the compression spring 27, the cushion chamber C between the support base 21 and the cushion member 23 is reduced to increase the pressure of the working oil therein. When the pressure rises, the hydraulic fluid is tightened by the gap Sa between the cushion member 23 and the locking bolt 25 and flows out to the outside (bottom side hydraulic chamber 5d), and the cushion member for the support base 21 ( Decrease the speed of 23). When the piston 9 again reaches the stroke end, the lowering speed of the piston 9 is further decelerated, and then when the piston 9 reaches the stroke end, the piston 9 is decelerated and stopped.

For this reason, even if the hydraulic cylinder 1 is used for elevators and hoisting devices having a variable load weight, the hydraulic cylinder 1 is lowered at a predetermined deceleration speed at the stroke end regardless of the load, thereby reducing the impact and stopping at a predetermined position.

Next, with reference to Figs. 3 and 4, the second reduction gear unit 2B of the second embodiment will be described. In addition, the same components as those in the first embodiment are denoted by the same reference numerals and description thereof will be omitted.

On the small diameter side of the bottom-shaped yaw-shaped blood 17a of the bottom member 17, the 1st receiving stand 51 of the step-shaped yaw shape is enclosed. In the first support stand 51, the stage of the large diameter blood 51a and the small diameter blood 51b having the diameter of a large and small diameter is formed so that the stage of this 1st support stand may be large. In the 51, a first hollow cushion member 53 (hereinafter referred to as a first cushion member 53) having an outer diameter portion corresponding to the inner diameter portion is inserted.

The first cushion member 53 is slidably so that its outer diameter 53a is slidable with respect to the large diameter blood 51a of the first receiving base 51, or the small diameter diameter 53b is applied to the small diameter blood 51b. It is inserted with a predetermined gap Sb. In addition, a space Rb (Rc) between the first support base 51 and the first cushion member 53 is provided, and the hydraulic oil is stored therein, and the space Rb is mainly formed as a cushion chamber C. have. 3 is a non-operational state, the compression spring 27 presses and expands the first cushion member 53 and the first cushion member 53 is positioned at a predetermined position with respect to the first support base 51. And the second reduction gear unit 2B is operating and then returning to the predetermined position. 4 shows that the second reduction gear unit 2B is operating.

In the second reduction gear portion 2B, when the piston 9 is in contact with the first cushion member 53, and the lowering first cushion member 53 is close to the first receiving stand 51, the cushion chamber Rb. The pressure of) rises and flows out into the space Rc from the simultaneous gap Sb. In the space Rc, the working oil received from the cushion chamber Rb and the working oil in the space Rc reduced by the proximity thereof are combined to increase the pressure, thereby increasing the pressure Sc between the first cushioning member 53 and the locking bolt 25. Outflow from the outside to slow down the speed of the first cushion member 53 with respect to the first support (51). The hydraulic oil which flowed outwards joins with the flow which the flow of the hydraulic fluid which flows into the supply-discharge port 19 in the bottom side hydraulic chamber 5d like the 1st Embodiment orthogonally crosses. In addition, as in the first embodiment, the hydraulic oil flowing outward flows into the bottom side hydraulic chamber 5d at a slow flow rate after colliding with the bolt head 25a, thereby obtaining the same effect.

As in the first embodiment, the second reduction gear unit 2B has a hollow space Rb and a space in which the first cushion member 53 is hollow and has a locking bolt 25 and a compression spring 27 in the center thereof. The check valve 54 is provided between Rc. At this time, the locking bolt 25 may have a large gap or a predetermined gap Sa may be provided for the first cushion member 53 as in the first embodiment. In FIG. 4, the bolt head 25a of the locking bolt 25 is immersed in the center of the blood 53b 'and the upper surface 25b and the first surface of the bolt head 25a when the first cushion member 53 is operated. The upper surface 53c of the one cushion member 53 is formed to be located in substantially the same plane.

