JP5578502B2 - speed controller - Google Patents

Description

  The present invention relates to a speed controller, and more particularly to a speed controller that is connected to an external cylinder and controls the operating speed of the external cylinder.

  In an automatic equipment line for assembling mechanical devices and electronic devices, devices using cylinders are frequently used. However, if the speed of the cylinder is increased, the cycle time can be reduced. However, there is a problem that the impact during operation is increased and the cylinder life is shortened. Therefore, there are many cases where the cylinder speed cannot be increased.

In view of this, technology has been developed to mitigate the impact of the cylinder so that the impact during operation does not increase even when the cylinder speed is increased.
As an example, a pneumatic cylinder with a cushion mechanism described in Patent Document 1 is disclosed. The cylinder is intended to relieve impact during operation by providing a cushion mechanism for relieving impact on the cylinder itself.

JP 2003-254303 A

  However, in the device disclosed in Patent Document 1, for example, an impact mitigation mechanism must be designed and incorporated for each cylinder according to its diameter and stroke, so that it lacks versatility and increases costs. There was a problem.

  The present invention has been made in view of the above circumstances, and can perform the operation in one stroke of the cylinder in two stages of high speed and low speed, thereby simultaneously solving the conflicting problems of increasing the speed of the cylinder and mitigating the shock during operation. An object of the present invention is to provide a low-cost speed controller that can be connected to various cylinders and can be adjusted to an optimum operation speed for each cylinder.

  As an embodiment, the above-described problem is solved by a solution as disclosed below.

In the disclosed speed controller, one end is connected to an external fluid supply source, the other end is connected to an external cylinder, a first flow path for allowing fluid to pass from the external fluid supply source to the external cylinder, and one end of the speed controller A second flow path connected to an external cylinder and having the other end connected to an exhaust port to allow fluid to pass from the external cylinder to the exhaust port; and a fluid flow rate provided in the middle of the second flow path A first throttle valve that adjusts the flow rate, a switching means that switches between a throttle position that adjusts the flow rate of fluid by the first throttle valve, and an open position that is not adjusted, and the open position in the switching means Adjusting means for adjusting a time until switching from the throttle position to the throttle position, the switching means has a slide valve as a switching valve for switching between the throttle position and the open position, and The A first urging means for applying an urging force to one end side of the id valve and a second urging means for applying an urging force to the other end side. The urging force by the first urging means is the second urging force. When the slide valve is switched to the open position when the urging force is greater than the urging force by the urging means, and when the urging force by the second urging means is greater than the urging force by the first urging means The slide valve is switched to the throttle position, and the first urging means has a chamber in which a fluid is stored and communicates between the external fluid supply source and the chamber and passes the fluid. And a third flow path that communicates between the chamber and one end side of the slide valve to allow fluid to pass therethrough, according to the amount of fluid stored in the chamber The sliding force is applied to the urging force generated as Characterized in providing the one end side.
According to this, by using it connected to the external cylinder, the operation in one stroke of the external cylinder can be performed in two stages of high speed and low speed. Accordingly, it is possible to realize speeding up by high speed movement and impact mitigation at the end of operation by low speed movement. Furthermore, it is possible to arbitrarily adjust the switching timing by the switching means.

In addition, it is possible to switch between the throttle position and the open position of the first throttle valve with a simple structure using the switching valve.

In addition, it is possible to switch the first throttle valve by operating the slide valve using the first urging means and the second urging means.

In addition, the pressure generated by storing the fluid in the chamber can be applied to the slide valve of the switching means as an urging force.

Moreover, it is preferable that the said adjustment means has a 2nd throttle valve which is provided in the middle of the said 3rd flow path, and adjusts the flow volume of the fluid.
According to this, the flow rate of the fluid discharged from the chamber can be adjusted, and as a result, the switching timing by the switching means can be arbitrarily adjusted.

The exhaust port is preferably provided with a third throttle valve for adjusting the flow rate of the fluid to be passed.
According to this, it is possible to arbitrarily adjust the cylinder speed when the external cylinder moves at a high speed.

