JPS61244901A - Remote control type piston equipment - Google Patents

Abstract

PURPOSE:To enable a piston of acting with a long displacement stroke under remote control by providing a nozzle which is of a movable type and placing a piston displacement shortening mechanism which mechanically shortens the displacement of the piston, between the nozzle the piston. CONSTITUTION:A cam rod 25 integrally projects from the right end face of a piston 22, a movable nozzle 23 is set slidably in the normal direction with respect to the sliding direction of the piston 22, and a roller 26 which is attached to the movable nozzle 23 is brought into contact with the cam face 25a of a cam rod 25. And a flapper 24 is set opposedly to the nozzle part 23a of the movable nozzle 23. Then, the piston 22 is moved by displacing the flapper 24, but the displacement is mechanically shortened by the cam rod 25 on account of which the piston can be displaced with a long stroke by use of a small input displacement under the remote control.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a remotely operated piston device, and particularly to a remotely operated hydraulic piston device whose position is controlled manually or by an electromagnetic actuator such as a proportional solenoid or a stepping motor.

[Conventional technology]

As a conventional remote operated piston device.

For example, there is one shown in FIG.

In this device, a nozzle 3 is provided on the opposite side of a piston rod 2a of a piston 2 sliding in a sliding hole 1a of a cylinder body 1, and is made to protrude into a spring chamber 1b.
A flapper 4 is fixedly disposed at the tip of an output rod 5a of a proportional solenoid 5 and is applied with a load by a spring 6.

Then, pressure oil is supplied from the pressure oil supply lower to the oil chamber A on the small area side of the piston 2 of the cylinder body 1, and is also supplied to the oil chamber B on the large area side via the orifice 8, and further the pressure oil is supplied to the nozzle. 3 into the spring chamber 1b, and returns to the tank 9 through a gap with the flapper 4.

In addition, 10 is an adjustment unit housing, and an adjustment screw 11 having a lock nut 12 is screwed onto the rear end surface.

The adjustment screw 11 and the output lot 5a of the proportional solenoid 5
A bias spring 13 that opposes the ejection force from the nozzle 3 in a steady state is engaged between the rear protrusion 5b and the rear protrusion 5b.

Therefore, when the flapper 4 is moved to the left in proportion to the output of the proportional solenoid 5, the gap with the nozzle 3 is narrowed, so the oil pressure in the oil chamber B is increased, and the piston 2 is moved to the left. That is, the piston 2 is positioned to automatically follow the flapper 4 so as to form a predetermined gap between the nozzle 3 and the flapper 4.

[Problem that the invention seeks to solve]

However, in such a conventional remotely operated piston device, the stroke of the piston 2 is determined by the stroke of the output lot 5a of the proportional solenoid 5, so when a small solenoid is used, the stroke is
It was only ~5■.

Therefore, when a large stroke is required, even if low-speed operation is sufficient without requiring much precision,
For example, as shown in FIG. 11, a rack rod 14 is integrally fixed to the piston rod 2a, and the rotation of a pinion gear 15 that meshes with the rack is detected by a position detector 16 such as a potentiometer, and the detected value is detected. Servo amplifier 1
7 and compares it with a command value, and controls the servo valve 18 in accordance with the difference to control the oil pressure in the oil chambers on both sides of the piston 2, thereby making it necessary to perform closed-loop control.

Therefore, not only is the system expensive, but the servo valve and the like are susceptible to oil contamination.

The purpose of this invention is to solve these problems and to make it possible to remotely operate a piston with a large displacement stroke using a small manual or electric input displacement using a nozzle flapper mechanism as shown in Fig. 10. shall be.

[Means for solving problems]

Therefore, the remotely operated piston device according to the present invention is a device as shown in FIG. 10! (However, the input means for setting the flapper position is not limited to the proportional solenoid.)
The nozzle is separated from the piston to form a movable nozzle, and a piston displacement reduction mechanism for mechanically reducing the displacement of the piston is provided between the nozzle and the piston, and the movable nozzle is displaced by this mechanism.

[For production]

With this configuration, when the input means displaces the flapper in the direction of approaching the movable nozzle, the gap between the two becomes smaller, increasing the nozzle back pressure, which is transferred to the oil chamber on the large area side of the piston of the cylinder. The transmission moves the piston, thereby displacing the movable nozzle in the direction of widening the gap, but the amount of displacement is mechanically reduced by the piston displacement reduction mechanism, so it is smaller than the amount of displacement of the piston.

