JPS61244902A - Remote control type piston equipment - Google Patents

Abstract

PURPOSE:To enable a piston of acting with a stroke elongated or shortened at a prescribed ratio to input displacement stroke under remote control by providing a nozzle which is of the movable type and placing a lever mechanism which shortens or elongates the displacement of the piston, between the nozzle and the piston. CONSTITUTION:A rod 25 having a shorter diameter than a piston rod 22a is firmly attached to the upper end face of a piston 22, a movable nozzle 23 is set slidably in the same direction as the piston 22, and a lever mechanism 27 which can vary the displacement ratio between the rod 26 and the movable nozzle 23 is set therebetween. The displacement ratio between the movable nozzle 23 and the piston 22 can then be varied by the lever mechanism 27. Thus the piston 22 of which the displacement stroke is shortened or elongated by the input displacement of a flapper 24 can be placed 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]

An example of a conventional remotely operated piston device is the one shown in FIG.

In this device, a nozzle 3 is protruded from the end surface of a piston 2 that slides in a sliding hole 1a of a cylinder body 1 on the opposite side of a piston rod 2a, 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 a spring 6 applies a load to the flapper 4.

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 The liquid is ejected from the nozzle 3 into the spring chamber 1b and returned to the tank S 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.
1 and the rear protrusion 5 of the output lot 5a of the proportional solenoid 5
A bias spring 13 is connected between the nozzle 3 and the nozzle 3 in a steady state.

Therefore, when the flapper 4 is moved to the left in proportion to the direction of the proportional solenoid 5, the gap with the nozzle 3 is narrowed, so that the oil pressure in the oil chamber B increases and the piston 2 moves 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 remote-operated piston device, the stroke of the piston 2 is determined by the stroke of the protruding rod 5a of the proportional solenoid 5, so when a small solenoid is used, the piston movement stroke is 3 to 5. It was just ■.

Therefore, when a large stroke is required, even if low-speed operation is sufficient without requiring much precision,
For example, as shown in FIG. 10, a rack rod 14 is integrally fixed to the piston rod 2a, and the rotation of a pinion gear 15 that engages with the rack is detected by a position detector 16 such as a potentiometer, and the detected value is The 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.

This not only makes the system expensive.

There is a problem in that servo valves and the like are easily affected by oil contamination.

Further, with any of the piston devices described above, contrary to the above, it is also difficult to control the displacement of the piston extremely finely.

This invention solves these problems by using a nozzle flapper mechanism as shown in FIG.

It is an object of the present invention to enable remote operation of a piston with a stroke that is expanded or contracted at a predetermined ratio with respect to manual or electric input displacement.

[Means for solving problems]

Therefore, the remotely operated piston device according to the present invention is a device as shown in FIG.

The input means for setting the position of the flapper is not limited to a proportional solenoid), and the nozzle is separated from the piston to make it a movable nozzle, and a rod that protrudes from the oil chamber on the large area side is fixed to the piston, and A lever mechanism is provided to reduce or enlarge the transmitted displacement of the piston, and the movable nozzle is displaced by this lever mechanism at a predetermined ratio to the displacement of the piston.

[Function] 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 caused by the large area side of the piston of the cylinder. The information is transmitted to the oil chamber of the piston and moves the piston, thereby displacing the movable nozzle in the direction of widening the gap, but since the amount of displacement is reduced or expanded at a predetermined ratio by the lever mechanism, it is smaller than the amount of displacement of the piston. become smaller or larger.

Therefore, in order to displace and balance the movable nozzle by an amount corresponding to the input displacement of the flapper, it is necessary to displace the piston according to the reduction or enlargement ratio by the lever mechanism, and as a result, a desired displacement stroke of the piston is obtained.

〔Example〕

Hereinafter, various embodiments of the present invention will be explained based on FIGS. 1 to 8 of the drawings. In these figures, parts similar to those in FIG. is 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 lower end surface and protrudes from the cylinder body 21 to drive a load (not shown).

A rod 25 having a smaller diameter than the piston rod 22a is fixed to the upper end surface of the piston 22 and projects into a hollow lever chamber 21c formed in the cylinder body 21.

In addition, in the diagram of the piston 22, the effective working area of the lower end surface and the upper end surface is 1:2, and the sliding hole 21 of the cylinder body 21. The lower oil chamber formed by the piston 22 is called the small-area oil chamber A, and the upper oil chamber 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 the same direction with the movable nozzle 23 shifted from the piston 22, and the tip end forming the nozzle part 23a is made to protrude into the spring chamber 2ib, and the rear end part 23b is It projects into the lever chamber 21e.

