US20040056225A1 - Multi-piston valve actuator - Google Patents
Multi-piston valve actuator Download PDFInfo
- Publication number
- US20040056225A1 US20040056225A1 US10/246,961 US24696102A US2004056225A1 US 20040056225 A1 US20040056225 A1 US 20040056225A1 US 24696102 A US24696102 A US 24696102A US 2004056225 A1 US2004056225 A1 US 2004056225A1
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- United States
- Prior art keywords
- cylinder
- stationary
- wall
- movable cylinder
- inner chamber
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 239000012530 fluid Substances 0.000 claims abstract description 83
- 238000004891 communication Methods 0.000 claims abstract description 21
- 239000004033 plastic Substances 0.000 claims description 13
- 229920003023 plastic Polymers 0.000 claims description 13
- 238000007789 sealing Methods 0.000 description 14
- 230000002093 peripheral effect Effects 0.000 description 10
- 239000000463 material Substances 0.000 description 5
- 239000012778 molding material Substances 0.000 description 4
- 239000003570 air Substances 0.000 description 3
- 238000002347 injection Methods 0.000 description 3
- 239000007924 injection Substances 0.000 description 3
- 239000012080 ambient air Substances 0.000 description 2
- 230000003247 decreasing effect Effects 0.000 description 2
- 238000001746 injection moulding Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000002441 reversible effect Effects 0.000 description 2
- 238000010276 construction Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000013011 mating Effects 0.000 description 1
- 238000000465 moulding Methods 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
- F15B15/1423—Component parts; Constructional details
- F15B15/1447—Pistons; Piston to piston rod assemblies
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B29—WORKING OF PLASTICS; WORKING OF SUBSTANCES IN A PLASTIC STATE IN GENERAL
- B29C—SHAPING OR JOINING OF PLASTICS; SHAPING OF MATERIAL IN A PLASTIC STATE, NOT OTHERWISE PROVIDED FOR; AFTER-TREATMENT OF THE SHAPED PRODUCTS, e.g. REPAIRING
- B29C45/00—Injection moulding, i.e. forcing the required volume of moulding material through a nozzle into a closed mould; Apparatus therefor
- B29C45/17—Component parts, details or accessories; Auxiliary operations
- B29C45/26—Moulds
- B29C45/27—Sprue channels ; Runner channels or runner nozzles
- B29C45/28—Closure devices therefor
- B29C45/2806—Closure devices therefor consisting of needle valve systems
- B29C45/281—Drive means therefor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
- F15B11/036—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force by means of servomotors having a plurality of working chambers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
- F16K31/122—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston
- F16K31/1225—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston with a plurality of pistons
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B29—WORKING OF PLASTICS; WORKING OF SUBSTANCES IN A PLASTIC STATE IN GENERAL
- B29C—SHAPING OR JOINING OF PLASTICS; SHAPING OF MATERIAL IN A PLASTIC STATE, NOT OTHERWISE PROVIDED FOR; AFTER-TREATMENT OF THE SHAPED PRODUCTS, e.g. REPAIRING
- B29C45/00—Injection moulding, i.e. forcing the required volume of moulding material through a nozzle into a closed mould; Apparatus therefor
- B29C45/17—Component parts, details or accessories; Auxiliary operations
- B29C45/26—Moulds
- B29C45/27—Sprue channels ; Runner channels or runner nozzles
- B29C45/28—Closure devices therefor
- B29C45/2806—Closure devices therefor consisting of needle valve systems
- B29C45/281—Drive means therefor
- B29C2045/2813—Common drive means for several needle valves
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B29—WORKING OF PLASTICS; WORKING OF SUBSTANCES IN A PLASTIC STATE IN GENERAL
- B29C—SHAPING OR JOINING OF PLASTICS; SHAPING OF MATERIAL IN A PLASTIC STATE, NOT OTHERWISE PROVIDED FOR; AFTER-TREATMENT OF THE SHAPED PRODUCTS, e.g. REPAIRING
- B29C45/00—Injection moulding, i.e. forcing the required volume of moulding material through a nozzle into a closed mould; Apparatus therefor
- B29C45/17—Component parts, details or accessories; Auxiliary operations
- B29C45/26—Moulds
- B29C45/27—Sprue channels ; Runner channels or runner nozzles
- B29C45/28—Closure devices therefor
- B29C45/2806—Closure devices therefor consisting of needle valve systems
- B29C45/281—Drive means therefor
- B29C2045/2841—Needle valves driven by a plurality of coaxial pistons
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
- F15B2211/7051—Linear output members
- F15B2211/7055—Linear output members having more than two chambers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/76—Control of force or torque of the output member
Definitions
- the present invention relates to a linear actuator having a plurality of piston surfaces for providing a higher output force upon application of a pressurized fluid to a given diameter actuator. More particularly, the present invention relates to a pressurized-fluid actuator of compact size and that includes a movable cylinder having one or more axially spaced piston surfaces for applying an actuating force for movement of the cylinder in a retraction direction, and at least one additional piston surface for applying additional actuating force for moving the cylinder in an extension direction.
