Compound actuator

Abstract

To provide a compound actuator capable of achieving a large stroke and high power while avoiding an increase in the size of a product and a cost increase.SOLUTION: A typical constitution of a compound actuator according to the present invention is a compound actuator 100 that comprises a plurality of actuators for moving and holding an object component. The compound actuator comprises a three-way valve 110, a spool valve 130 that operates by the three-way valve, a piston 150 that operates by pressure oil output from the spool valve, and a holding actuator 170 for holding the piston in a position to which the piston is moved.SELECTED DRAWING: Figure 1

Description

[Technical Field]

[0001] The present invention relates to a compound actuator having multiple actuators for moving and holding a workpiece. [Background technology]

[0002] Vehicles are equipped with clutch actuators that operate, for example, clutches. As an example, Patent Document 1 discloses a "drive assembly for use in a power transmission system of an automobile." The drive assembly in Patent Document 1 includes "a rotatable housing, an output section, first and second clutch sections disposed in a power path between the housing and the output section, a controllable actuator that actuates the clutches so as to selectively connect the first and second clutch sections to each other to transmit torque, a target element that is axially movable when the clutch is actuated, and a sensor that cooperates with the target element to determine the clutch position of at least one of the clutches."

[0003] The drive assembly of Patent Document 1 is for engaging and disengaging a vehicle clutch. In Patent Document 1, when the electromagnet is energized, magnetic flux is generated in the housing and anchor element, causing the anchor element and sleeve to move together in a direction that causes the protrusion to protrude (clutch engagement). When the electromagnet is de-energized, a return force from the sliding disk causes the anchor element and sleeve to move together in a direction that moves away from the protrusion (clutch disengagement). [Prior art documents] [Patent documents]

[0004] [Patent Document 1] Patent No. 6525553 Summary of the Invention [Problem to be solved by the invention]

[0005] In order to increase the stroke or output of a drive assembly such as that described in Patent Document 1, it is necessary to increase the number of turns of the coil or the attraction area of ​​the electromagnet, which may result in an increase in the size of the product, which may deviate from the standard size or increase costs.

[0006] In view of the above problems, the present invention has an object to provide a composite actuator that can achieve a large stroke and a large output while avoiding an increase in size and cost of the product. [Means for solving the problem]

[0007] In order to solve the above problems, a representative configuration of a composite actuator according to the present invention is a composite actuator including a plurality of actuators that move and hold target components, and the composite actuator includes a three-way valve, a spool valve that operates by the three-way valve, a piston that operates by pressure oil output from the spool valve, and a holding actuator that holds the piston at the position to which it has moved.

[0008] The holding actuator may be an electromagnetic solenoid, or a solenoid with a built-in magnet that holds the actuator by magnetic force.

[0009] The piston may be a multi-stage piston having a plurality of piston chambers arranged in the protruding direction of the piston.

[0010] The piston may include a first piston arranged on the retraction side of the piston, a second piston arranged on the protrusion side of the piston than the first piston, and a communication passage for guiding pressurized oil output from the spool valve, and the communication passage may be configured to guide pressurized oil to both a first piston chamber of the first piston and a second piston chamber of the second piston.

[0011] The piston is fitted with a pin that extends to the position of the holding actuator and moves with the piston. The holding actuator is a solenoid with a built-in magnet that is positioned perpendicular to the direction of movement of the piston and holds the piston in two positions by magnetic force. The holding actuator engages with the pin at the position where the piston moves in the protruding direction, and the engagement with the pin is maintained in a non-energized state, thereby maintaining the protruding state of the piston. [Effects of the Invention]

[0012] According to the present invention, it is possible to provide a composite actuator that can achieve a large stroke and a large output while avoiding an increase in size and cost of the product. [Brief explanation of the drawings]