Therefore, for the movable nozzle to be displaced and balanced by an amount corresponding to the input displacement of the flapper, a larger displacement of the piston is required, resulting in a larger displacement stroke of the piston.

〔Example〕

Hereinafter, various embodiments of the present invention will be described based on FIGS. 1 to 9 of the drawings.

Components similar to those in FIG. 10 are designated by the same reference numerals, and their description will be omitted.

Figure 1 shows a first embodiment of the present invention.This remotely operated piston device has a piston 22 slidably housed in a sliding hole 21a formed in a cylinder body 21. A piston rod (output rod) 22a is integrally fixed to the left end surface and protrudes from the cylinder body 21 to drive the load W.

A cam rod 25 having a smaller diameter than the piston rod 22a is integrally protruded from the right end surface of the piston 22 in the figure, and is made to protrude into the Rondo chamber 21C formed in the cylinder body 21, and the piston 22 slides on the lower surface of the tip end thereof. An inclined surface (cam surface) that is gently inclined with respect to the direction (arrow direction) is formed.

In addition, in the diagram of the piston 22, the effective working area between the left end face and the right end face is 1:2, and the left oil chamber formed by the sliding hole 21a of the cylinder body 21 and the piston 22 is placed on the small area side. The oil chamber on the right side is called the large-area oil chamber B.

On the other hand, the movable nozzle 23 is slidably inserted into the cylinder body 21 in a direction perpendicular to the sliding direction of the piston 22,
The tip side where the nozzle part 23a is formed is the spring chamber 21b.
A bracket 23b is provided at the rear end, and a roller 26 is pivotally supported there.

The roller 26 is brought into rolling contact with the inclined surface 2Sa of the cam rod 25. This movable nozzle 23 is always urged upward in the figure by a spring 27 engaged between it and the flange portion 21d of the cylinder body 21.

The cam rod 25 and the roller 26 constitute a piston displacement reduction mechanism that mechanically reduces the displacement of the piston.

Nozzle portion 23 of movable nozzle 23. A flapper 24 similar to the conventional example shown in FIG.
A load is applied by a spring 28 that is engaged between the solenoid 5 and the solenoid 5, and is displaced in proportion to the output of the proportional solenoid 5.

Then, the pressure oil supplied from the pressure oil source 20 is transferred from the pressure supply lower of the cylinder body 21 to the oil passage 29. It is supplied to the oil chamber A through the oil passage 29b, and is also supplied to the oil chamber B through the orifice 8, which is a flow rate control section. Further, the pressure oil in the oil chamber B is supplied to the movable nozzle 23 through the oil passage 29C, and is ejected from the nozzle portion 23a through the internal oil passage, and flows out into the spring chamber 21b through the gap with the flapper 24. Then, it is returned to the tank 9 through the discharge oil path 29d.

In addition, the pressure oil that has flowed into the Rondo chamber 21c also flows through the oil passage 298.
and return to the tank S through the discharge oil path 29d.

Next, the operation of the first embodiment configured as described above will be explained.

From the illustrated balanced state, when the proportional solenoid 5, which is the input means, is driven to move the flapper 24 upward, the nozzle portion 23. The gap between them is narrowed.

As a result, the back pressure of the movable nozzle 23 increases, which is transmitted to the oil chamber B, and the force that presses the piston 22 to the left increases, so the piston 22 moves to the left.

Since the cam rod 25 also moves to the left as the piston 22 moves to the left, the roller 26 that rolls into contact with the inclined surface moves upward along with the movable nozzle 23 following the movement of the inclined surface. When the movable nozzle 23 rises, the gap between the movable nozzle 23 and the flapper 24 widens, forming a predetermined gap and creating a new positioning state for balance.

In this case, if the slope of the inclined surface of the cam rod 25 is l/20, even if the stroke of the output rod 5a of the proportional solenoid S is 5 degrees, the piston 22 (7)
g! 5 x 20 = 100tm ft.

Since the movable nozzle 23 is driven by the piston 22 through a piston displacement reduction mechanism, the spring 27 only needs to be strong, so that locking phenomenon due to oil contamination does not occur.
Only the flapper 24 loaded by is attached, and this part is not locked by hydraulic pressure.