- Linear actuators incorporating pistons that move within cylinders upon application of a pressurized fluid are well known in the art and are used for many different purposes.
- the output force provided by such actuators can be increased either by increasing the pressure of the fluid supplied to operate the actuator, or by increasing the diameter of the piston to increase the surface area of the piston.
- some applications require the actuator to be contained within a very limited space (so that the diameter of the piston cannot be increased). In such applications, the pressure necessary to provide the required actuating force may exceed practical limits. Accordingly, an alternative design is needed that will provide the required actuating force in a limited space at a reasonable pressure.
- an actuator in accordance with one aspect of the present invention includes a stationary cylinder of tubular form that defines an inner cylindrical surface.
- a movable cylinder is slidably carried within the stationary cylinder and has a rod affixed thereto, the rod extending from the movable cylinder in an axial direction relative to the stationary cylinder.
- the movable cylinder divides the stationary cylinder into an upper chamber and a lower chamber.
- the movable cylinder also includes an inner cylindrical space.
- a fixed piston extends transversely across the inner cylindrical space of the movable cylinder, thereby dividing the inner cylindrical space into a first inner chamber and a second inner chamber.
- a first fluid conduit is in communication with the upper chamber of the stationary cylinder and with the first inner chamber of the movable cylinder. Supplying a pressurized fluid to the first fluid conduit thus initiates movement of the movable cylinder and rod in a forward direction relative to the stationary cylinder, thereby providing a rod extension stroke.
- a second fluid conduit is in fluid communication with the second inner chamber for moving the movable cylinder and rod in a reverse direction relative to the stationary cylinder when pressurized fluid is introduced, thereby providing a rod retraction stroke.
- the actuator includes a stationary cylinder containing a movable cylinder that is divided into multiple inner chambers by fixed (stationary) pistons.
- the inner chambers are in fluid communication with extension and retraction ports provided in the cylinder wall.
- Introduction of pressurized fluid into the retraction port causes the fluid pressure to act on “n” piston surface(s) to retract the movable cylinder and rod
- introduction of pressurized fluid into the extension port causes the fluid pressure to act on “n+1” axially-spaced piston surfaces to extend the movable cylinder and rod.
- the actuator provides an increased extension force without increasing the overall diameter of the actuator and without increasing the pressure of the fluid.
- FIG. 1 is a fragmentary, side elevational view, partially in cross-section, of a portion of a mold assembly in an injection molding machine incorporating a linear actuator in accordance with the present invention operatively associated with a valve gate for controlling the flow of plasticated material to a mold cavity, wherein the movable cylinder is in a fully retracted position so that the valve pin is in the open position to allow flow of plastic melt into the mold cavity.
- FIG. 2 is an enlarged view of the portion of FIG. 1 contained within the circle 2 .
- FIG. 3 is a cross-sectional view of the actuator in accordance with the present invention, taken along the line 3 - 3 of FIG. 1.
- FIG. 4 is a cross-sectional view of the actuator in accordance with the present invention, taken along the line 4 - 4 of FIG. 1.
- FIG. 5 is a partial side elevational view similar to that of FIG. 1, showing the movable cylinder of the actuator in an intermediate position between fully retracted and fully extended positions.
- FIG. 6 is a partial side elevational view similar to that of FIGS. 1 and 5 showing the movable cylinder of the actuator in a fully extended position.
- FIG. 7 is a fragmentary, side elevational view, partially in cross-section, of a portion of a mold assembly, showing an alternate embodiment of an actuator in accordance with the present invention capable of providing increased actuating force, wherein the movable cylinder of the actuator is in a fully retracted position.
- FIG. 8 is a partial side elevational view of the same alternate embodiment shown in FIG. 7, wherein the movable cylinder of the actuator in a fully extended position.