This movable nozzle 23 is always urged downward in the figure by a spring 26a engaged between it and the flange portion 21d of the cylinder body 21. And this movable nozzle 2
A flapper 24 similar to the conventional example shown in FIG. 9 is disposed facing the nozzle portion 23a of No. 3 and fixed to the output rod 5a of the proportional solenoid 5, and is operated by a spring 26b engaged between it and the flange portion 21d. It is loaded and displaced in proportion to the output of the proportional solenoid 5.

A lever 27 is provided in the lever chamber 21c with one end pivotally supported by a shaft 28, and a roller 29 pivotally supported at the other end is brought into rolling contact with the tip of the rod 25 and moved to a position near the shaft 28. A roller 30, which is pivotally supported by the rod 25, is brought into rolling contact with the rear end portion 23b of the movable nozzle 23 from the opposite side to the rod 25.

These levers 27 and shafts 28. The rollers 29 and 30 constitute a lever mechanism that reduces the displacement of the piston 22 transmitted via the rod 25.

Then, the pressure oil supplied from the pressure oil source 20 is supplied from the pressure supply lower of the cylinder body 21 to the oil chamber A through the oil passage 31a, and is also supplied to the oil chamber B through the oil passage 31b via the orifice 8 which is a flow passage control part. also supplied to

Further, the pressure oil in the oil chamber B is supplied to the movable nozzle 23 through the oil passage 31e, and the nozzle portion 23a is supplied through the internal oil passage.
The spring is ejected from the spring chamber 21b through the gap with the flapper 24.

Then, the oil is guided to the lever chamber 21c by the oil passage 31d,
Furthermore, it is returned to the tank 9 through the discharge oil path 31e.

Next, the operation of the first embodiment configured as described above will be explained. - When the proportional solenoid 5, which is the input means, is driven to move the flapper 24 downward from the illustrated balanced state, the gap with the nozzle portion 23a is narrowed.

This increases the back pressure of the movable nozzle 23.

This is transmitted to the oil chamber B and the force that presses the piston 22 downward increases, so the piston 22 moves downward.

Since the rod 2S moves simultaneously with this downward movement of the piston 22, the lever 27 follows the displacement of the rod 25 due to the pressing force of the movable nozzle 23 and rotates in the direction shown by arrow C.

As a result, the movable nozzle 23 also descends, so that the gap with the flapper 24 widens, forming a predetermined gap and creating a new positioning state for balance.

In this case, the dimension from the shaft 28 of the lever 27 to the shaft fulcrum of the roller 30 is Q8, and the dimension ρ2 is the dimension from the shaft fulcrum of the roller 29.
Then, the displacement amount of the piston 22 is 22/QI of the displacement amount of the movable nozzle 23 (corresponding to the displacement amount of the flapper 24).
Double.

Therefore 1 For example, Q 2 / Q 1 = 5
Then, even if the stroke of the output rod 5a of the proportional solenoid 5 is 4 ms, the stroke of the piston 22 is 4X5=20 mm.

Furthermore, since the movable nozzle 23 is driven by the piston 22 via the rod 25 and the lever 27, the spring 26a only needs to be strong, so that locking phenomenon due to oil contamination does not occur.On the other hand, the proportional solenoid 5 has a spring 26b. 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. Even if dirt accumulates between the nozzle portion 23a and the flapper 24, the back pressure increases and the piston 22 moves.

The movable nozzle 23 is moved away from the flapper 24 to flush out the dust.

Figure 2 shows a second embodiment of the present invention.
The size relationship of the effective action areas of the hydraulic pressure on both sides of the piston 22 in the first embodiment is reversed, and the position of the fulcrum of the lever 27 is changed.

That is, a small-diameter piston rod 22b is fixed to the lower end surface of the piston 22 to drive a load (not shown), and a large-diameter rod 3'5 is fixed to the upper surface and projects into the lever chamber 21C.

Therefore, the oil chamber on the upper side of the piston 22 becomes the oil chamber A on the small area side, and the oil chamber on the lower side becomes the oil chamber B on the large area side.