The check valve 54 flows hydraulic fluid from the space Rc toward the cushion chamber C (space Rb) when the first cushion member 53 falls from the first support base 51, and the first cushion member 53 flows. ) And the simultaneous cushion chamber C which returns quickly is prevented from becoming a vacuum. Hydraulic fluid flows into the space Rc at the gap between the locking bolt 25 and the first cushion member 53.

As for the length of the predetermined clearance gap Sb between the 1st cushion member 53 and the small diameter part 51b, the 2nd reduction gear part 2B accompanies the descent of the 1st cushion member 53, as shown in FIG. As a result, the pressure increase rate of the cushion chamber C increases with the drop, and the deceleration speed of the piston 9 is increased as much as the drop, so that the impact upon stopping can be made smaller. In addition, since the working oil of the cushion chamber (C) flows out through the space (Rc) to the outside, it is easy to simultaneously produce a larger cushioning effect and becomes compact. Since the pressure in the cushion chamber C flows out through the space Rc, the pressure fluctuation is very small.

In the above-described embodiment, a predetermined gap Sb is provided between the first cushion member 53 and the small acupoint blood 51b, but a predetermined gap (B) between the first cushion member 53 and the large acupuncture blood 51a is provided. Simultaneous and sliding the space between the first cushion member 53 and the small diameter blood 51b for providing Sb may be possible, and the space Rc may be the cushion chamber C. FIG. In this case, the check valve 54 may be configured to allow hydraulic fluid to flow from the space Rb toward the space Rc.

Next, referring to Fig. 5, the third reduction gear unit 2C of the third embodiment will be described. In addition, the same components as those in the second embodiment are denoted by the same reference numerals and description thereof will be omitted.

In the second embodiment, the compression spring 27 is installed in the hollow portion of the first cushion member 53, but in the third embodiment, the first compression spring 27A is located on the first cushion outside the second support 51A. It is provided between the member 53 and the second support base 51A. Others are the same as in the second embodiment, so detailed description thereof will be omitted.

Next, the fourth reduction gear unit 2D of the fourth embodiment will be described with reference to FIG. The same components as those in the second embodiment are denoted by the same reference numerals and the description thereof will be omitted.

In the first to third embodiments, the load of the compression spring 27 prevents the simultaneous cushion members 23 and 53 received from the locking bolt 25 from coming out of the cushion bolts 23 and 53. In contrast, in the fourth embodiment, the snap ring 55 is attached to the third support base 51B, and the load of the compression spring 27 is simultaneously received by the snap ring 55 through the second cushion member 53A. The outflow of the two cushion members 53A is prevented. Since it is the same as the other second embodiment, a detailed description thereof will be omitted.

Next, referring to Fig. 7, the fifth reduction gear portion 2E of the fifth embodiment will be described. The same components as those in the second and fourth embodiments are denoted by the same reference numerals and description thereof will be omitted.

In the first to fourth embodiments, the cushion member 53 is hollow, but in the fifth embodiment, the third cushion member 53B is made solid. In the third cushion member 53B, the outer marginal diameter 53b whose outer diameter 53a is formed to be dense and slidable with respect to the external blood 51a of the third receiving base 51B is small diameter blood 51b. Is inserted with a predetermined gap Sb.

A small hole 57 is provided in the third cushion member 53B for communicating the space Rb to the bottom side hydraulic chamber 5d of the first cylinder portion 5. Space (Rb) (Rc) is provided between the third support (51B) and the third cushion member (53B), the operating oil is stored therein, the space (Rc) is mainly formed as a cushion chamber (C) It is. Moreover, the compression spring 27 which returns the 3rd cushion member 53B in the space Rc is arrange | positioned. Moreover, 54 A of 1st check valves which flow toward the space Rc (cushion chamber C) from the space Rb are arrange | positioned, and the space Rc is prevented from becoming a vacuum. The hydraulic oil of the bottom side hydraulic chamber 5a flows into the space Rb from the small hole 57.