[0013] [Figure 1] 1 is an overall view of a compound actuator according to a first embodiment. [Figure 2] FIG. 2 is a rear view of the compound actuator. [Figure 3] 1A and 1B are diagrams illustrating a composite actuator before and during operation. [Figure 4] 10A and 10B are diagrams illustrating holding and retraction of the composite actuator. [Figure 5] 10A and 10B are diagrams illustrating a composite actuator according to a second embodiment. [Figure 6] 10A and 10B are diagrams illustrating retraction and protrusion operations. [Figure 7] 10A and 10B are diagrams illustrating the energization and retraction operations. [Figure 8] 10A and 10B are diagrams illustrating a composite actuator according to a third embodiment. [Figure 9] 9A and 9B are diagrams illustrating the compound actuator of FIG. 8 before and during operation. [Figure 10] 9A and 9B are diagrams illustrating the holding and retraction of the composite actuator of FIG. 8. [Figure 11] 10A and 10B are diagrams illustrating a composite actuator according to a fourth embodiment. DETAILED DESCRIPTION OF THE INVENTION

[0014] Preferred embodiments of the present invention will be described in detail below with reference to the accompanying drawings. Dimensions, materials, and other specific values ​​shown in the embodiments are merely examples for facilitating understanding of the invention and, unless otherwise specified, do not limit the present invention. In this specification and drawings, elements having substantially the same functions and configurations are designated by the same reference numerals to avoid redundant explanation, and elements not directly related to the present invention are not shown.

[0015] 1A and 1B are overall views of a composite actuator 100 according to a first embodiment. FIG. 1A is an overall perspective view of the composite actuator 100. FIG. 1B is a plan view of the composite actuator 100.

[0016] Figure 2 is a rear view of the compound actuator 100. Figure 2(a) is an external view of the rear of the compound actuator 100. Figure 2(b) is a view of the internal structure of the compound actuator 100 as seen from the rear side.

[0017] As shown in Figures 1(a) and 1(b), the composite actuator 100 includes a three-way valve 110, a spool valve 130, a piston 150, and a holding actuator 170 as multiple actuators (see Figure 2(b)). As shown in Figure 2(b), the spool valve 130 and the piston 150 are built into a block 192 and a cover 190. The three-way valve 110 and the holding actuator 170, which are electrical components, are attached to the block 192 afterwards. However, it is possible to select which elements to integrate and which to separate as appropriate.

[0018] As shown in Figure 2(b), the three-way valve 110 has a coil 114 and a plunger 116 arranged inside a casing 112. The plunger 116 is biased in the protruding direction by a spring 118, and is retracted when current is applied to the coil 114. A valve element 120 attached to the tip of the plunger 116 pushes a hard ball 122 to close a valve seat 121 (normally closed).

[0019] 2(a), an IN port 202 and an output port 204 of the three-way valve 110 are formed in the block 192. The output port 204 of the three-way valve 110 is connected to a pilot port 210 of the spool valve .

[0020] The spool valve 130 is a valve that operates according to the output (pilot pressure) of the three-way valve 110. The spool valve 130 includes a spool 132 and a first spring 134 (a return spring for the spool 132) attached to an end of the spool 132.

[0021] 2(a), the block 192 is formed with an IN port 212 of the spool valve 130, an A port 214 of the spool valve 130, a B port 216 connected to the back pressure port 154 of the piston 150, and a drain port 218. The IN port 212 of the spool valve 130 shares a hydraulic pressure source with the IN port 202 of the three-way valve 110. The output from the A port 214 is not used in this embodiment. The drain port 218 discharges hydraulic oil leaking near the first spring 134.

[0022] The piston 150 operates when pressure oil output from the spool valve 130 is supplied to a back pressure chamber 152. A front shaft 156 for pushing a mating part is provided at the tip of the piston 150. A second spring 158 (piston return spring) is arranged around the front shaft 156.

[0023] The holding actuator 170 holds the piston 150 at the position to which the piston 150 has moved (protruded). In the first embodiment, the holding actuator 170 is an electromagnetic solenoid, and has a coil 172 and a plunger 174 disposed therein. The plunger 174 abuts against a shaft 175, and the shaft 175 abuts against the rear shaft 157 of the piston 150. The plunger 174 is biased in the protruding direction by a spring 176. Then, by passing current through the coil 172, a holding force is applied when the piston 150 is protruded.