On the other hand, the lever 27 has an intermediate portion relatively close to the movable nozzle 23 that is supported on the cylinder body 21 by a shaft 28, and rollers 29 and 30 are supported near both ends, and one of the rollers 2S is connected to a rod 33. The roller 30 is inserted into an engagement hole 33a formed near the tip of the movable nozzle 23 and brought into rolling contact with the inner surface thereof, and the other roller 30 is brought into rolling contact with the rear end 23b of the movable nozzle 23.

Therefore, in this embodiment, the direction of movement of the flapper 24 by the proportional solenoid 5 and the movement of the movable nozzle 23 thereby are opposite to the direction of movement of the piston 22.

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

Figure 3 shows a third embodiment of the present invention. This example is
A manual input means is provided in place of the proportional solenoid which is the input means in the first embodiment.

That is, a manual adjustment screw 40 is screwed into a female screw portion 21e formed at an end in the moving direction of the movable nozzle 23 of the cylinder body 21, which is a fixed member, and an O-ring 41 is inserted between it and the sliding surface of the cylinder body 21. It is interposed 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 42.

Also, in the hollow part formed in the manual adjustment screw 40.

A spring 43 stronger than the spring 26b is attached,
The push rod 42 is pushed inward through the washer 44. 45 is a lock nut that fixes the position of the manual adjustment screw 40.

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 manually set as desired.

Further, by pushing in or pulling out the push rod 42, the piston 22 can be quickly driven without rotating the manual adjustment screw 40. After operation, it returns to its original position accurately.

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

Figure 4 shows a fourth embodiment of the present 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.

Figure 5 of the Hoshidate Mugei Group shows the fifth embodiment of this invention.
This embodiment improves accuracy by reducing positioning fluctuations due to load fluctuations and the like in the first embodiment.

That is, in order to 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 valve 80 is installed in the oil passage 31b between
is inserted into the oil passage 31c between the oil chamber B and the movable nozzle 23.
A pressure reducing valve 81 is inserted therein. The pressure reducing valve 81 serves to keep the pressure drop constant in the gap between the movable nozzle 23 and the flapper 24.

Due to the functions of the constant flow rate control valve 80 and the pressure reducing valve 81, the gap between the movable nozzle 23 and the flapper 24 is kept constant even when the load fluctuates, thereby enabling highly accurate positioning.

Even if the pressure in the oil chamber B on the large-area side of the piston 22 is high and the ejection force from the movable nozzle 23 is too large, the pressure reducing valve 81 reduces the pressure to an appropriate constant pressure, making it unnecessary to use a small solenoid. enable.

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

In this embodiment, as shown by the imaginary line in FIG. 5, a position detector 82 for detecting the position of the movable core of the proportional solenoid 5 is provided to control the proportional solenoid 5 in a closed loop. , the accuracy can be further improved by more than one order of magnitude.

Fig. 6 shows a sixth embodiment of the present invention. This example is
A double lever mechanism is provided to increase the magnification rate of displacement.

That is, an L-shaped lever chamber 2 is provided within the cylinder body 21'.
10', and a first lever 51 consisting of a long piece and a short piece bent at right angles and a straight second lever 52 are attached to the shaft 5, respectively.
It is pivoted by 3.54.

Then, the roller 55, which is pivotally supported at the tip of the long piece of the first lever 51, is brought into rolling contact with the tip of the rod 25.

The roller 56 that is pivoted on the tip of the short piece is rolled into contact with the end of the second lever 52 that is far from the fulcrum shaft 54, and the roller 57 that is pivoted on the other end is rolled onto the rear end 23b of the movable nozzle 23. I'm letting you touch me.

Therefore, the first. If the length from each fulcrum of the second lever 51, 52 to the rolling contact point of each roller is 11 # Q21 Q3 * Q4 as shown in the figure, then the amount of displacement of the piston 22 and the amount of displacement of the movable nozzle 23 and flapper 24 are The ratio is (Q4 /Q3) x (Q'2 /111+), and the expansion or reduction rate of the displacement amount can be increased.

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

Figure 7 shows an application example in which the remotely operated piston device according to the present invention is used to control the opening mu of a poppet valve.

The poppet valve 60 is opened and closed by a solenoid valve 62, and its opening amount is regulated by the piston 22.

That is, the poppet 61 is driven at high speed by hydraulic pressure whose applied force direction is switched by the solenoid valve 62.

The opening amount is optionally remotely controlled by a remotely operated piston device 20 according to the present invention.

