JP3726930B2 - Actuator - Google Patents

Description

[0001]
【Technical field】
The present invention relates to an actuator including a cylinder and a piston housed in the cylinder so as to be movable in the longitudinal direction thereof, and fluid chambers a and b formed on both sides of the piston. More specifically, the present invention relates to an actuator capable of holding a piston in a fixed position and changing a moving speed in the middle of a piston stroke.
[0002]
[Prior art]
Hereinafter, an actuator mounted on an aircraft and operating a missile launcher that launches a missile from the aircraft will be described as an example.
[0003]
In general, an actuator that operates an aircraft missile launcher arbitrarily operates a plurality of positions such as a storage position in the aircraft or in the vicinity of the fuselage, and a standby position different from the storage position. That is, normally, such an actuator for a missile launcher needs to be operated slowly until “storage position → standby position” and instantaneously operated to push out the missile until “standby position → launch position”. .
[0004]
Furthermore, it is necessary to wait at the standby position until the missile is fired. For this purpose, it is necessary to hold the output piston at the third position in the middle of the stroke from the contracted position to the extended position.
[0005]
In order to realize such an operation, conventionally, there is a combination of a one-stage operation actuator that moves at a constant speed between a contracted position and an extended position and injection with explosives, or servo control of the actuator.
[0006]
[Problems to be solved by the invention]
However, the former, which combines injection with explosives, has problems of maintainability and safety, such as taking time to load explosives and the risk of explosion.
[0007]
On the other hand, the latter in which the actuator is servo-controlled has a problem in terms of cost due to a proportional control valve for making a hydraulic servo, a stepless position detector, and the like.
[0008]
In addition, the missile launcher, due to its nature, needs to make a quick transition from the standby state to the launch state, and because the piston operating speed at a specific position is fast, it is necessary to supply a large amount of hydraulic oil instantaneously. It becomes. When an actuator is designed with this large flow rate value, the valves, passages (piping), etc. become very large, causing problems in cost and weight. This problem also affected the size of the supply source of working fluid on the fuselage side.
[0009]
As a countermeasure, there is a case in which an accumulator is provided outside the actuator in order to compensate for the lack of the supply capacity of the working fluid. However, when the accumulator broke for some reason (for example, landing), there was a risk that the fragments would scatter and damage the aircraft.
[0010]
As described above, adding explosives to the actuator or making it into a servo has problems in terms of maintainability, safety, and cost.
[0011]
In addition, with the conventional actuator, when the fluid pressure supply is stopped or when the pressure supply source fails, the piston starts to move because it has no drag, and is released due to the missile launcher's own weight during parking. There is a problem. As a countermeasure, there is a method of providing a lock mechanism in the actuator, but there is a problem in cost because the structure becomes complicated.
[0012]
OBJECT OF THE INVENTION
An object of the present invention is to solve the problems associated with the prior art described above and to provide an actuator having at least a multistage control function and a speed change function for each stage control of the multistage control function.
Furthermore, the present invention preferably provides an actuator having a function of suppressing the flow rate of a working fluid or a function of restraining a piston when the hydraulic pressure is OFF, as shown in the embodiments.