Alternatively, the exhaust port may be configured to be open to the atmosphere.
According to this, since it is possible to move the external cylinder at a high speed and no equipment such as a throttle valve is provided, the manufacturing cost can be reduced.

The second biasing means preferably includes a spring member, and applies a biasing force generated as a resilient force of the spring member to the other end side of the slide valve.
According to this, it becomes possible to give the elastic force by a spring member to the slide valve of a switching means as urging | biasing force.

The first flow path and the second flow path are connected via a three-way branch shuttle valve, and the flow path between the shuttle valve and the outer cylinder is the first flow path. It is preferable that only one channel is provided as a shared channel between the path and the second channel.
According to this, since a part of the first flow path and the second flow path can be configured as a shared flow path, the structure is simplified compared to a configuration in which each is provided as a separate flow path. And the manufacturing cost can be reduced.

  According to the disclosed speed controller, it is possible to simultaneously increase the speed of the cylinder and reduce the impact during operation. Therefore, the cycle time in the automatic equipment line can be reduced and the life of the cylinder can be extended. it can. Furthermore, it has the versatility that it can be connected to various cylinders, and the cost can be reduced. Therefore, it is possible to reduce the initial cost when installing the line and to improve the yield when the line is operating.

It is the schematic (front sectional drawing) which shows the example of the speed controller which concerns on 1st embodiment of this invention. It is a circuit diagram of the speed controller shown in FIG. It is an external cylinder speed-impact measurement figure in the speed controller which concerns on the conventional embodiment, and the speed controller which concerns on this embodiment. It is an external cylinder operation | movement-impact measurement figure in the speed controller which concerns on the conventional embodiment, and the speed controller which concerns on this embodiment. It is the schematic (front sectional drawing) which shows the example of the speed controller which concerns on 2nd embodiment of this invention. FIG. 6 is a circuit diagram of the speed controller shown in FIG. 5. It is the schematic (front sectional drawing) which shows the example of the speed controller which concerns on 3rd embodiment of this invention. FIG. 8 is a circuit diagram of the speed controller shown in FIG. 7.

(First embodiment)
Hereinafter, a first embodiment of the present invention will be described in detail with reference to the drawings. FIG. 1 is a front sectional view (schematic diagram) showing an example of a speed controller 1 according to the present embodiment, and FIG. 2 is a circuit diagram thereof. Note that components having the same function are denoted by the same reference symbols throughout the drawings for describing the embodiments, and the repetitive description thereof may be omitted.

  The speed controller 1 according to the present embodiment is connected to, for example, an external cylinder S that constitutes an automatic equipment line or the like, and controls the operating speed of the external cylinder S.

  As shown in FIGS. 1 and 2, the speed controller 1 has one end connected to an external fluid supply source (not shown) via a first pipe joint 12 and the other end connected to the outside via a second pipe joint 14. A first flow path 16 connected to the cylinder S to allow fluid (for example, compressed air) to pass from the external fluid supply source to the external cylinder S, and one end to the external cylinder S via the second pipe joint 14. Connected, the other end is connected to the exhaust port, and a second flow path 18 is provided to allow fluid (for example, air) to pass from the external cylinder S to the exhaust port 32. In the present embodiment, the first flow path 16 and the second flow path 18 are connected via a three-way branch shuttle valve 20, and the flow path between the shuttle valve 20 and the external cylinder S is The first flow path 16 and the second flow path 18 are configured as a shared flow path. According to this, the structure can be simplified and the manufacturing cost can be reduced.

  A first throttle valve 22 that adjusts the flow rate of the fluid passing therethrough is provided in the middle of the second flow path 18. Furthermore, switching means 24 is provided for switching between a throttle position where the flow rate of the fluid is adjusted by the first throttle valve 22 and an open position where no adjustment is made. The switching means 24 includes a switching valve that switches between the throttle position and the open position. The switching means 24 in the present embodiment has a slide valve 26 as a switching valve, and applies a biasing force to the first biasing means 28 that applies a biasing force to the one end 26 a side of the slide valve 26 and a biasing force to the other end 26 b side. Second urging means 30. As an action thereof, the slide valve 26 is switched to the open position when the urging force by the first urging means 28 is larger than the urging force by the second urging means 30. On the other hand, when the urging force by the second urging means 30 is larger than the urging force by the first urging means 28, the slide valve 26 is switched to the throttle position.