[0024] Next, a description will be given of the operation of the compound actuator 100. Figure 3 is a diagram for explaining the compound actuator 100 before and during operation, with Figure 3(a) showing the state before operation and Figure 3(b) showing the state during operation.

[0025] 3(a), the coil 114 of the three-way valve 110 is not energized. At this time, no hydraulic oil is output from the three-way valve 110, and the spool valve 130 does not operate. The IN port 212 of the spool valve 130 is connected to the A port 214, and the hydraulic oil is simply discharged.

[0026] As shown in Figure 3(b), when the coil 114 is energized, the plunger 116 moves and the valve element 120 opens. Then, hydraulic oil input from the IN port 202 of the three-way valve 110 is output from the output port 204 and flows to the pilot port 210 of the spool valve 130. Then, the spool 132 is pushed by the hydraulic oil and moves, connecting the IN port 212 and the B port 216. The hydraulic oil input from the IN port 212 flows into the back pressure chamber 152 through the back pressure port 154 of the piston 150, moving the piston 150. This causes the front shaft 156 to protrude, moving a mating part W (e.g., a clutch).

[0027] With the above configuration, the piston 150 operates as a so-called hydraulic cylinder. Because the stroke of the piston 150 depends on the volume of hydraulic oil flowing into the back pressure chamber 152, it is easy to achieve a large stroke. Furthermore, because the output of the piston 150 depends on the pressure of the hydraulic source, it is easy to achieve a large output. Therefore, according to the present invention, it is possible to provide a composite actuator that can achieve a large stroke and a large output while avoiding an increase in the size and cost of the product.

[0028] 4A and 4B are diagrams for explaining the holding and retraction of the composite actuator 100, with FIG. 4A showing the holding operation and FIG. 4B showing the retraction operation.

[0029] When the piston 150 is in the protruding state, the plunger 174 of the holding actuator 170 is pushed by the spring 176 and moves (see FIG. 3(b)). That is, the plunger 174 moves following the piston 150, and the shaft 175 of the holding actuator 170 abuts against the rear shaft 157 of the piston 150.

[0030] 4(a), the coil 172 of the holding actuator 170 is energized to apply an attractive force to the plunger 174 (which has already moved, so no further movement occurs). In this way, the holding actuator 170 restricts the return of the piston 150 (movement to the right in the figure).

[0031] In this way, the holding actuator 170 is able to achieve a large stroke by combining the spring 176, which is responsible for the initial movement, with the coil 172. This makes it possible for the holding actuator 170 to hold the piston 150 even when the piston 150 has a large stroke.

[0032] After energizing the coil 172 of the holding actuator 170, the coil 114 of the three-way valve 110 is de-energized. This causes the position of the spool 132 to return to the right in the figure, and the pressure in the back pressure chamber 152 of the piston 150 is released through the drain port 218 of the spool valve 130. In other words, the piston 150 is not held by hydraulic pressure, but is held solely by the biasing force of the holding actuator 170.

[0033] 4(b), the supply of electricity to the coil 172 of the holding actuator 170 is stopped. Then, the piston 150 returns to its initial position (to the right in the figure) due to the biasing force of the second spring 158 and the reaction force from the mating part W. Note that, in order for the piston 150 to be retracted, the second spring 158 and the spring 176 are selected so that the force of the second spring 158 plus the reaction force of the mating part W is greater than the force of the spring 176. The hydraulic oil that had been filled in the back pressure chamber 152 is discharged from the drain port 218 of the spool valve 130. Pushed by the piston 150, the plunger 174 of the holding actuator 170 also returns to its initial position.

[0034] Next, a second embodiment of the composite actuator according to the present invention will be described. Fig. 5 is a diagram illustrating a composite actuator 100A according to the second embodiment. The holding actuator 170 of the composite actuator 100 shown in Fig. 1 is an electromagnetic solenoid. Instead, the composite actuator 100A shown in Fig. 5 is equipped with a magnet-incorporated solenoid 180 that incorporates a magnet and uses magnetic force to hold the actuator.