[0014]
[Means for Solving the Problems]
In the present invention, a cylinder and a piston housed in the cylinder so as to be movable in the longitudinal direction thereof are formed , and fluid chambers a and b are formed on both sides of the piston. The cylinder has a large inner diameter portion, a small inner diameter portion, Are connected in the longitudinal direction, and a projecting portion extending in the longitudinal direction of the cylinder projects from the end surface on the small inner diameter side into the cylinder, and the piston is slidably fitted into the small inner diameter portion of the cylinder. A concave portion extending in a longitudinal direction from an end surface located on the small inner diameter side of the cylinder is formed, and the concave portion is slidably sealed to the protruding portion. fitted and, wherein the fluid chamber b the small-inner-diameter portion and the piston body of the cylinder is formed, the longitudinal direction at a connection portion extending magnitude inner diameter of said cylinder The free piston having a large and small outer diameter portion is fitted slidably sealed to said cylinder, being the fluid chamber a is formed by the large inner diameter portion and the piston rod of the cylinder,
The fluid chambers a and b are respectively connected to a high pressure port and a low pressure port of a three-position switching valve, and an input side port of the three-position switching valve is connected to a supply pipe for supplying high-pressure fluid, and a discharge side The port communicates with a discharge line for returning the return fluid ,
The three-position switching valve is
The high pressure port is connected to the fluid chamber a and the low pressure port is connected to the fluid chamber b, and the contraction force of the piston determined by the area difference between the inner diameter of the small diameter portion of the cylinder and the outer diameter of the piston rod acts on the piston. Storage mode to shrink ,
A step 1 mode in which the high-pressure port is connected to both fluid chambers a and b, and a force due to a difference in pressure receiving area facing both fluid chambers a and b of the piston body acts on the piston body to cause the piston to move in the extending direction; And
The high-pressure port and the fluid chamber b, the low-pressure port and the fluid chamber a are connected, the free piston in the fluid chamber a connected to the low-pressure port is lost, the high-pressure working fluid flows into the fluid chamber b, and the output piston Step 2 mode to stretch ,
The above object is achieved by an actuator characterized in that
[0015]
In the present invention, a specially structured cylinder as described above is adopted and a special three-position switching valve is connected to smoothly supply a large flow rate of working fluid during high-speed operation of the piston, and the piston is required. Sometimes it can be moved at high speed.
[0018]
In the actuator of the present invention, both the fluid chambers are connected to a three-position switching valve, and the operation of the actuator is controlled by operating the three-position switching valve. In addition, a pilot check valve that closes when the pressure in the fluid chamber is low is provided in a pipe line connected to the fluid chamber on the large inner diameter side of the cylinder of the actuator. When the supply of pressurized fluid is stopped, the pilot check valve eliminates fluid leakage, and the piston rod can be held in that state.
[0019]
【Example】
Hereinafter, the present invention will be described in more detail with reference to the drawings. FIG. 3 shows the structure of a missile launcher operated by an actuator according to the present invention.
[0020]
This missile launcher is provided in a body 1 such as a trunk or wing of an airplane (fighter), and a launcher base 2 can be moved up and down from the body 1 by the structure described below. The missile 3 is attached to be able to launch.
[0021]
In the steady state, the launcher base 2 is positioned at the storage position of the airframe 1. When the missile 3 is fired, the launcher base 2 is projected from the storage position to the lower standby position, and is in this state. Further, when the missile 3 is actually fired, the missile 3 is fired at a launch position further below the standby position.
[0022]
In order to reduce the influence on the airframe 1 when the missile 3 is fired and to increase the accuracy of the missile 3 hit, it is necessary to move to a launch position that is further away from the storage position. Moreover, in such a missile launcher, there is a relatively long time for movement from the storage position to the standby position, but it is necessary to move from the standby position to the launch position in a very short time.
[0023]
An example of the movement state of this missile launcher is shown in FIG. In FIG. 4, the horizontal axis represents the time axis, and the vertical axis represents the position of the launcher base 2.
[0024]
In FIG. 4, the missile 3 is normally in the retracted position near the fuselage 1. As described above, when it is necessary to launch the missile 3, the launcher base 2 moves from the retracted position to the intermediate standby position at a relatively low speed (step 1 down mode).
[0025]
When launching the missile 3, it is necessary to move rapidly from this standby position to the launch position in a very short time (step 2 down mode). In FIG. 4, the position immediately moves from the standby position to the launch position (that is, the step 1 down mode and the step 2 down mode are directly connected). However, it is often the case that the launcher base 2 is held as it is in the standby position until the launch. Moreover, it may return from the standby position to the retracted position without firing.
[0026]
When firing, the step 2 down mode from the standby position to the launch position needs to be moved within a short time competing for seconds, that is, the step 1 down mode is moving from the storage position to the standby position. It is necessary to move to the launch position at a much higher speed.
[0027]
Then, after the launch is finished, there is no need to rush to the storage position, so it is only necessary to return slowly.
[0028]
The structure of the missile launcher shown in FIG. 3 will be briefly described. The launcher base 2 and the airframe 1 are connected by two links L and M that are equal in length and provided in a cross shape. The midpoints of the two links L and M are connected to each other by a pin P so as to be pivotable.
