JP3958242B2 - Time drive for pneumatic actuator - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a time drive device and a time drive method for a pneumatic actuator that can control a drive time of a pneumatic actuator such as a pneumatic cylinder, a motor, and a pump only by air pressure. The “air pressure” in the present invention is used to include a gas pressure such as nitrogen, oxygen, and argon sealed in a cylinder at a predetermined pressure.
[0002]
[Prior art]
Conventionally, for example, a pneumatic actuator such as a pneumatically driven continuous pump for supplying pressurized lubricating oil to a plurality of lubrication points has a start time (standby time) and an operation time after the start time has elapsed. It is usual to measure the time by controlling the pneumatic solenoid valve.
[0003]
Prior literature was investigated, but no suitable one was found.
[0004]
[Problems to be solved by the invention]
However, the above-mentioned conventional technology requires both electric and air sources, and in particular, the electrical equipment in the explosion-proof area must satisfy the standards stipulated by law. The price is nearly ten times higher. Explosion-proof electrical equipment is expensive in all cases, not just the control panel.
Therefore, the applicant of the present application provides a time-driven drive device and a time-driven method for a pneumatic actuator that can be controlled only by air pressure (including gas pressure sealed in a cylinder) without using any electricity.
[0005]
[Means for Solving the Problems]
The pneumatic actuator timing drive device according to claim 1, wherein an air supply source (14) supplies an air flow to a piston rod (1b) having a piston (1a) of a pneumatic cylinder (1). Pneumatic actuator that repeatedly reciprocates between the forward position and the rear end position in the pneumatic cylinder (1) using the air flow from the pneumatic cylinder and operates the pneumatic actuator (12) in accordance with the reciprocating operation A forward drive pipe (22), a reverse pipe (21), and a mechanical switching valve (7), the forward pipe (22) responding to the supply of air flow. The piston rod (1b) is moved forward from the retracted position to the advanced position, and the reverse pipe (21) moves the piston rod (1b) from the advanced position to the retracted position in response to the supply of airflow. For retreating The mechanical switching valve (7) includes a function of switching the air supply destination from the air supply source (14) to the forward piping (22) or the backward piping (21). When 1b) moves forward and reaches the forward position, the air flow source from the air supply source (14) is switched from the forward piping (22) to the backward piping (21), and the piston rod (1b) moves backward. When the retreat position is reached, the air flow supply source from the air supply source (14) is switched from the retreat pipe (21) to the forward pipe (22).
The forward piping (22) and the backward piping (21) each include a throttle valve (2), and one or both include pressure reducing valves (3, 4), and pressure reducing valves (3, 4) The throttle opening degree of the throttle valve (2) is adjusted, and the pressure of the air flow supplied to the pneumatic cylinder (1) by the forward piping (22) and the backward piping (21) is set to different values. As a result, the advance time required for the piston rod (1b) to advance from the rear end position to the advance position and the reverse time required to move back from the advance position to the reverse position are the following: When the forward piping (22) and the backward piping (21) have only a throttle valve, the difference is set to a value larger than the difference that can be set only by adjusting the throttle opening of the throttle valve. It is characterized by that.
[0006]
The time-measurement drive device for the pneumatic actuator according to claim 2 is the time-measurement drive device according to claim 1, wherein the advance pipe (22) includes a throttle valve (2) and a pressure reducing valve (3).
The advance time is set to be longer than the reverse time.
[0008]
DETAILED DESCRIPTION OF THE INVENTION
In FIG. 1, reference numeral 1 denotes a known pneumatic (air) cylinder having a piston 1a and a piston rod 1b. What is shown is a single-sided rod, but it may be a double-sided rod.
Reference numeral 20 denotes an L-shaped bracket attached to the threaded portion 1c at the front end (left end in FIG. 1) of the piston rod 1b, and its length is set slightly longer than the cylinder stroke.
Reference numerals 3a and 3b are protrusions provided on the bracket 20 for operating a flip toggle (lever) 7-1 of a mechanical switching valve 7 described later. The protrusion 3a is a rod front end side, and the protrusion 3b is a head (cylinder). It is provided at a location corresponding to the (rear end) side. The distance L between both protrusions is set within the cylinder stroke. FIG. 1 shows a state immediately after the projecting portion 3a that has been moved backward has collided with the flip toggle 7-1 and the backward piping 21 has been switched to the forward piping 22 side.