When the poppet 61 momentarily opens, pressure oil is fed into the cylinder 63 from the pressure oil supply source 20 at a flow rate commensurate with the opening amount, so that flow rate control with a good rise in flow rate can be performed.

In each of the above-described embodiments, the roller supported by the lever is brought into rolling contact with the rod and the movable nozzle, but the roller may be brought into contact with the rod and the movable nozzle by means of an elongated hole and a pin.

For example, as shown in FIG. 8, elongated holes 27a and 27b are formed at positions far from and near the fulcrum shaft 28 of the lever 27, respectively, and a bottle 71 implanted at the tip of the rod 25 fixed to the piston is elongated. The movable nozzle 23 is inserted into the hole 27a.
The bottle 72 installed at the rear end is inserted into the elongated hole 27b.

In this way, the lever 27 has a large degree of freedom in the left and right directions in the figure, so the lever 27 can be rotated in the direction of the arrow without difficulty, and since the vertical direction is tightly regulated, the lever 27 can be moved even at high speeds. 27 and rod 25 or movable nozzle 23
I don't think there will be any separation between the two.

Furthermore, in each of the above-described embodiments, the ratio of the small area to the large area on which the hydraulic pressure acts on both sides of the piston is set to 1=2, but this can be changed as appropriate depending on the state of the external load.

For example, if a pushing force is always applied to the piston from a load, a so-called ram cylinder type piston without a small area portion may be used.

In each of the above embodiments, the displacement of the piston is reduced at a predetermined ratio by the lever mechanism and transmitted to the movable nozzle, so that the piston stroke is expanded in response to the input displacement of the flapper. Conversely, it is also possible to use a lever mechanism to amplify the displacement of the piston at a predetermined ratio and transmit it to the movable nozzle, thereby obtaining a piston stroke that is reduced relative to the input displacement of the flapper.

〔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 displacement stroke that is expanded or contracted by manual or electric input displacement of the flapper. The enlargement or reduction ratio can be set arbitrarily by a lever mechanism.

For example, using a small proportional solenoid with a stroke of 4+nn+, a piston stroke of 20III11 or more or, conversely, less than 1 mm can be obtained proportionally.

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 6 are schematic sectional views showing structures of first to sixth embodiments of the present invention, respectively. FIG. 7 is a configuration diagram of a poppet valve showing an application example of the remotely operated piston device according to the present invention. FIG. 8 is a sectional view of a main part showing another example of the lever mechanism according to the embodiment of the present invention. FIG. 9 and FIG. 10 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 control section) 20 ... Remotely operated piston device 21.21'.
... Cylinder body 22 ... Pistons 22a, 22
b... Piston rod 23... Movable nozzle 24... Flapper 25
．． 33...Rods 26a, 26b...Springs 27.51, 52...Lever 28.53.54...Axis (fulcrum) 29.30.55-57...Roller 40...Manual adjustment Screw 42...Push rod 50...Stepping motor 51...Rotation amount-linear amount conversion mechanism 60...Poppet valve 60...Poppet 62
...Solenoid valve 63...Cylinder 80...
・Constant flow control valve 81...Reducing valve 82...Position detector Figure 1's2 Figure 3! il 4vA 311511m Figure 6 Figure 8 Figure 9 Figure 10

Claims (1)

[Scope of Claims] 1. A piston that slides within a cylinder, a rod that is fixed to an end face of the piston and protrudes from an oil chamber on the large area side of the piston, and the piston that is transmitted through the rod. a lever mechanism that reduces or expands the displacement of the piston, a movable nozzle that is displaced by the lever mechanism at a predetermined ratio with respect to the displacement of the piston, a flapper that faces the movable nozzle, and a position of the flapper that is set. an input means for
Pressure oil is supplied from the pressure oil supply port to the oil chamber on the large area side of the piston through the flow control unit, and the pressure oil in the oil chamber is jetted out from the movable nozzle and passes through the gap with the flapper to the tank. A remotely operated piston device characterized by being configured to return to its original position. 2. The remotely operated piston device according to claim 1, wherein the input means is a proportional solenoid. 3. The remote operation according to claim 1, wherein the input means includes 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. shaped piston device. 4. The remotely operated piston device according to claim 1, 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. 5 Claim 1 in which the flow rate control section is an orifice
5. A remotely operated piston device according to any one of items 1 to 4. 6. The remotely operated piston device according to any one of claims 1 to 4, wherein the flow rate control section is constituted by a constant flow rate control valve and a pressure reducing valve.