[0035] FIG. 5(a) is an overall configuration diagram of the composite actuator 100A, and FIG. 5(b) is a configuration diagram of a magnet-equipped solenoid 180. The magnet-equipped solenoid 180 holds the piston 150 in a position to which the piston 150 has moved (protruded). The magnet-equipped solenoid 180 includes a coil 182 and a plunger 184 in a solenoid body 181. A shaft 185 formed integrally with the plunger 184 abuts against the rear shaft 157 of the piston 150. The plunger 184 is urged in the protruding direction by a spring 183. When the plunger 184 is attracted to the magnet 187, the holding force of the magnet 187 is released (cancelled) by passing current through the coil 182.

[0036] A disk-shaped stopper 186 that restricts the movement limit of the plunger 184 in the protruding direction is disposed inside the solenoid body 181. An annular magnet 187 is disposed between the stopper 186 and the solenoid body 181. A magnetic gap 186a (gap) is formed between the side edge of the stopper 186 and the solenoid body 181 to make it difficult for magnetic flux to pass through.

[0037] FIG. 6 is a diagram for explaining the retracting and protruding operations, and FIG. 7 is a diagram for explaining the energizing and retracting operations.

[0038] 6(a) shows the plunger 184 when it is retracted (initial state). The plunger 184 is pushed by the piston 150 and is in a retracted position (on the right side in the figure). At this time, the magnetic flux leaving the magnet 187 forms a magnetic path M1 that passes through the stopper 186, the magnetic gap 186a, the solenoid body 181, and returns to the magnet 187.

[0039] Figure 6(b) shows the protruding operation. When the piston 150 moves (see Figure 3(b)), the shaft 185 of the magnet-embedded solenoid 180 loses support from the rear shaft 157 of the piston 150. As a result, the plunger 184 moves in the protruding direction (to the left in the figure) due to the biasing force of the spring 183.

[0040] When plunger 184 abuts against stopper 186, magnetic flux does not easily pass through magnetic gap 186a, so magnetic flux flows from stopper 186 to plunger 184. As a result, the magnetic flux leaving magnet 187 flows from stopper 186 to plunger 184, and switches to magnetic path M2, which passes through the bobbin of coil 182 and solenoid body 181 and returns to magnet 187 (magnetic path switching). Because magnetic path M2 passes through the boundary between stopper 186 and plunger 184, an attractive force is generated between them. This attractive force and the biasing force of spring 183 maintain piston 150 in the protruding state. Therefore, it can be maintained stably without requiring power.

[0041] Figure 7(a) shows the state when current is applied for retraction. A current is passed through coil 182 so as to generate a magnetic flux in the opposite direction to the magnetic flux of magnet 187. When magnetic path M3 is formed around coil 182, it becomes difficult for the magnetic flux of magnet 187 to pass around the coil, so it begins to flow across magnetic gap 186a again, switching to magnetic path M1. Then, there is no longer any magnetic flux flowing through the boundary between stopper 186 and plunger 184, and plunger 184 loses its attractive force.

[0042] Figure 7(b) shows the state after the retraction movement. When the plunger 184 loses its attractive force, the piston 150 returns to its initial position (to the right in the figure) due to the biasing force of the second spring 158 and the reaction force from the mating part W (see Figure 4(b)). The hydraulic oil that had been filling the back pressure chamber 152 is discharged from the drain port 218 of the spool valve 130. Pushed by the piston 150, the plunger 184 of the magnet-embedded solenoid 180 also returns to its initial position.

[0043] Next, a third embodiment of the compound actuator according to the present invention will be described. Fig. 8 is a diagram illustrating a compound actuator 100B according to the third embodiment. The compound actuator 100B includes a multi-stage piston 220 instead of the piston 150 of the compound actuator 100 shown in Fig. 1.