[0029]
One link L is supported by a pin A so as to be swingable with respect to a fixed point of the fuselage 1, and the other side of the link L is pin-coupled to the launcher base 2 by a pin B.
[0030]
The tip of the other link M is slidably connected to a pin D slidably provided in a guide (not shown) extending in a horizontal direction from the pin A of the machine body 1. The other end of this is pin-coupled to the launcher base 2 by a pin C so as to be swingable.
[0031]
In the missile launcher device having the above-described configuration, the pin D of the link L is moved in the horizontal direction along the guide, so that the pin C at the other end of the link L becomes a line extending vertically from the pin A of the body 1. Move along. By this. The launcher base 2 that is pin-coupled with the pins B and C always moves up and down in parallel with the airframe 1.
[0032]
The cylinder 10 rear end of the actuator 10 according to the present invention is pivotally attached to the airframe 1 by a pin F, and the piston rod tip is connected to a link M by a pin E, and the actuator 10 is operated to open and close between the links L and M. The launcher base 2 is moved up and down by controlling the angle.
[0033]
Next, an actuator 10 according to the present invention will be described with reference to FIG. The actuator 10 includes a cylinder 20 and a piston 30 housed in the cylinder 20 so as to be movable in the longitudinal direction. Fluid chambers a and b are formed on both sides of the piston 30. As described above, the right end of the cylinder 20 is pin-connected to the airframe 1 by the pin F. The piston 30 includes a piston main body 31 and a piston rod 32 connected to the piston main body 31, and the tip of the piston rod 32 is pin-coupled to the link M by the pin E as described above.
[0034]
In Figure 1, the cylinder 20 has its inner diameter made larger in diameter 21 and a small diameter in the small diameter portion 22. Large diameter, an intermediate portion of the large and small in diameter 21 and 22 are attached while forming a step 23 It is in a state.
[0035]
Further, a protruding portion 24 protrudes from the right end portion of the cylinder 20 into the cylinder 20. On the other hand, the piston body 31 is adapted to fit into the small inside diameter portion 22 of the cylinder 20, between the peripheral surface of the small inside diameter portion 22 and the piston body 31 of the cylinder 20 is sealed by O-ring 41 and the piston body 31 is slidable relative to the small inside diameter portion 22. The piston 30 is formed with a recess 30 a extending from the right end to the middle, and the recess 30 a is adapted to fit with the protruding portion 24 of the cylinder 20. An O-ring 42 is also mounted between the projecting portion 24 of the cylinder 20 and the recessed portion 30a of the piston, and the piston 30 and the projecting portion 24 are slidably fitted in a sealing manner. Yes.
[0036]
The left end portion of the piston rod 32 is slidably fitted through an O-ring 45 in an opening 25 a formed in the end surface portion 25 on the large inner diameter side of the cylinder 20.
[0037]
Free piston 50 between the larger inside diameter portion 21 and the small inside diameter portion 22 of the further the cylinder 20 inside the cylinder 20 is adapted to fit. Free piston 50 has a concatenation of the small outer diameter portion 52 that fits into the small inside diameter portion 22 of the large outer diameter portion 51 and a cylinder 20 which fits into the large inside diameter portion 21 structure, large and small outer diameter portion A step 53 is formed between 51 and 52. Freedom between the large and small outer diameter portion 51, 52 and the magnitude in the diameter 21, 22 of the cylinder of the piston 50 is O-ring 43 and 44 is mounted, the free piston 50 is slidably sealingly cylinder 20 It is mated.
[0038]
Above (a portion of the fluid chamber a that is formed on the left side of the piston body 31) cylinder large in diameter 21 of the cylinder 20, check valve 70, communicates with the outlet port 60a of the three-position switching valve 60 via a conduit 71 are doing. Further, (part of cylinder small in diameter 21 of the cylinder 20) fluid chambers b formed in the right side of the piston body 31 of the cylinder 20, in addition to the outlet port 60b of the three-position switching valve 60 via a conduit 72 Communicating with The input side port 60c of the three-position switching valve 60 is in communication with a supply line 80 for supplying high pressure fluid, and the discharge side port 60d is in communication with a discharge line 85 for returning the return fluid. Further, a discharge passage 86 communicates between the discharge port pipe 85 and the intermediate portion of the free piston 50.