In the fifth reduction gear portion 2E, the piston 9 is brought into contact with the third cushion member 53B and then lowered again, so that the cushion chamber (when the third cushion member 53B is close to the third receiving stand 51B) C) (flow in the space Rb while being tightened by the simultaneous gap Sb in which the pressure in the space Rc rises). In the space Rb, the hydraulic oil received from the cushion chamber C and the hydraulic oil in the space Rb reduced by the proximity are joined to each other to flow out from the small holes 57 while increasing the pressure, and the third receiving stand 51B. The speed of the third cushion member 53B with respect to the motor is decelerated. As in the first embodiment, the hydraulic oil that flows out is joined in a flow orthogonal to the flow of the hydraulic oil flowing from the bottom side hydraulic chamber 5d to the supply and discharge port 19.

Next, the reduction gear unit 2E 'of the application example of the fifth embodiment will be described with reference to FIG. Instead of the small holes 57 provided in the cushion member 53B of FIG. 7, a groove 77 is provided in a part of the large diameter portion 53a of the cushion member 53B, and the area of the space Rc (cushion chamber C) is determined. It can secure large and becomes compact.

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Next, the sixth reduction gear portion 2F of the sixth embodiment will be described with reference to FIG.

In the above embodiment, a predetermined gap Sa (Sb) is used between the cushion member and the support base. As shown in Fig. 9, in the third cushion member 63 of the sixth reduction gear portion 2F, the outer diameter 63a is added to the large diameter blood 51a of the first receiving stand 51 and the outer diameter 63b is applied. The small diameter blood 51b is inserted in such a way that it can slide. Moreover, the groove 63c is formed in the outer diameter 63b of the small diameter part. This groove 63c may be provided where the predetermined gap Sb is formed.

The width and depth of the groove 63c may be constant or the width and depth may be variable. For example, in the case where the width and depth of the groove 63c are changed downward so that the cross-sectional area is temporarily large, the variable cross-sectional area is changed so that either one of the width and depth of the groove 63c is directed downward. In this case, as in the second embodiment, as the pressure drop rate of the cushion chamber C increases with the drop of the cushion member, the pressure decrease rate of the piston becomes larger as the pressure drops, so that the shock at the time of stopping stops. Can be made smaller. On the contrary, a groove may be provided in the inner diameter portion of the support base, or a groove may be provided in both the outer diameter portion and the inner diameter portion of the cushion member.

In the above embodiment, an example of a hydraulic cylinder extending in two stages has been described, but a single-acting cylinder and a ram cylinder may also be used, or may be used in a multi-stage hydraulic cylinder extending in another three-stage, four-stage, or five-stage. Although the hydraulic cylinder 1 of this invention was demonstrated using a hydraulic elevator, it goes without saying that it uses for a hydraulic unloading machine.

According to the first aspect of the invention, the hydraulic oil delivered from the hydraulic cylinder is made between the supply port and the bottom side hydraulic chamber directly without passing the slow stop means as in the conventional example, so that the hydraulic resistance and pressure fluctuation can be reduced. Since there is no heat generation, the cooling equipment can be omitted and energy can be saved.

Also, the oil discharged from the cushion member to the outside at the stroke end is joined by the flow in which the hydraulic oil flowing from the bottom hydraulic chamber to the delivery port is orthogonal, and the pressure of the cushion chamber is rapidly discharged from the bottom hydraulic chamber. It is easy to control the deceleration speed because it is less affected by the working oil flowing in the port. Therefore, the loading weight is variable, so that even if a hydraulic cylinder such as an elevator or a lifting device is used, the stroke end is determined at the stroke end regardless of the loading weight. It can be stopped at a predetermined position by reducing the impact by descending at a deceleration speed of.