[0009]
Reference numeral 2 denotes a throttle valve (flow rate control mechanism) provided at both inlets 23 and 24 of the cylinder 1, and the one shown in the figure shows a meter-in control type. Of course, it is possible to use meter-out control, and it is not necessary to have the same specification (same aperture size).
Reference numerals 3 and 4 denote pressure reducing valves (flow rate control mechanisms) interposed between the throttle valve 2 and an outlet of a mechanical switching valve 7 described later, and reference numerals 5 and 6 denote pressure gauges. These pressure gauges 5 and 6 display the forward time and the backward time in parallel on the pressure display.
7 is a known mechanical switching valve, which is a 2-position 5-port valve. That is, the flow path (forward piping 22 and backward piping 21) from the air supply source 14 to the cylinder 1 is switched by tilting the flip toggle 7-1 shown in FIG. The tilted toggle has a structure that keeps its position unless it depends on external force. In FIG. 4, 26 is a body, 27 is a push rod, 28 is a cam, 29 is a valve spring, 30 is a head cover, and 31 is a toggle spindle.
[0010]
Reference numeral 8 in FIG. 1 is a supply pressure reducing valve connected to the inlet 26 of the mechanical switching valve 7. Reference numeral 9 denotes a filter, 10 denotes a stop valve, 11 denotes a pressure gauge for visually checking the pressure reduction of the pressure reducing valve 8, and 12 denotes a pneumatic actuator such as a pneumatically driven continuous operation pump, a motor, and a cylinder.
13 is an external connection port of a control box 25 communicated with a circuit (retracting pipe 21) from the mechanical switching valve 7 to the pressure reducing valve 4 by a pipe 13a, and is connected to the pneumatic actuator 12 through the pipe 13b. The 12 outlets communicate with the single line distribution valve 15 via a pipe 13c. Reference numeral 16 denotes a plurality of lubrication points. In addition, although the thing of illustration shows the thing which installed the external connection port 13 only in the pressure-reduction valve 4 side, it is also possible to provide in the pressure-reduction valve 3 side (advance piping 22), and also providing both in the pressure-reduction valve. The external connection port on the 3 side may be connected to another pneumatic actuator (not shown). 14a is an air supply port.
[0011]
The operation of the embodiment (apparatus) described above is as follows.
Pressurized air (for example, factory air) supplied from the air supply source 14 passes through the stop valve 10 and the filter 9, and the pressure supplied to the pneumatic actuator 12 and the pressure reducing valves 3 and 4 is set by the pressure reducing valve 8. This operation is performed while looking at the scale (supply source pressure) of the pressure gauge 11 with the adjustment handle 11a of FIG.
Further, in the state of FIG. 1, the mechanical switching valve 7 flows into the head side of the cylinder 1 through the pressure reducing valve 3 and the throttle valve 2, and the piston rod 1b is advanced to the left in the drawing. The advance time to reach the stroke end is set by adjusting the throttle openings of the pressure reducing valve 3 and the throttle valve 2. This operation is performed while looking at the scale of the pressure gauge 5 (pump activation time meter) with the adjustment handle 5a of FIG. In the case of centralized refueling, the pump activation time (standby time or the advance time) is approximately 1 to 4 hours.
With this control, the piston rod 1b slowly moves forward, and when it is close to the stroke end, the projection 3b of the bracket 20 tilts the flip toggle 7-1 of the mechanical switching valve 7. By being tilted, the switching valve 7 is switched, and the flow of pressurized air is switched. This time, the pressure reducing valve 4 reaches the throttle valve 2 and flows into the rod side of the cylinder 1, and the piston rod 1b is moved to the piston rod 1b in FIG. Move back to the right.
The reverse time is set by adjusting the throttle opening of the pressure reducing valve 4 and the throttle valve 2. This operation is performed while looking at the scale of the pressure gauge 6 (pump operating hour meter) with the adjustment handle 6a of FIG. In the case of centralized refueling, the pump operation time is approximately 1 to 10 minutes.
With this control, the piston rod 1b moves backward, and when it is close to the stroke end shown in FIG. 1, the projection 3a of the bracket 20 tilts the flip toggle 7-1 of the switching valve 7. By tilting, the flow path is switched, the supply of pressurized air to the pneumatic actuator 12 is stopped, the actuator 12 stops at the position shown in FIG. 1, and the piston rod 1b starts moving forward. Repeat operation.