More specifically, in the slide valve 26 of FIG. 1, the right half X is illustrated as the state in which the slide valve 26 is switched to the throttle position, and the left half Y is the slide valve 26 to the open position. It is illustrated as a state where switching has been performed.
Here, when the slide valve 26 is switched to the throttle position of the right half X, one end of the slide valve 26 is connected to the lower end 22 a of the first throttle valve 22. Therefore, by rotating the screw-type first throttle valve 22 and moving the lower end portion 22a up and down, the interval between the throttle portions 22x can be adjusted.
On the other hand, when the slide valve 26 is switched to the throttle position of the left half Y, one end of the slide valve 26 is separated from the lower end 22 a of the first throttle valve 22. Therefore, not only the adjustment by the first throttle valve 22 is not performed, but also the interval between the throttle portions 22y becomes larger than a predetermined value, and an open state where the throttle does not act on the passing fluid is brought about.

  The end portion of the second flow path 18 is configured as an exhaust port 32 that exhausts the fluid discharged from the external cylinder S and passing through the second flow path 18. In the present embodiment, the exhaust port 32 is provided with a third throttle valve 34 that adjusts the flow rate of the fluid to be passed. According to this, the flow rate of the fluid exhausted from the exhaust port 32 can be adjusted. Although details will be described later, the speed of the high speed side operation of the external cylinder S can be adjusted by adjusting the flow rate.

  Note that the switching means and the switching valve are not limited to the above configuration, and other known configurations can be employed.

Next, the first urging means 28 and the second urging means 30 will be described.
The first urging means 28 in the present embodiment has a chamber 36 in which a fluid is stored, and a third flow that allows fluid to pass between an external fluid supply source (not shown) and the chamber 36. The channel 38 and the fourth flow path 40 that allows the fluid to pass through the chamber 36 and the one end 26a side of the slide valve 26 are configured. According to this, since a fluid (for example, compressed air) is stored in the chamber 36 through the third flow path 38, a pressure corresponding to the storage amount of the fluid is generated, so that the pressure is slid as an urging force. It can be given to the one end 26a side of the valve 26. On the other hand, by discharging the fluid (here, air) from the chamber 36 through the third flow path 38, the amount of fluid stored decreases and the pressure decreases, so the urging force gradually decreases.

  On the other hand, the second urging means 30 in the present embodiment includes a spring member 30a. According to this, the urging force generated as the elastic force of the spring member 30a can be applied to the other end 26b side of the slide valve 26. The urging force by the second urging means 30 has a predetermined magnitude determined by the spring constant of the spring member 30a.

  Therefore, according to the configuration of the first urging means 28 and the second urging means 30 described above, the amount of fluid stored in the chamber 36 is larger than a predetermined amount, and the pressure by the fluid is lower than the predetermined value. When it becomes larger, the biasing force by the first biasing means 28 due to the pressure becomes larger than the biasing force by the second biasing means 30 (a predetermined force determined by the spring constant of the spring member 30a). . On the other hand, when the amount of fluid stored in the chamber 36 is smaller than a predetermined amount and the pressure by the fluid is smaller than a predetermined value, the urging force by the first urging means 28 due to the pressure is The biasing force by the second biasing means 30 (a predetermined force determined by the spring constant of the spring member 30a) is smaller.

Next, adjustment means for adjusting the time until the switching means 24 switches from the open position to the aperture position will be described.
The adjusting means in this embodiment includes a second throttle valve 42 that is provided in the middle of the third flow path 38 and adjusts the flow rate of the fluid. According to this, since the flow rate of the fluid passing therethrough can be reduced by setting the second throttle valve 42 in the direction in which the second throttle valve 42 is throttled, the discharge speed of the fluid from the chamber 36 can be reduced, and the first urging means The speed at which the urging force by 28 is reduced can be reduced. That is, the timing at which the slide valve 26 is switched from the open position to the throttle position can be relatively delayed.
On the other hand, since the flow rate of the passing fluid can be increased by setting the second throttle valve 42 in the opening direction, the discharge speed of the fluid from the chamber 36 can be increased, and the first urging means 28 The speed at which the urging force decreases can be increased. That is, the timing at which the slide valve 26 is switched from the open position to the throttle position can be made relatively fast.
In this way, by adjusting the flow rate of the fluid (fluid discharged from the chamber 36) by the second throttle valve 42, the switching means 24, that is, the timing for switching between the open position and the throttle position in the slide valve 26 can be arbitrarily set. It becomes possible to adjust.