[0044] Fig. 8(a) is an overall configuration diagram of the composite actuator 100B. Fig. 8(b) is a configuration diagram of the multi-stage piston 220, showing the state in which the multi-stage piston 220 is operating. The multi-stage piston 220 operates when pressure oil output from the spool valve 130 is supplied to the back pressure chamber 152.

[0045] 8(b), the multi-stage piston 220 includes a first piston 222, a second piston 224, a stopper 226, and a communication passage 228. The first piston 222 and the second piston 224 are arranged in the protruding direction of the multi-stage piston 220. The first piston 222 is disposed on the retraction side (right side in the figure) of the multi-stage piston 220, and has a first piston chamber 230. The second piston 224 is disposed on the protruding side (left side in the figure) of the multi-stage piston 220 relative to the first piston 222, and has a second piston chamber 232.

[0046] Furthermore, a protruding end face 234 of the first piston 222 is seated on a retracting end face 236 of the second piston 224. This allows the hydraulic force of the first piston 222 to be transmitted to the second piston 224. Furthermore, a front shaft 156 for pushing a mating part W (see Figures 9 and 10) is provided on a protruding end face 237 of the second piston 224. A second spring 158 (piston return spring) is arranged around the front shaft 156.

[0047] The stopper 226 is disposed between the first piston 222 and the second piston 224, and is engaged with the block 192. Therefore, the stopper 226 does not move relative to the block 192. The stopper 226 also has a large diameter portion 238 and a small diameter portion 240.

[0048] The large diameter portion 238 of the stopper 226 is housed in the second piston 224 and defines a second piston chamber 232 together with the second piston 224. The small diameter portion 240 of the stopper 226 passes through the first piston 222 and defines a first piston chamber 230 together with the first piston 222 and the block 192.

[0049] Furthermore, the multi-stage piston 220 defines a space 242 by the stopper 226, the end face 234 on the protruding side of the first piston 222, and the second piston 224. This space 242 prevents the hydraulic force of the first piston 222 from being canceled out. The space 242 is also sealed with, for example, a packing, so that oil does not leak from the first piston chamber 230 and the second piston chamber 232. Therefore, the space 242 is not subjected to hydraulic pressure.

[0050] 8(b) are formed in the multi-stage piston 220 so as not to seal the space 242. The breathing passage 244 is formed in a part of the retraction-side end face 236 of the second piston 224 and communicates with the space 242. The breathing passage 246 is formed in the outer periphery 250 of the second piston 224 and communicates with the breathing passage 244. The breathing passage 248 is formed in a plug 252 against which the second spring 158 abuts, and communicates with the breathing passage 246 via a spring chamber 254 and further with the outside. In this way, in the multi-stage piston 220, the breathing passages 244, 246, 248 allow the space 242 to be lowered to atmospheric pressure without being sealed, allowing the first piston 222 to stroke.

[0051] The communicating passage 228 is a passage that guides pressure oil output from the spool valve 130 to the multi-stage piston 220, and has a central hole 228a and a lateral hole 228b. The central hole 228a penetrates the large diameter portion 238 and the small diameter portion 240 of the stopper 226 and extends in the protruding direction of the multi-stage piston 220. The shaft 175 of the holding actuator 170 is also passed through the central hole 228a. The lateral hole 228b penetrates from the side surface of the small diameter portion 240 to the central hole 228a, and communicates with the back pressure chamber 152 of the multi-stage piston 220.

[0052] In the multi-stage piston 220, pressure oil output from the spool valve 130 is supplied to the back pressure chamber 152 through the back pressure port 154 of the multi-stage piston 220, as shown by the arrows in Figure 8(b). Therefore, the pressure oil is received by a first pressure receiving surface 256 of the first piston 222 that faces the first piston chamber 230. The pressure oil further passes from the back pressure chamber 152 through the lateral hole 228b and central hole 228a of the communicating passage 228, and is received by a second pressure receiving surface 258 of the second piston 224 that faces the second piston chamber 232. As a result, the first piston 222 and the second piston 224 can each receive the pressure oil and move in the protruding direction.