[0039]
Between the exhaust passage 86 communicating with the intermediate portion of the conduit 71 and the free piston 50 connected to vena diameter portion 21 of the aforementioned cylinder 20, it is provided with a thermal relief valve 75, the fluid chamber of the actuator 10 for some reason When the pressure in a becomes excessive due to heat, the pressure is released by the thermal relief valve 75 to prevent an accident.
[0040]
An accumulator 90 with gas and working fluid as a boundary is connected to the supply pipe line 80 to the three-position switching valve 60, and a charge valve 91 and a pressure transducer 92 are provided on the gas side of the accumulator 90. The supply working fluid is stored in advance in the accumulator 90 and can be supplied when necessary.
[0041]
Further, an accumulator 95 having a boundary between gas and working fluid is connected to the discharge pipe 85 from the three-position switching valve 60, and the discharge working fluid is temporarily supplied to the accumulator 95 by the pressure from the discharge pipe 85. It can be stored.
[0042]
The operation of the embodiment of the actuator of the present invention shown in FIG. 1 having the above configuration will be described below. The relationship between ON / OFF of the two # 1 and # 2 solenoids 61a and 61b of the three-position switching valve 60 and the operating state of the actuator is as shown in Table 1.
[0043]
[Table 1]
(Storage mode)
When the # 1 solenoid 61a of the three-position switching valve 60 is OFF and the # 2 solenoid 61b is ON or OFF, the three-position switching valve 60 is in the storage mode position shown in FIG. At this time, the three high-pressure port 60a of the position switching valve 60 and the fluid chamber a of the actuator 10, the low pressure port 60b leads the fluid chamber b, the outer diameter d1 of the inner diameter B2 and the piston rod 32 in the small diameter portion 22 of the cylinder 20 The contraction force of the piston determined by the area difference between and acts on the piston, and the piston rod 32 contracts.
[0044]
Further, when the supply of hydraulic pressure is cut off at this contracted position, the control pressure to the pilot check valve 70 is also cut off, and the check valve 70 can seal the fluid chamber a and prevent the piston 30 from extending. The piston 30 is restrained.
[0045]
If the working fluid in the sealed fluid chamber a is thermally expanded and the pressure in the fluid chamber a rises excessively, the thermal relief valve 75 is activated to release the working fluid in the fluid chamber a and cause the cylinder 20 to burst. prevent.
[0046]
(Step 1 down mode)
When the # 1 solenoid 61a of the three-position switching valve 60 is turned on and the # 2 solenoid 61b is turned off, the three-position switching valve 60 enters the step 1 down mode. At this time, the high-pressure port 60a of the three-position switching valve 60 is connected to both fluid chambers a and b, and the difference in pressure receiving area facing both fluid chambers a and b of the piston body 31, that is, the piston body facing the fluid chamber a. the pressure receiving area of 31 is the difference between the outer diameter d1 of the inner diameter B2 and the piston rod 32 in the small diameter portion 22 of the cylinder 20, the pressure receiving area of the piston body 31 facing the fluid chamber b is small in diameter 22 of the cylinder 20 Is the difference between the inner diameter B2 of the cylinder 20 and the outer diameter d2 of the protrusion 24 of the cylinder 20,
Piston pressure receiving area = (B2-d2)-(B2-d1) = d1-d2
A force obtained by multiplying the working fluid pressure by the pressure acts on the piston main body 31, and the piston 30 starts to move in the extending direction.
[0047]
At this time, the fluid chamber a is because they are pressurized, fluid chamber area difference of the both end faces in the free piston 50 provided in a, i.e. the inner diameter B1 and the small in the large diameter portion 21 of the cylinder 20 The difference between the inner diameter B2 of the diameter portion 22, that is, the force obtained by multiplying the pressure receiving area of B1-B2 by the working fluid pressure acts, and the free piston 50 is pushed rightward in FIG. A stopper is formed in the cylinder 20 by being pressed against the step portion 23 between 21 and 22. In this case, the outputs of the free piston 50 of the stopper from the output of the piston 30 so that the larger (i.e., so that the B1-B2> d1-d2) , the inner diameter B1 and small in the large diameter portion 21 of the cylinder 20 the inner diameter B2 of the inner diameter portion 22, an outer diameter d1 and since the dimensions of the outer diameter d2 of the projecting portion 24 of the cylinder 20 are selected respectively, the output piston 30 where the two pistons 30 and 50 to each other strikes the piston rod 32 is Stop. In this way, the actuator 10 can be held in the step 1 down position.