Therefore, even if dirt particles are mixed into the hydraulic fluid, their influence is small. If the nozzle part 23. When dust accumulates between the piston 2 and the flapper 24, back pressure increases, causing the piston 2 to
2 moves, moving the movable nozzle 23 away from the flapper 24 and flushing away the dust.

Figure 2 shows a second embodiment of the invention. This example is
In the first embodiment, the purpose is to shorten the cam rod 25 protruding from the piston 22, or to make the slope of the cam rod gentler to increase the reduction rate of the piston displacement. It shows.

That is, the cam rod 35 protruding from the right end surface of the piston 22 has an inclined surface 35. is formed so close to the piston 22 that it faces into the oil chamber B during its movement stroke. Therefore, the rod chamber 21e communicates with the oil chamber B.

Therefore, the hydraulic pressure in the Rondo chamber 21c acts on the rear end rod portion 3'5c of the movable nozzle 33 in accordance with its cross-sectional area, and a downward force is generated.

In order to counteract this pressing force, the movable nozzle 33 has a small diameter portion 3.
3d to form an oil chamber a in which hydraulic pressure acts on the movable nozzle 33 with the same working area as the cross-sectional area of the rod portion 33c,
Pressure oil in the rod chamber 21c is guided there through an oil passage 29f, and is also communicated with the oil chamber B through an oil passage 29g.

The oil chamber formed at the rear of this movable nozzle 33 is
Eight discharge oil passages 2Sd are communicated through the oil passage 29h.

Other configurations and operations are the same as in the first embodiment, so
The explanation will be omitted.

Figure 3 shows a third embodiment of the present invention, in which a manual input means is provided in place of the proportional solenoid which is the input means in the second embodiment.

That is, the female threaded portion 21 is formed at the end of the cylinder body 21, which is a fixed member, in the moving direction of the movable nozzle 33. A manual adjustment screw 40 is screwed into the cylinder body 21, and an O-ring 41 is interposed between the cylinder body 21 and the sliding surface of the cylinder body 21 to maintain oil tightness.

A push rod 42 is slidably provided through the manual adjustment screw 40, and a flapper 24 is fixed to the tip of the large diameter portion 42a.

Also, a spring 43 stronger than the spring 2B is engaged with the hollow part formed in the manual adjustment screw 40, and the washer 4
4 to push the push rod 42 inward.

45 is a lock nut.

Therefore, by rotating the manual adjustment screw 40, it is moved in the axial direction, and the push rod 42 is also moved via the spring 43, so that the position of the flapper 24 can be set manually. Also, push rod 4
2 by pushing in or pulling out the piston 22.
can be quickly driven.

Other configurations and functions are the same as in the second embodiment, so
The explanation will be omitted.

Figure 4 shows a fourth embodiment of this invention. This example is
In place of the proportional solenoid 5 which is the input means in the first embodiment, an input means using a stepping motor is provided to enable digital input.

That is, a stepping motor 50 and a rotation amount-to-linear electric conversion mechanism 51 such as a rack and pinion mechanism for converting the rotation into linear displacement are provided, and the stepping motor 50 is rotated in steps.

The flapper 24 is linearly displaced via the rotation amount-linear electric conversion mechanism 51.

Other configurations and functions are the same as in the first embodiment, so
The explanation will be omitted.

11 Mistake ■ FIG. 5 shows a fifth embodiment of the present invention. This embodiment improves accuracy by reducing positioning fluctuations due to load fluctuations, etc.

That is, in order to always keep the gap between the movable nozzle 23 and the flapper 24 constant, it is necessary to keep the supply flow rate of pressure oil constant. A constant flow control well 8 is installed in the oil passage 29b between
0 is inserted into the oil passage 29 between the oil chamber B and the movable nozzle 23.
A pressure reducing valve 81 is inserted into C.

The effect of the pressure reducing valve 81 is that, in addition to achieving high accuracy, high pressure is not applied to the movable nozzle 23, and the stick phenomenon is completely eliminated.

Note that the spring chamber of the pressure reducing valve 81 is communicated with the spring chamber 21b of the nozzle flapper mechanism through an oil passage 29+.

Other configurations and functions are the same as in the first embodiment, so
The explanation will be omitted.

FIG. 6 shows another example of the joining structure between the piston 22 and the cam rod 25 or 35 in each of the embodiments described so far.