[0053] Next, the operation of the compound actuator 100B will be described. Figure 9 is a diagram for explaining the compound actuator 100B of Figure 8 before and during operation, with Figure 9(a) showing the state before operation and Figure 9(b) showing the state during operation.

[0054] In the pre-operation state shown in Figure 9(a), the coil 114 (see Figure 3(a)) of the three-way valve 110 is not energized. At this time, no hydraulic oil is output from the three-way valve 110, and the spool valve 130 does not operate. The IN port 212 of the spool valve 130 is connected to the A port 214, and the hydraulic oil is simply discharged.

[0055] As shown in Figure 9(b), when the coil 114 is energized, the plunger 116 moves and the valve element 120 opens (see Figure 3(b)). Then, the hydraulic oil input from the IN port 202 of the three-way valve 110 is output from the output port 204 and flows to the pilot port 210 of the spool valve 130. Then, the spool 132 is pushed by the hydraulic oil and moves, connecting the IN port 212 and the B port 216. The hydraulic oil input from the IN port 212 flows into the back pressure chamber 152 through the back pressure port 154 of the multi-stage piston 220.

[0056] As described above, the first piston 222 and the second piston 224 receive pressure oil at the first pressure-receiving surface 256 and the second pressure-receiving surface 258, respectively, and move in the protruding direction. At this time, the protruding-side end surface 234 of the first piston 222 moves in the protruding direction, thereby reducing the unsealed space 242 and coming into contact with the large diameter portion 238 of the stopper 226, as shown in FIG. 8(b). Note that air in the space 242 is exhausted to the outside through the breathing paths 244, 246, and 248. As a result, the front shaft 156 of the composite actuator 100B protrudes, and the mating part W can be moved.

[0057] In this way, the multi-stage piston 220 operates as a so-called hydraulic cylinder. The multi-stage piston 220 also has a plurality of (here, two) first pistons 222 and second pistons 224 arranged in the protruding direction. Therefore, the multi-stage piston 220 can increase the pressure-receiving area (the total area of ​​the first pressure-receiving surface 256 and the second pressure-receiving surface 258) that receives the pressure oil output from the spool valve 130 without increasing the piston diameter. Therefore, the composite actuator 100B can increase the protruding force for moving the mating part W without increasing the size of the piston.

[0058] 10A and 10B are diagrams for explaining the holding and retraction of the composite actuator 100B of FIG. 8, with FIG. 10A showing the holding operation and FIG. 10B showing the retraction operation.

[0059] When the multi-stage piston 220 is in the protruding state, the plunger 174 of the holding actuator 170 is pushed by the spring 176 and moves (see FIG. 3(b)). That is, the plunger 174 moves following the multi-stage piston 220, and the shaft 175 of the holding actuator 170 abuts against the second pressure-receiving surface 258 of the second piston 224 of the multi-stage piston 220.

[0060] 10(a), the coil 172 (see FIG. 4(a)) of the holding actuator 170 is energized to apply an attractive force to the plunger 174 (which has already moved, so no further movement occurs). In this way, the holding actuator 170 restricts the return of the multi-stage piston 220 (movement to the right in the drawing).

[0061] Furthermore, after energizing the coil 172 of the holding actuator 170, energization of the coil 114 of the three-way valve 110 (see FIG. 4(a)) is stopped. This causes the position of the spool 132 to return to the right in the figure, and the pressure in the back pressure chamber 152 of the multi-stage piston 220 passes through the back pressure port 154 and is released from the drain port 218 of the spool valve 130. In other words, the multi-stage piston 220 is not held by hydraulic pressure, but is held solely by the biasing force of the holding actuator 170.

[0062] During the retraction operation shown in FIG. 10(b), the supply of current to the coil 172 (see FIG. 4(b)) of the holding actuator 170 is stopped. Then, the multi-stage piston 220 returns to its initial position (right side in the figure) due to the biasing force of the second spring 158 and the reaction force from the mating part W. Note that, in order for the multi-stage piston 220 to be retracted, the second spring 158 and the spring 176 are selected so that the force of the second spring 158 + the reaction force of the mating part W > the force of the spring 176. Then, pushed by the multi-stage piston 220, the plunger 174 of the holding actuator 170 also returns to its initial position as shown in FIG. 4(b).