[0048]
(Step 2 down mode)
When both the # 1 and # 2 solenoids 61a and 61b of the three-position switching valve 60 are turned on, the high pressure port 60a and the fluid chamber b, and the low pressure port 60b and the fluid chamber a are connected. Immediately after this, the binding force of the free piston 50 in the fluid chamber a connected to the low pressure port 60b is lost, and the high pressure working fluid flows into the fluid chamber b and presses the output piston 30. Expands.
[0049]
At this time, when the piston 30 is operated instantaneously, there is a limit to supply / discharge of the working fluid. Therefore, the supply side of the high pressure compensates for the shortage of the working fluid by simultaneously pushing out the working fluid accumulated in the accumulator 90 by the charge valve 91 and the pressure transducer 92.
[0050]
On the low pressure side, a large flow rate of working fluid that is instantaneously discharged is temporarily accumulated in the accumulator 95 and gradually discharged after the operation of the output piston 30 is completed. In this way, the actuator 10 that can handle an instantaneous large flow rate is established.
[0051]
(Up mode)
From any position of the step 1 and 2 described above, it is possible to switch the # 1 solenoid 61a of the three-position switching valve 60 OFF, the piston in the housing mode by switching the # 2 solenoid 61b to ON / OFF, thereby The high pressure port 60a of the three-position switching valve 60 is connected to the fluid chamber a of the actuator 10 and the low pressure port 60b is connected to the fluid chamber b, and the area difference between the inner diameter B2 of the small diameter portion 22 of the cylinder 20 and the outer diameter d1 of the piston rod 32. The determined contraction force of the piston acts on the piston, and the piston rod 32 contracts.
[0052]
[Another example]
In the embodiment shown in FIG. 1 described above, the accumulator 90 for supplying a large amount of pressurized fluid is provided outside the actuator 10. However, in the embodiment shown in FIG. 2, the protruding portion 24 of the cylinder 20 and the piston rod 32 are provided. An air gap is provided between them, and an accumulator similar to the accumulator 90 shown in FIG. 1 is formed there.
[0053]
That is, in FIG. 2, the protruding portion 24 protruding from the right end surface of the cylinder 20 has a cylindrical shape, and the piston rod 32 slides outside the cylindrical protruding portion 24 in the same manner as in the above-described embodiment. The seal fits movably.
[0054]
A piston 93 that divides the gas chamber and the hydraulic chamber of the accumulator 90 is fitted into the cylindrical projecting portion 24 so as to be slidable through an O-ring 46 in a sealed state. The projecting portion 24 is a concentric double cylinder, and a gas pressure supply path 94 extending in the longitudinal direction is formed between the two cylinders.
[0055]
The left chamber of the accumulator 90 piston 93 is a gas chamber g. The gas chamber g is connected to a charge valve 91 and a pressure transducer 92 via a gas pressure supply path 94 from a port 24 b near the left end of the protrusion 24 of the cylinder 20.
[0056]
The right side of the piston 93 is a working fluid chamber p. The working fluid chamber p is connected to the supply line 80 through a port 24 a and a line 87 formed on the wall surface of the cylindrical upper protrusion 24 of the cylinder 20.
[0057]
When the actuator 10 is rapidly operated as in the above-described embodiment, the working fluid stored in the working fluid chamber p in the accumulator 90 is supplied to the working fluid chamber b of the actuator 10 and the piston rod 32 of the actuator 10 is moved. Rapid movement is possible.
[0058]
Further, reference numerals 6a and 6b in FIG. 2 are switches composed of, for example, limit switches for piston position confirmation.
[0059]
Since the other structure of this embodiment is the same as that of the embodiment of FIG. 1 described above, the same parts are denoted by the same reference numerals, and description thereof will be omitted.