However, since the second throttle valve 42 is provided in the third flow path 38, not only when the fluid is discharged from the chamber 36, but also when the fluid is stored in the chamber 36, the throttle action occurs. Therefore, the problem that a storage speed falls may arise. Therefore, in this embodiment, by separately providing a storage channel 46 provided with a check valve 44 in the middle, when the fluid is stored in the chamber 36, the second throttle valve 42 is affected by the throttle action. Without the need to store at high speed.
The adjusting means is not limited to the above configuration.

  Next, the operation of the speed controller 1 having the above configuration will be described with reference to the circuit diagram of FIG.

First, FIG. 2 (a) shows a case where the outer cylinder S performs an end limit (outward) operation.
First, fluid (for example, compressed air) is supplied from an external fluid supply source (not shown) connected via the first pipe joint 12, and the fluid passes through the first flow path 16 and is on one end side of the external cylinder S. Is supplied to the inside (arrow A), and the outer cylinder S performs a limit-bound (outward) operation. At this time, the internal fluid (here, air) is discharged from the other end side of the external cylinder S (arrow B).
At this time, a fluid (here, compressed air) is also supplied from an external fluid supply source (not shown) through the first flow path 16 to the third flow path 38 that is branched and formed in the middle (here, compressed air) ( Arrow C1). On the way, the fluid passes through two flow paths: a third flow path 38 (arrow C2) provided with the second throttle valve 42 and a storage flow path 46 (arrow C3) provided with the check valve 44. Passes and is stored in the chamber 36.
As a result, a pressure is generated in the fluid stored in the chamber 36 (here, compressed air), and the pressure is applied to one end (26a in FIG. 1) of the slide valve 26 via the fourth flow path 40. Acts (arrow D). This is the urging force by the first urging means 28.

Next, FIG. 2B shows a case where the outer cylinder S performs a return limit (return path) operation (high speed operation).
First, fluid (here, compressed air) is supplied from an external fluid supply source (not shown) through the other end of the external cylinder S to the inside (arrow E), and the external cylinder S performs a return limit (return path) operation. At this time, the fluid (here, air) inside the outer cylinder S is discharged from one end side of the outer cylinder S to the second flow path 18 connected via the second pipe joint 14 (arrow F). .
At the time when the discharge from the external cylinder S is started, the amount of fluid stored in the chamber 36 is larger than a predetermined amount and the pressure by the fluid is larger than a predetermined value. The urging force by the second urging means 30 is larger than the urging force by the second urging means 30, and the switching means 24, that is, the slide valve 26 is switched to the open position where the squeezing action by the first throttle valve 22 is not performed. ing. Therefore, the fluid discharged from the external cylinder S is discharged to the exhaust port 32 without being subjected to the throttle action by the first throttle valve 22, and the throttle action by the third throttle valve 34 provided in the exhaust port 32. In response, the flow rate is adjusted and then exhausted (arrow G).
By the action of the third throttle valve 34, it is possible to adjust when the return limit (return path) operation of the external cylinder S is performed at high speed. For example, by setting the third throttle valve 34 closer to the open state, exhaust can be performed at a high speed, that is, the fluid discharge speed from the external cylinder S can be increased, so that the return limit (return path) of the external cylinder S can be reduced. The operation (high speed operation) can be performed at a higher speed. On the other hand, by setting the third throttle valve 34 to gradually narrow, the return limit (return path) operation (high speed operation) of the external cylinder S can be gradually decreased from the high speed.