That is, the cam rod 25 or 35 is integrated with the piston 22 in the axial direction and is connected to the piston 22 so as to be relatively rotatable via a thrust bearing 55 embedded in the end surface of the piston 22.

Therefore, it is convenient to rotate the piston rod 22a when it is easier to connect the piston rod 22a to the load.

IJJL Takumi Figure 7 shows a sixth embodiment of this invention. In this embodiment, a cam rod (cam plate in this example) that moves together with a piston.
is provided outside the cylinder body.

That is, the piston 22 sliding inside the cylinder body 60
The cam plate 65 is connected to the piston rod 22. through a connecting member 63 fixed at right angles to the tip of the piston rod 22a. The inclined surface 65. is installed parallel to the lower surface. is formed.

A control section main body 61 is connected to the cylinder main body 60 in a direction perpendicular to its axial direction by a connecting member 62, and a cam plate 65 is inserted into the connecting space.

A roller 67 that is pivotally supported on the bracket 6 fixed to the lower surface of the cylinder body 60 rolls into contact with the upper surface of the cam plate 65, and a roller 26 that is pivotally supported on the rear end of the movable nozzle 23 that is inserted into the control section body 61. is in rolling contact with the inclined surface 65a of the cam plate 65.

Since the other configurations and operations are substantially the same as those in the first embodiment, their explanations will be omitted.

Star garden group FIG. 8 shows a seventh embodiment of the invention.

In this embodiment, instead of the cam plate 65 in the sixth embodiment, a rack support 75 is attached parallel to the piston rod 22a via a connecting member 63, and a pinion gear 76 that meshes with the rack is rotated.

A cam plate 78 pivotally supported at the rear end of the control section main body 71 is rotated via a connecting shaft 77.

A roller 26 that is pivotally supported at the rear end of the movable nozzle 23 is brought into rolling contact with the cam surface of the cam plate 78, and these constitute a piston displacement reduction mechanism, and the movable nozzle 23 is reduced by the displacement of the piston 22. It is designed to be displaced.

Since the other configurations and operations are substantially the same as those in the first embodiment, their explanations will be omitted.

Ee slip M FIG. S shows an eighth embodiment of the invention.

In this embodiment, the rack support 75 of the seventh embodiment is mounted with the rack facing toward the front, and a male screw member 77 is concentrically fixed to a pinion gear 76 that meshes with the rack.
This is a female threaded portion 91 formed at the rear end of the control unit main body 91.
a, and the tip of this male threaded member 77 is brought into contact with an abutment member 23c provided at the rear end of the movable nozzle 23, thereby forming a piston displacement reduction mechanism.

Therefore, when the piston 22 moves, the rack shaft 75 also moves, and the pinion gear 76 rotates together with the male threaded member 77, so that the male threaded member 77 advances and retreats within the female threaded portion 91 of the control unit main body S1. Then, the movable nozzle 23 is reduced.

Since the other configurations and operations are substantially the same as those in the first embodiment, their explanations will be omitted.

1 side 1! In each of the above embodiments in which the proportional solenoid is used as an input means, if the proportional solenoid is provided with a position detector to perform closed loop control, even more accurate piston position control is possible. In that case, the 11th
Since there is no need to provide a position detector to a mechanical device driven by a piston as in the conventional example shown in the figure, the structure is simplified.

Furthermore, in each of the above embodiments, the ratio of the small area to the large area on which the hydraulic pressure acts on both sides of the piston was set to 1:2, but this can be changed as appropriate depending on the state of the external load. If a force is applied, a so-called ram cylinder type piston without a small area portion may be used.

〔Effect of the invention〕

As described above, by using the remotely operated piston device according to the present invention, the piston can be remotely operated with a large displacement stroke by a small input displacement, either manually or electrically. The ratio of the displacement strokes can be arbitrarily set by selecting the reduction ratio of the piston displacement reduction mechanism, for example, the slope of the inclined surface of the cam rod.

Furthermore, it is resistant to oil contamination and does not require expensive parts, so it can be provided at low cost.