[0063] Next, a fourth embodiment of the compound actuator according to the present invention will be described. Fig. 11 is a diagram illustrating a compound actuator 100C according to the fourth embodiment. Fig. 11(a) shows the compound actuator 100C before operation, and Fig. 11(b) shows it during operation.

[0064] The composite actuator 100C includes a multi-stage piston 220A and a magnet-embedded solenoid 260 arranged perpendicular to the piston 150 and the electromagnetic solenoid holding actuator 170 of the composite actuator 100 shown in FIG.

[0065] As shown in the figure, the magnet-equipped solenoid 260 is disposed in a direction perpendicular to the direction of movement of the multi-stage piston 220A, and has a built-in magnet that holds it in two positions by magnetic force. A plate 264 is attached to a shaft 262 of the magnet-equipped solenoid 260. Therefore, the plate 264 is integrated with the shaft 262. The plate 264 is slidably disposed in a plate sliding hole 266 formed in the block 192.

[0066] A pin 268 is attached to second piston 224A of multi-stage piston 220A. Pin 268 is attached to the center of second pressure-receiving surface 258A of second piston 224A and passes through a central hole 270a of stopper 226A. Note that stopper 226A is formed with a communication passage 270 having central hole 270a and a lateral hole 270b. Furthermore, a retraction-side end 272 of pin 268 is slidably disposed in a pin slide hole 274 formed in block 192.

[0067] 11(a) shows that the multi-stage piston 220A has not moved in the protruding direction. At this time, the retracted end 272 of the pin 268 is located further toward the retracted side than the position of the plate 264 of the magnet-embedded solenoid 260, and is in slidable contact with the plate 264. The pin 268 extends to the position of the magnet-embedded solenoid 260 and moves together with the multi-stage piston 220A.

[0068] The second piston 224A is integrated with the front shaft 156, around which a second spring 158 (piston return spring) is arranged. The stopper 226A is arranged between the first piston 222A and the second piston 224A, and is further engaged with the block 192. Therefore, the stopper 226A does not move relative to the block 192.

[0069] When the coil 114 (see FIG. 3(b)) of the three-way valve 110 is energized, the hydraulic oil input from the IN port 212 of the spool valve 130 flows into the back pressure chamber 152 through the back pressure port 154 of the multi-stage piston 220A as described above.

[0070] Therefore, the pressure oil is received by the first pressure-receiving surface 256A of the first piston 222A shown in Figure 11(b). Furthermore, the pressure oil passes from the back pressure chamber 152 through the lateral hole 270b and the central hole 270a of the communication passage 270 and is received by the second pressure-receiving surface 258A of the second piston 224A. As a result, the first piston 222A and the second piston 224A can each receive the pressure oil and move in the protruding direction. Then, the second piston 224A, which is integrated with the front shaft 156, protrudes, moving the mating part W (see Figure 10).

[0071] In the composite actuator 100C, when the multi-stage piston 220A moves in the protruding direction, the pin 268 also moves in the protruding direction as shown in Figure 11(b). As a result, the retracted end 272 of the pin 268 is positioned further protruding than the position of the plate 264 of the magnet-equipped solenoid 260.

[0072] At this time, by energizing the coil (not shown) of the magnet-equipped solenoid 260 and protruding the shaft 262, the plate 264 is inserted into the retracted end 272 of the pin 268 and engages with the pin 268, thereby maintaining the protruding state of the multi-stage piston 220A.

[0073] Furthermore, in the composite actuator 100C, the magnet-embedded solenoid 260 maintains the engagement between the plate 264 and the pin 268 in a non-energized state, so there is no need to continuously energize the multi-stage piston 220A to maintain its protruding state, thereby reducing power consumption.