Here, when the outer cylinder S performs the return limit (return path) operation, the fluid is also discharged from the chamber 36 (arrow H). Therefore, when the discharge from the external cylinder S is started, the fluid pressure in the chamber 36 is high, but the fluid discharge gradually proceeds from the chamber 36, so that the discharge from the external cylinder S is started. At the time point, the fluid pressure in the chamber 36 is reduced, so that the urging force by the first urging means 28 is smaller than the urging force by the second urging means 30. At that time, the switching means 24, that is, the slide valve 26 is switched to the throttle position where the first throttle valve 22 performs the throttle action. Based on this, switching to the return limit (return path) operation (low speed operation) of the external cylinder S shown below is performed.
As described above, the timing of switching can be adjusted by adjusting the flow rate of the fluid discharged from the chamber 36 by the second throttle valve 42.

Finally, FIG. 2C shows a case where the outer cylinder S performs a return limit (return path) operation (low speed operation).
As described above, when the switching means 24, that is, the slide valve 26 is switched to the throttle position where the first throttle valve 22 performs the throttle action, the fluid discharged from the external cylinder S is the first throttle valve 22. After being subjected to the throttling action, the gas is discharged to the exhaust port 32 and exhausted from the exhaust port 32 (arrow I). In the present embodiment, the throttle amount by the first throttle valve 22 is set to be narrower than the throttle amount by the third throttle valve 34. Therefore, when the flow rate adjustment by the first throttle valve 22 shown in FIG. 2C is performed, the external flow rate adjustment by the third throttle valve 34 shown in FIG. The squeezing action received by the fluid discharged from the cylinder S becomes a state in which the squeezing is further performed. That is, the flow rate adjustment of the fluid discharged from the external cylinder S is controlled by the first throttle valve 22. in this way. When the flow rate adjustment of the fluid discharged from the external cylinder S is switched from the third throttle valve 34 to the first throttle valve 22, the operating speed of the external cylinder S is switched from high speed to low speed. It will be.
Therefore, the operation of the return limit (return path) of the external cylinder S can be adjusted at a low speed by the action of the first throttle valve 22. For example, by setting the first throttle valve 22 to be narrower, the exhaust gas can be slowed down, that is, the fluid discharge speed from the external cylinder S can be slowed. Therefore, the return limit (return path) operation of the external cylinder S (low speed) Operation) can be made slower. On the contrary, by setting the first throttle valve 22 to be close to the open state, the return limit (return path) operation (low speed operation) of the external cylinder S can be gradually increased from the low speed.
Thus, since the speed of the external cylinder S can be reduced when the stroke end is reached, the impact can be reduced.

  Here, FIG. 3 shows an external cylinder speed-impact measurement diagram in the speed controller according to the conventional embodiment and the speed controller 1 according to the present embodiment. Here, as a conventional embodiment, a speed controller that cannot perform speed switching is taken as an example (the same applies in FIG. 4 described later). In FIG. 3, (1) shows the speed in the speed controller according to the conventional embodiment, and (2) shows the speed in the speed controller according to the present embodiment. Further, (3) shows an impact when the return limit (return path) of the speed controller according to the conventional embodiment is stopped, and (4) shows an impact when the return limit (return path) of the speed controller according to the present embodiment is stopped. Is shown.

  As is apparent from FIG. 3, when the speed controller according to the conventional embodiment is used, the speed is constant ((1) in FIG. 3), and the impact is not relieved ((3) in FIG. 3). On the other hand, when the speed controller 1 according to the present embodiment is used to switch the speed in the middle of one stroke (return limit), for example, the speed before switching is set to the double speed of (1) and the speed after switching. Is set to 1/2 speed of (1) ((2) of FIG. 3), the required time for moving the same distance is shorter than that of (1) (that is, speeding up in the whole process is achieved). In addition, the effect of reducing the impact was obtained ((4) in FIG. 3).

  Next, FIG. 4 shows an external cylinder operation-impact measurement diagram in the speed controller according to the conventional embodiment and the speed controller 1 according to the present embodiment. In FIG. 3, (1) shows the speed in the speed controller according to the conventional embodiment, and (2) shows the speed in the speed controller according to the present embodiment. Further, (3) shows an impact when the return limit (return path) of the speed controller according to the conventional embodiment is stopped, and (4) shows an impact when the return limit (return path) of the speed controller according to the present embodiment is stopped. Is shown.