[Brief explanation of the drawing]

1 to 5 are schematic sectional views showing structures of first to fifth embodiments of the present invention, respectively. FIG. 6 is a partial front view showing another example of the joint structure between the piston and the cam rod, with main parts taken in section. 7 to S are schematic sectional views showing structures of sixth to eighth embodiments of the present invention, respectively. FIGS. 10 and 11 are a schematic sectional view and a system configuration diagram showing different examples of conventional remote-operated piston devices, respectively. 5...Proportional solenoid 7...Pressure oil supply port 8
... Orifice (flow rate control part) 21.60 ... Cylinder body 22 ... Piston 22a ... Piston rod 23.3'3 ... Movable nozzle 24 ... Flapper 25.35 ... Cam rod 25,. 3Sa... Inclined surface 26.67... Roller 27.2B... Spring 40... Manual adjustment screw 42... Push rod 50... Stepping motor 51... Rotation amount - linear amount conversion mechanism 61.71.91...Control unit body 65...Cam plate 75...Rack support 76...Pinion gear 77...Male thread member 78...Cam plate 80...Constant flow rate control valve 81...Reducing valve W.
...Load No. 711 Figure 8 Figure 9 Figure 10 Figure 11 Procedural amendment (March 27, 1986, Director General of the Patent Office, Michibu Uga 1, Case Indication Patent Application No. 84626, 1983) 2. Name of J! Akira Remotely Operated Piston Device 3. Relationship with the Amendment Case Patent applicant 2-16-46 Minami Kamata, Ota-ku, Tokyo (338)
Tokyo Keiki Co., Ltd. 4, Agent (Telephone 986-2380) 1-20-5 Nuikebukuro, Toshima-ku, Tokyo (1) Detailed explanation of the invention in the specification - 6. Contents of amendments (1) "Pressure supply port" on page 10, line 3 of the specification is corrected to "pressure oil supply port." (2) In the same book, page 20, line 17, change “reduction ratio 1, for example” to “
Correct the reduction ratio (for example). (3) Correct "Figure 4" of the drawing as shown in the attached corrected drawing.

Claims (1)

[Claims] 1. A piston that slides within a cylinder, a piston displacement reduction mechanism that mechanically reduces the displacement of the piston, a movable nozzle that is displaced by the piston displacement reduction mechanism, and the movable nozzle. is provided with a flapper facing the flapper and an input means for setting the position of the flapper, and supplies pressure oil from the pressure oil supply port to the oil chamber on the large area side of the piston of the cylinder via the flow rate control unit, and A remotely operated piston device, characterized in that pressurized oil in the oil chamber is jetted out from the movable nozzle and returned to the tank through a gap with the flapper. 2. The piston displacement reduction mechanism includes a rod that is integrally fixed to the piston and has an inclined surface that is gently inclined with respect to the sliding direction of the piston, and a roller that rolls into contact with the inclined surface of the rod, 2. A remotely operated piston device according to claim 1, wherein said roller is pivotally supported by said movable nozzle. 3. The piston displacement reduction mechanism includes a rack rod integrally fixed to the piston and forming a rack along the sliding direction of the piston, a pinion gear meshing with the rack of the rack rod, and integrally with the pinion gear. Claim 1, comprising a rotating cam plate and a roller that rolls into contact with the cam surface of the cam plate, the roller being pivotally supported by the movable nozzle.
Remotely operated piston device as described in . 4. The piston displacement reduction mechanism includes a rack rod integrally fixed to the piston and forming a rack along the sliding direction of the piston, a pinion gear meshing with the rack of the rack rod, and integrally with the pinion gear. The remote control type according to claim 1, comprising a male screw member that rotates and is screwed into a female screw portion formed on the fixed member, and the male screw member is in contact with the rear end of the movable nozzle. piston device. 5. The remotely operated piston device according to any one of claims 1 to 4, wherein the input means is a proportional solenoid. 6. Claims 1 to 4, wherein the input means comprises a manual adjustment screw that is screwed into a female threaded portion formed on the fixing member, and a push rod that slidably passes through the manual adjustment screw. The remotely operated piston device according to any one of the above. 7. The remotely operated piston device according to any one of claims 1 to 4, wherein the input means comprises a stepping motor and a rotation amount-linear amount conversion mechanism that converts the rotation of the stepping motor into linear displacement. 8 Claim 1 in which the flow rate control section is an orifice
The remotely operated piston device according to any one of items 7 to 8. 9. The remotely operated piston device according to any one of claims 1 to 7, wherein the flow rate control section is constituted by a constant flow rate control valve and a pressure reducing valve.