[0061]
【The invention's effect】
As is clear from the above description, the present invention has the following effects.
(1) Multi-stage control of the actuator has become possible.
(2) The operating speed / output of the actuator can be set for each control stage.
(3) The working fluid can be suppressed instantaneously, and the weight of the airframe and the actuator can be reduced and the cost can be reduced.
(4) It is possible to prevent malfunction due to its own weight when the hydraulic pressure supply is stopped.
[0062]
Furthermore, the present invention according to claim 2 also provides the following effects.
(5) The reliability by protection of the accumulator is improved, and the ballistic resistance is improved.
[Brief description of the drawings]
FIG. 1 is a sectional view schematically showing an embodiment of the present invention.
FIG. 2 is a cross-sectional view showing another specific embodiment of the present invention.
FIG. 3 is an operation explanatory diagram of a missile launcher using the actuator 10 according to the present invention.
4 is a diagram showing the operation of the missile launcher shown in FIG. 3. FIG.
[Explanation of symbols]
1 body 2 launcher platform 3 missile 10 actuator 20 cylinder 21 larger in diameter 22 small in diameter 23 stage 24 protrusion 30 piston 30a recess 31 piston body 32 the piston rod 50 free piston 51 large outer diameter portion 52 small outer diameter portion 53 Step part 60 Three-position switching valve 60a Outlet port 60b Outlet port 60c Input side port 60d Discharge side port 61a # 1 solenoid 61b # 2 solenoid 70 Check valve 71 Pipe line 72 Pipe line 75 Thermal relief valve 80 Supply line 85 Drain line 86 Discharge path 90 Accumulator 91 Charge valve 92 Pressure transducer

Claims (1)

A cylinder 20 and a piston 30 housed in the cylinder 20 so as to be movable in the longitudinal direction thereof are formed , and fluid chambers a and b are formed on both sides of the piston 30. The cylinder 20 has a large inner diameter portion 21 and a small inner diameter portion. protrusion 24 extending in the longitudinal direction of the cylinder 20 with 22 and are connected longitudinally protrudes from the end surface of the small inner diameter portion side in the internal cylinder 20, the piston 30 is small-inner-diameter portion of the cylinder 20 has a recess 30a extending in the longitudinal direction from the end face positioned on the small-inner-diameter side of the cylinder with a piston body 31 and the piston rod 32 projecting from the piston body 31 slidably sealed fit to, the recesses 30a are fitted slidably sealed to the projecting portion 24, the small diameter portion 21 and the piston body 31 of the cylinder 20 Ri said fluid chamber b is formed, the free piston 50 having a large and small outer diameter portion is fitted slidably sealed to the cylinder 20 in the longitudinal direction at a connection portion extending magnitude inside diameter portion of the cylinder 20, a large of the cylinder The fluid chamber a is formed by the inner diameter portion 21 and the piston rod 32 ,
The fluid chambers a and b communicate with the high-pressure port 60a and the low-pressure port 60b of the three-position switching valve 60, respectively. The input-side port 60c of the three-position switching valve 60 communicates with a supply line 80 that supplies high-pressure fluid. The discharge side port 60d communicates with a discharge pipe 85 for returning the return fluid ,
The three-position switching valve 60 is
The high pressure port 60a is connected to the fluid chamber a and the low pressure port 60b is connected to the fluid chamber b. The contraction force of the piston 30 determined by the area difference between the inner diameter of the small inner diameter portion 22 of the cylinder 20 and the outer diameter of the piston rod 32 is determined by the piston 30. A storage mode in which the piston rod 32 contracts ,
Step 1 in which the high pressure port 60a and the fluid chambers a and b are connected, and the force due to the difference in pressure receiving area facing the fluid chambers a and b of the piston body 31 acts on the piston body 31 and the piston 30 starts to move in the extending direction. mode, and
The high pressure port 60a is connected to the fluid chamber b, the low pressure port 60b and the fluid chamber a are connected, the binding force of the free piston 50 in the fluid chamber a connected to the low pressure port 60b is lost, and the high pressure working fluid flows into the fluid chamber b. Step 2 mode in which the output piston 30 extends ,
The actuator characterized by taking .

Images