  As is clear from FIG. 4, in an experiment in which a predetermined distance (for example, 100 [mm]) is moved, the speed controller 1 according to the present embodiment and the speed controller according to the conventional embodiment are operated similarly, When only the speed controller 1 according to the present embodiment is decelerated when the return limit is stopped (immediately before the stroke end), the speed controller 1 according to the present embodiment has an impact 1 / lower than that of the speed controller according to the conventional embodiment. Experimental results reduced to 10 were obtained. In this example, the speed controller 1 according to the present embodiment is only 0.33 [sec] longer than the speed controller according to the conventional embodiment.

  Thus, the speed controller 1 according to the present embodiment can switch the moving speed of the external cylinder in two stages. Furthermore, by adjusting the flow rate before switching, it is possible to adjust the cycle of the external cylinder to increase the speed, and by adjusting the flow rate after switching, the external cylinder is stopped, that is, near the stroke end. The moving speed can be decelerated, and the impact can be adjusted (relaxed).

(Second embodiment)
Next, the speed controller 1 according to the second embodiment will be described. The speed controller 1 according to this embodiment has the same basic configuration as that of the first embodiment described above, but has a difference in the arrangement structure of the first throttle valve 22 in particular. Hereinafter, the present embodiment will be described focusing on the difference.

As shown in the front sectional view (schematic diagram) of FIG. 5, the speed controller 1 according to the present embodiment has a configuration in which two exhaust ports 32 (32x and 32y in the figure) are provided. The configuration in which the third throttle valve 34 is provided in one exhaust port 32x is the same as that in the first embodiment described above, but the configuration in which the first throttle valve 22 is provided in the other exhaust port 32y is characteristic. .
Further, the point that the switching unit 24 is configured to include the slide valve 26 and the principle of the switching operation are the same as those of the first embodiment described above. However, the difference is that the switching unit 24, that is, the slide valve 26 is switched. The exhaust path of the fluid discharged from the external cylinder S is switched between the exhaust port 32x and the exhaust port 32y.

  A circuit diagram according to this embodiment is shown in FIG. When the speed of the return limit (return path) of the external cylinder S (ie, at low speed) is adjusted by the action of the first throttle valve 22, the fluid passes only through the first throttle valve 22, and the third throttle valve The point of not passing through 34 is an operational feature, which is different from the first embodiment described above.

  However, as in the first embodiment described above, the switching means 24, that is, the slide valve 26 is changed from the open position (the position where the fluid flow rate is not adjusted by the first throttle valve 22) to the throttle position (the first position). Switching to the position where the flow rate of the fluid is adjusted by the throttle valve 22), the flow rate adjustment of the fluid discharged from the external cylinder S is changed from the adjusted state by the third throttle valve 34 to the first throttle valve 22. Switching to the adjustment state is performed.

  In this way, the switching means 24, that is, the slide valve 26 is adjusted from the open position (the position where the fluid flow rate is not adjusted by the first throttle valve 22) to the throttle position (the fluid flow rate is adjusted by the first throttle valve 22). Switching to the position where the external cylinder S is switched) provides the same effect as that of the first embodiment described above in that the operation speed of the external cylinder S is switched from high speed to low speed. Is done.

(Third embodiment)
Next, the speed controller 1 according to the third embodiment will be described. The speed controller 1 according to this embodiment has the same basic configuration as that of the first embodiment described above, but has a difference particularly in a structure in which the third throttle valve is not provided. Hereinafter, the present embodiment will be described focusing on the difference.

  As shown in the front sectional view (schematic diagram) of FIG. 7, the speed controller 1 according to the present embodiment has a structure in which the exhaust port 32 is opened to the atmosphere without providing a third throttle valve. Since the third throttle valve is not provided, a simple structure can be obtained, and the manufacturing cost can be reduced.