[0074] In the composite actuator 100C, after the protruding state of the multi-stage piston 220A is maintained, the coil of the magnet-equipped solenoid 260 is energized to retract the shaft 262, thereby retracting the plate 264 integrated with the shaft 262, thereby disengaging the plate 264 from the pin 268.

[0075] While the preferred embodiments of the present invention have been described above with reference to the accompanying drawings, it goes without saying that the present invention is not limited to such examples. It is clear that those skilled in the art can conceive of various modifications and alterations within the scope of the claims, and it is understood that such modifications and alterations also fall within the technical scope of the present invention. [Industrial Applicability]

[0076] The present invention can be used as a composite actuator that can achieve a large stroke and a large output. [Explanation of symbols]

[0077] M1...magnetic path, 100...composite actuator, 100A...composite actuator, 110...three-way valve, 112...casing, 114...coil, 116...plunger, 118...spring, 120...valve body, 121...valve seat, 122...hard ball, 130...spool valve, 132...spool, 134...first spring, 150...piston, 152...back pressure chamber, 154...back pressure port, 156...front shaft, 157...rear shaft, 158...second spring, 170...holding actuator, 172...coil, 174...plunger, 175 ...shaft, 176...spring, 180...magnet built-in solenoid, 181...solenoid body, 182...coil, 183...spring, 184...plunger, 185...shaft, 186...stopper, 186a...magnetic gap, 187...magnet, 190...cover, 192...block, 202...IN port, 204...output port, 206...IN port, 208...OUT port, 210...pilot port, 212...IN port, 214...A port, 216...B port, 218...drain port, 100B...composite actuator actuator, 220... multi-stage piston, 222... first piston, 224... second piston, 226... stopper, 228... communication passage, 228a... central hole, 228b... horizontal hole, 230... first piston chamber, 232... second piston chamber, 234... end face of the protruding side of the first piston, 236... end face of the retracting side of the second piston, 237... end face of the protruding side of the second piston, 238... large diameter portion of the stopper, 240... small diameter portion of the stopper, 242... space, 244, 246, 248... breathing passage, 250... outer periphery of the second piston, 252... plug , 254...spring chamber, 256...first pressure receiving surface, 258...second pressure receiving surface, 100C...compound actuator, 220A...multi-stage piston, 222A...first piston, 224A...second piston, 226A...stopper, 256A...first pressure receiving surface, 258A...second pressure receiving surface, 260...magnet-integrated solenoid, 262...shaft of magnet-integrated solenoid, 264...plate, 266...plate sliding hole, 268...pin, 270...communicating passage, 270a...center hole, 270b...side hole, 272...retraction side end of pin, 274...pin sliding hole

Claims

1. A composite actuator having a plurality of actuators for moving and holding a target part, The composite actuator comprises: A three-way valve, a spool valve operated by the three-way valve; a piston operated by pressure oil output from the spool valve; a holding actuator for holding the piston at the position to which the piston has moved; A composite actuator comprising:

2. 2. The composite actuator according to claim 1, wherein the holding actuator is an electromagnetic solenoid.

3. 2. The compound actuator according to claim 1, wherein the holding actuator is a solenoid with a built-in magnet that holds the actuator by magnetic force.

4. 2. The composite actuator according to claim 1, wherein the piston is a multi-stage piston having a plurality of piston chambers arranged in a protruding direction of the piston.

5. The piston is a first piston disposed on the retraction side of the piston; a second piston disposed on a protruding side of the piston relative to the first piston; a communication passage for guiding pressure oil output from the spool valve, 5. The compound actuator according to claim 4, wherein the communication passage guides the pressure oil to both a first piston chamber of the first piston and a second piston chamber of the second piston.

6. The piston is provided with a pin that extends to the position of the holding actuator and moves together with the piston, The holding actuator is The piston is disposed perpendicular to the direction of movement of the piston, It is a solenoid with a built-in magnet that holds two positions by magnetic force.

2. The composite actuator according to claim 1, wherein the piston engages with the pin at a position where the piston has moved in a protruding direction, and the engagement with the pin is maintained in a non-energized state, thereby maintaining the protruding state of the piston.

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