According to the second aspect of the present invention, a passage through the hollow portion of the cushioning material is not formed as in the conventional example, and the passage portion can be a cushion chamber, so that a hydraulic pressure section having a large cross-sectional area can be formed and the speed reduction device can be made compact. In addition, since the speed reduction device is formed by a simple shape receiving stand and a hollow cushion member, it is not necessary to process a tapered diaphragm on the cushion member, which is a large part, so that the parts are easily manufactured and the cost is reduced.

According to the third invention, the deceleration speed of the piston can be increased, the impact at the time of stopping becomes smaller, and the hydraulic fluid of the cushion chamber flows out through the adjacent space, so that a large cushion can be obtained.

According to the fourth aspect of the invention, when the diaphragm of the cushion member is formed in the cylindrical gap, the above processing is easy and the degree of deceleration speed is improved. According to the fifth and sixth inventions, when the grooves are formed, the variation in the cross-sectional area of the diaphragm is small, so that the degree of the deceleration speed can be improved as the variation in the tightening resistance is reduced. In addition, even when the groove is formed, the deviation allowable range of the groove is large, so that processing is easy.

In addition, when the width and depth of the grooves are changed downward so that the cross-sectional area becomes large for a while, as in the second embodiment, the pressure increase rate can be increased along with the falling of the cushion member, and the impact at rest can be increased. It can be made smaller.

According to the seventh invention, the position detection sensor detects the position of the cushion member and transmits it to a control device (not shown). The position detecting sensor detects that the cushioning member has fallen to a predetermined position from the receiving stand after the deceleration device is operated and is returned to the predetermined position, and transmits it to the control device, and the cushioning member does not return to the predetermined position. When the deceleration unit is in a state in which a predetermined function is exerted, it can safely decelerate and stop. If it does not return, there are various effects such as safety measures such as displaying the effect or stopping the operation.

Claims (7)

It is installed on the bottom member and the bottom member installed on one end of the tube and the piston which is able to slide inside the tube of the cylinder, and on the supply and discharge port and bottom member which supply and discharge the hydraulic oil into the tube. And a reduction gear which has a reduction gear that reduces the speed by contacting the piston near the stroke end when the cylinder contracts, and has a reduction gear characterized in that a rapid discharge port is provided between the piston and the reduction gear. Hydraulic cylinder. The deceleration device according to claim 1, wherein the deceleration device is provided with a U-shaped pedestal so as to slide into a U-shaped pedestal and a cross-section so as to be slidable to a c-shaped pedestal. 계) the locking bolt attached to the support stand through the hollow cushion member with a predetermined gap with the hollow cushion member inserted therebetween, and the support stand and the hollow cushion member separated between the support stand and the hollow cushion member. Hydraulic cylinder with spring-loaded reduction gear. 2. The speed reducing device according to claim 1, wherein the speed reduction device is provided with a pedestal-shaped pedestal and a pedestal-shaped pedestal to be fitted into the recess provided in the bottom member of the cylinder facing the piston. The sliding member is inserted so as to be slidable, and the cushioning member which decelerates the piston by diaphragm tightening the internal hydraulic fluid in one space between the recessed recesses of the end and the cushioning member does not come off from the supporter. A hydraulic cylinder having a stop means and a spring reduction device for separating the support and the hollow cushion member between the support and the hollow cushion member. 4. The hydraulic cylinder according to claim 2 or 3, wherein the speed reduction device has a speed reduction device having a support base and a cushion member, wherein the cushion member is inserted in the support space with a gap for distributing the working oil. 4. The hydraulic cylinder according to claim 2 or 3, wherein the speed reduction device has a groove for circulating hydraulic oil in the inner diameter of the support, and has a speed reduction device having a support and a cushion member inserted therein. 4. The hydraulic cylinder according to claim 2 or 3, wherein the reduction device has a groove for circulating hydraulic oil in the outer diameter portion of the cushion member, and has a receiving unit and a reduction device having a cushion member inserted therein. 4. The hydraulic cylinder according to any one of claims 1 to 3, wherein the cushion member has a position detection sensor for detecting that the cushion member has returned to a predetermined position at the time of contraction of the cylinder.

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