  A circuit diagram according to the present embodiment is shown in FIG. In the first embodiment described above, the third throttle valve 34 (see FIGS. 1 and 2) can be used to adjust the speed (here, high speed) of the return limit (return path) of the external cylinder S. On the other hand, in this embodiment, the speed of the return limit (return path) of the external cylinder S (high speed here) cannot be arbitrarily adjusted, and depends on the flow rate at which the fluid is exhausted by opening to the atmosphere. The predetermined speed will be set.

  In the present embodiment, the switching means 24, that is, the slide valve 26 is moved from the open position (the position where the flow rate of the fluid is not adjusted by the first throttle valve 22) to the throttle position (the flow rate of the fluid by the first throttle valve 22). Is switched to the adjustment position by the first throttle valve 22 from the atmosphere open state.

  In this way, the switching means 24, that is, the slide valve 26 is adjusted from the open position (the position where the fluid flow rate is not adjusted by the first throttle valve 22) to the throttle position (the fluid flow rate is adjusted by the first throttle valve 22). Switching to the position where the external cylinder S is switched) provides the same effect as that of the first embodiment described above in that the operation speed of the external cylinder S is switched from high speed to low speed. Is done.

As described above, according to the disclosed speed controller, the operation in one stroke of the cylinder can be performed in two stages of high speed and low speed, thereby simultaneously solving the problems of speeding up the cylinder and reducing shock during operation. It becomes possible to do. In addition, since it has versatility that can be connected to various cylinders, a dedicated design for each cylinder is not required and the cost is low, and it is extremely easy to adjust to an optimum operation speed for each cylinder.
As a result, the cycle time in the automatic equipment line can be reduced and the life of the cylinder can be extended. Therefore, it is possible to reduce the initial cost when installing the line and to improve the yield when the line is operating.

  Needless to say, the present invention is not limited to the embodiment described above, and various modifications can be made without departing from the present invention.

DESCRIPTION OF SYMBOLS 1 Speed controller 16 1st flow path 18 2nd flow path 22 1st throttle valve 24 Switching means 26 Slide valve 28 1st biasing means 30 2nd biasing means 32 Exhaust port 34 3rd throttle valve 36 Chamber 38 Third flow path 40 Fourth flow path 42 Second throttle valve (adjusting means)
S External cylinder

Claims (5)

A first flow path having one end connected to an external fluid supply source and the other end connected to an external cylinder to pass fluid from the external fluid supply source to the external cylinder;
A second flow path having one end connected to the external cylinder and the other end connected to an exhaust port, and allowing fluid to pass from the external cylinder to the exhaust port;
A first throttle valve provided in the middle of the second flow path to adjust the flow rate of the fluid;
A switching means for switching between a throttle position for adjusting the flow rate of the fluid by the first throttle valve and an open position for which adjustment is not performed;
Adjusting means for adjusting time until switching from the open position to the aperture position in the switching means ,
The switching means has a slide valve as a switching valve for switching between the throttle position and the open position, and includes a first urging means for applying an urging force to one end side of the slide valve and an other end side. Second urging means for applying urging force, and when the urging force by the first urging means is larger than the urging force by the second urging means, the slide valve is switched to the open position. And when the urging force by the second urging means is larger than the urging force by the first urging means, the slide valve is switched to the throttle position,
The first urging means has a chamber in which a fluid is stored, a third flow path that allows fluid to pass between the external fluid supply source and the chamber, and the chamber and the slide. A fourth flow path that allows fluid to pass through and communicates with one end side of the valve, and generates an urging force generated as a pressure corresponding to the amount of fluid stored in the chamber. Speed controller characterized by giving to the side . The adjusting means, the third speed controller according to claim 1, wherein the provided in the middle of the flow channel having a second throttle valve for adjusting the flow rate of the fluid. Wherein the exhaust port, the speed controller according to claim 1 or claim 2, characterized in that the third throttle valve for adjusting the flow rate of the fluid passing is provided. The exhaust port, the speed controller according to claim 1, characterized in that open to the atmosphere. The said 2nd biasing means has a spring member, and gives the biasing force which generate | occur | produces as the elastic force of this spring member to the other end side of the said slide valve, The any one of Claims 1-4 characterized by the above-mentioned. The speed controller according to one item.

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