[0012]
In the above-described embodiment, the air supply source 14 is described as air pressure such as factory air. However, instead of the air supply source 14, a cylinder filled with a gas such as nitrogen, oxygen, argon or the like at a predetermined pressure is used. It is also possible. Since the sealing pressure of the business gas cylinder is approximately 15 Mpa (150 kg / cm 2), the pressure can be reduced to 1 Mpa (10 kg / cm 2) or less by a pressure reducing valve and supplied to the apparatus. Further, for example, by appropriately selecting the cross-sectional area of the reverse piping 21, one or both of the pressure reducing valve 4 and the throttle valve 2 can be omitted. As described above, “air pressure” in the present invention is used to include a gas pressure such as nitrogen, oxygen, and argon sealed in a cylinder at a predetermined pressure. Therefore, the “air pressure” may be “nitrogen pressure”, “oxygen pressure”, or “argon pressure”.
[0013]
【The invention's effect】
According to the invention (apparatus) of claims 1 and 2, since it can be controlled only by pneumatic pressure (including the gas pressure) without using electricity, there is an effect on repeated operation of pneumatic actuators for explosion-proof areas, In particular, a significant cost reduction can be expected.
If the single-line distribution valve 15 is connected to the pneumatic actuator 12 (centralized oil pump) shown in FIG. 1, a large number of lubrication points 16 can be automatically and automatically lubricated. Further, when a motor or cylinder is employed instead of the pump as an example of the pneumatic actuator 12, it can be used for repetitive conveyance and rotation of objects.
In the illustrated embodiment, if the stop valve 10 is closed and the supply of air is cut off, there is an advantage that the entire stop can be quickly performed.
[Brief description of the drawings]
FIG. 1 is a system diagram when the present invention is applied to a central fueling system.
FIGS. 2A and 2B are a schematic plan view and a schematic front view of the apparatus, respectively.
FIG. 3 is a system diagram of a centralized oil supply device in which the present invention is applied to a pneumatic grease pump.
FIG. 4 is a schematic front view for explaining a flip toggle mechanism.
[Explanation of symbols]
1 Pneumatic cylinder 1a Piston 1b Piston rod 2 Throttle valve (an example of a flow rate adjusting mechanism)
3, 4 Pressure reducing valve (an example of flow rate adjustment mechanism)
3a, 3b Protrusion 7 Mechanical switching valve 12 Pneumatic actuator 21 Back piping 22 Forward piping

Claims (2)

The piston rod (1b) having the piston (1a) of the pneumatic cylinder (1) is moved into the pneumatic cylinder (1) by using the air flow from the air supply source (14) for supplying the air flow. A pneumatic actuator timing drive device that repeatedly reciprocates between the forward position and the rear end position, and operates the pneumatic actuator (12) in accordance with the reciprocal movement,
A forward piping (22), a backward piping (21), and a mechanical switching valve (7);
The advance pipe (22) is for advancing the piston rod (1b) from the retracted position to the advanced position in response to the supply of airflow,
The retreat pipe (21) is for retreating the piston rod (1b) from the advance position to the retreat position in response to the supply of airflow.
The mechanical switching valve (7) includes a function of switching the air supply destination from the air supply source (14) to the forward piping (22) or the backward piping (21), and the piston rod (1b) When the forward movement position is reached and the forward movement position is reached, the supply destination of the air flow is switched from the forward movement pipe (22) to the backward movement pipe (21), and the piston rod (1b) moves backward and reaches the backward movement position. The air flow supply destination is switched from the backward piping (21) to the forward piping (22).
The forward piping (22) and the backward piping (21) each include a throttle valve (2), and one or both include pressure reducing valves (3, 4), and the pressure reducing valve (3 4) and the throttle opening of the throttle valve (2) are adjusted, and the pressure of the air flow supplied to the pneumatic cylinder (1) by the forward pipe (22) and the reverse pipe (21) is different. Thus, the forward time required for the piston rod (1b) to advance from the rear end position to the forward position and the reverse time required to retract from the forward position to the reverse position are the forward time and the reverse time. When the forward piping (22) and the backward piping (21) have only the throttle valve, the difference is set to a value that is larger than the difference that can be set only by adjusting the throttle opening of the throttle valve. A time drive device for a pneumatic actuator, characterized in that The forward piping (22) includes a throttle valve (2) and a pressure reducing valve (3).
The time-measurement drive device of the pneumatic actuator according to claim 1, wherein the advance time is set to be longer than the reverse time.

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