- FIGS. 1 and 2 of the drawings there is shown a valve actuator 10 in accordance with the present invention.
- a flow nozzle 12 for receiving a flow of molten plastic material from an injection unit (not shown) supplied via a molding material passageway 14 .
- the nozzle 12 conveys and controls the supply of plastic melt to a mold cavity 16 that is defined by respective opposed, suitably-shaped recesses formed in a first mold segment 18 and a cooperating second mold segment 20 .
- the first mold segment 18 is maintained in a stationary condition.
- the second mold segment 20 is supported for movement relative to the first mold segment 18 to define the closed mold cavity 16 when the mold segments 18 , 20 are in contact, and to allow removal of a molded part by separating the mold segments 18 , 20 to open the mold cavity 16 .
- the plastic melt from the injection unit is caused to flow through the molding material passageway 14 and into the nozzle 12 .
- the nozzle 12 includes a discharge outlet or gate 22 that communicates directly with the mold cavity 16 .
- Flow of the plastic melt through the nozzle 12 is controlled by a valve pin 26 that is movable toward and away from the gate 22 to close and open selectively the gate 22 at appropriate times during a molding cycle. As shown in FIG. 1, the valve pin 26 is in the retracted or open position, which will allow flow of plastic melt through the nozzle 12 and into the mold cavity 16 .
- the valve pin 26 is an end portion of an elongated rod 28 that has its opposite end connected to the actuator 10 .
- the actuator 10 includes two concentric cylinders, a movable cylinder 30 that connects to the rod 28 , and a stationary cylinder 32 that slidably receives the movable cylinder 30 .
- An upper end wall 34 and a lower end wall 36 serve to close the movable cylinder 30 , so that it functions as a piston within the stationary cylinder 32 , as will be more fully described later.
- An end cap 38 closes one end of the stationary cylinder 32 to define an upper chamber 40 between the end cap 38 and the upper end wall 34 of the movable cylinder 30 .
- the actuator 10 is contained within an appropriately sized bore 24 in a mold plate 44 , and is held in place by appropriate fasteners, such as bolts 42 through the end cap 38 .
- the mold plate 44 is suitably secured relative to the nozzle 12 in mold segment 18 so that the rod 28 and associated valve pin 26 are properly oriented relative to the valve seat 46 in the nozzle 12 .
- the valve seat 46 includes a tapered passageway that diverges from the gate 22 to a cylindrical bore 48 that interconnects with the passageway 14 .
- the stationary cylinder 32 has a stepped diameter to be received by the similarly stepped bore 24 in mold plate 44 .
- This stepped design facilitates an economical assembly, using a fluid-tight seal between the stationary cylinder 32 and the bore 24 , so that the lower portion of the bore 24 and the stationary cylinder 32 work together to contain the movable cylinder 30 .
- the bore 24 in the mold plate 44 could be machined with a constant diameter to receive a stationary cylinder 32 having a straight diameter and extending to the bottom of the bore 24 to fully contain the movable cylinder 30 .
- a lower chamber 41 is defined by the space between the lower end wall 36 and the bottom wall 25 of the bore 24 in plate 44 .
- a bore 45 in the plate 44 is sized to allow passage of the rod 28 with sufficient clearance to provide a vent to ambient atmosphere for the lower chamber 41 .
- a support post 50 rigidly connected to the end cap 38 , as by a bolt 52 , extends downwardly and passes through the upper end wall 34 and into the interior of the movable cylinder 30 .
- the support post 50 terminates at a transversely-extending fixed piston 54 .
- the fixed piston 54 is a disk-shaped member that has a peripheral edge 56 that is spaced inwardly of the inner surface of the cylinder side wall 58 of the stationary cylinder 32 , so that the piston 54 is contained within the movable cylinder 30 .
- the peripheral edge 56 preferably includes an annular recess 60 to receive a peripheral sealing ring 62 .
- the movable cylinder 30 is a hollow, generally cylindrical structure that is received within the stationary cylinder 32 and bore 24 for axial, sliding movement along the inner surfaces thereof.
- the annular lower end wall 36 of the cylinder 30 extends transversely inside the bore 24 just below the stationary cylinder 32 .
- the lower end wall 36 can comprise two portions fastened together by bolts 64 to facilitate manufacture, as well as attachment of the rod 28 to the movable cylinder 30 .
- the lower end wall 36 includes a flanged portion 66 with an outer peripheral recess 68 to receive a first outer sealing ring 70 on the movable cylinder 30 , which is slidable along and that sealingly engages the inner surface of the bore 24 .
- the lower end wall 36 with flanged portion 66 is positioned between the fixed piston 54 and the bottom wall 25 of the bore 24 .
- a tubular side wall 72 of the movable cylinder 30 Extending axially from the periphery of the lower end wall 36 adjacent and along the inner surface of the cylinder side wall 58 and toward the end cap 38 is a tubular side wall 72 of the movable cylinder 30 .
- a second outer sealing ring 74 and a third outer sealing ring 76 are each carried in annular recesses 78 , 80 , respectively, on the outer periphery of the side wall 72 of the movable cylinder 30 , in axially spaced relationship with the first outer sealing ring 70 and in axially spaced relationship with each other.
- Each of the second and third sealing rings 74 , 76 are slidable along and sealingly engage the inner surface of the cylinder side wall 58 .
- the end 82 of the rod 28 opposite from the valve pin 26 is securely received within the flanged portion 66 of the lower end wall 36 , so that both the movable cylinder 30 and the valve pin 26 move together.
- the upper end wall 34 of the movable cylinder 30 Spaced axially along the side wall 72 from the lower end wall 36 and on the opposite side of the fixed piston 54 from the lower end wall 36 is the upper end wall 34 of the movable cylinder 30 , extending across the interior space defined by the side wall 72 .
- the inner surface of the side wall 72 includes a radial step 84 against which the upper end wall 34 rests, and an annular retaining ring 86 is received in an inner peripheral groove 88 formed in the inner surface of the side wall 72 to retain the upper end wall 34 in position relative to the side wall 72 .
- the upper end wall 34 preferably includes an outer peripheral recess 89 to receive a sealing ring 90 , as well as an inner annular recess 92 to receive a sealing ring 94 , to facilitate a fluid tight seal of the upper end wall 34 with the side wall 72 and support post 50 , respectively.
- the volume between the lower end wall 36 and the fixed piston 54 defines a first inner chamber 96 within the cylinder 30
- the annular volume between the upper end wall 34 and the fixed piston 54 defines a second inner chamber 98 within the cylinder 30
- the side wall 72 includes radially-extending openings 100 that provide fluid communication with the second inner chamber 98 , as will be more fully explained later.
- a source of pressurized fluid such as pressurized gas or pressurized hydraulic fluid
- the connections between the ports 102 , 104 and the respective pressurized fluid source and lower pressure fluid reservoir can be effected through a suitable reversible flow control valve (not shown) of a type that is well known to those skilled in the art.
- the first port 102 connects with an annular chamber 106 surrounding the lower portion of the stationary cylinder side wall 58 and adjacent the lower end wall 36 of the movable cylinder 30 .
- the annular chamber 106 communicates with both the first inner chamber 96 and the upper chamber 40 of the stationary cylinder 32 via a passage 108 in the lower end wall 36 . More specifically, the passage 108 opens into the first inner chamber 96 , which communicates with the upper chamber 40 via a second passage 110 and radial openings 118 in the support post 50 of the fixed piston 54 , thus enabling fluid communication of the first port 102 with both the first inner chamber 96 and upper chamber 40 .
- the second port 104 terminates at a channel 112 that connects with radial openings 114 through the side wall 58 of the stationary cylinder 32 .
- the radial openings 114 communicate with an annular chamber 116 around the upper portion of the movable cylinder 30 .
- the annular chamber 116 connects with the second inner chamber 98 through the radially-extending openings 100 in the side wall 72 just below the radial step 84 , thereby enabling fluid communication between the second port 104 and the second inner chamber 98 of the movable cylinder 30 .
- the actuator 10 is shown in FIGS. 1 and 2 with the movable cylinder 30 , rod 28 , and valve pin 26 each in their retracted positions, relative to the stationary cylinder 32 and to the valve seat 46 .
- pressurized fluid is introduced through the first port 102 , while the second port 104 is in fluid communication with a lower pressure fluid reservoir, or the like.
- the introduction of pressurized fluid at the first port 102 causes the pressurized fluid to enter into and to flow through the annular channel 106 , then through the first passage 108 and into the first inner chamber 96 within the cylinder 30 .
- each of the upper chamber 40 and the first inner chamber 96 are at an elevated pressure, relative to the lower chamber 41 , which is vented to the atmosphere through the bore 45 around rod 28 , and relative to the second inner chamber 98 .
- the second inner chamber 98 is in fluid communication with the lower pressure fluid reservoir through the openings 100 , annular chamber 116 , radial openings 114 , annular channel 112 , and second port 104 .
- any fluid within the second inner chamber 98 passes through the openings 100 , into annular chamber 116 , through radial openings 114 , into annular channel 112 , and finally out through the second port 104 , which is at a lower pressure than the first port 102 .
- the continued application of greater fluid pressure at the first port 102 will cause the cylinder 30 to travel to the end of its extension stroke, as shown in FIG. 6.
- the upper end wall 34 makes contact with a forward cushion 120 attached to the fixed piston 54 and the end of the valve pin 26 is held tightly against the valve seat 46 to block flow through the gate 22 .
- air contained within the lower chamber 41 is exhausted through the bore 45 .
- the first port 102 In order to move the actuator 10 from the extended position shown in FIG. 6, thereby opening the gate 22 and allowing the flow of molten plastic material into the mold cavity 16 , the first port 102 must be disconnected from the source of pressurized fluid and is placed in communication with a lower pressure reservoir, or the like.
- the second port 104 is then connected with the source of pressurized fluid, and pressurized fluid enters the annular channel 112 through the second port 104 . From the annular channel 112 the pressurized fluid flows through the radial openings 114 in the side wall 58 and into the second inner chamber 98 within the cylinder 30 .
- the entry of pressurized fluid into the second inner chamber 98 applies a force against the inner surface the upper end wall 34 , causing the cylinder 30 and the valve pin 26 to retract into the stationary cylinder 32 until it reaches the position shown in FIG. 1, where the lower end wall 36 makes contact with a retract cushion 122 attached to the fixed piston 54 .
- the valve pin 26 retracts into the nozzle 12 and away from the gate 22 to allow molding material to flow through the nozzle 12 and into the mold cavity 16 .
- the partial vacuum that would otherwise be generated within the lower chamber 41 is relieved by allowing ambient air to enter the lower chamber 41 through the bore 25 around the rod 28 .
- FIGS. 7 and 8 show an alternate embodiment of a valve actuator 125 in accordance with the present invention that employs additional surfaces to further enhance the actuation force.
- the actuator 125 has an outer housing 126 and end cap 138 that are received in a mold plate 143 .
- a stationary cylinder 132 is received within the interior space defined by the housing 126 , the end cap 138 and a bore 124 in adjacent mold plate 144 that matches the inside diameter of the housing 126 .
- bolts 142 passthrough the end cap 138 and housing 126 to engage the underlying mold plate 144 to fix the actuator 125 in the mold assembly.
- the stationary cylinder 132 could be received within mating bores in the mold plates 143 , 144 or within a single mold plate, as in the previously described embodiment, eliminating the need for the outer housing 126 .
- a movable cylinder 130 is slidably received within the stationary cylinder 132 .
- An elongated rod 128 has one end 182 securely received within a lower end wall 136 of the movable cylinder 130 , so that both the movable cylinder 130 and the rod 128 move together, with the opposite end of the rod 128 functioning as a valve pin, as previously described.
- the end cap 138 closes one end of the stationary cylinder 132 to define an upper chamber 140 between an upper wall 134 of the movable cylinder 130 and the end cap 138 .
- a bottom wall 127 of the bore 124 closes the opposite end of the stationary cylinder 132 to fully contain the movable cylinder 130 .
- the actuator 125 includes a first port 202 and a second port 204 , each of which is alternately adapted to be in communication with a source of pressurized fluid (not shown), such as pressurized gas or pressurized hydraulic fluid, and with a lower pressure fluid reservoir (not shown), as described previously.
- the first port 202 extends through the outer housing 126 and terminates at a channel 206 that connects with a first passage 208 contained in a tubular side wall 158 of the cylinder 132 .
- the first passage 208 opens at one end 209 into the upper chamber 140 , as well as an intermediate point 210 and an opposite end 211 to enable fluid communication between the first port 202 and the interior of the movable cylinder 130 for purposes that will be hereinafter explained.
- the second port 204 extends through the outer housing 126 and terminates at a channel 212 that connects with a second passage 214 contained in the wall 158 of the cylinder 132 .
- the second passage 214 opens at one end 215 into an annular channel 216 , as well as at an opening 217 to a second annular channel 218 to enable fluid communication between the second port 204 and the interior of the movable cylinder 130 .
- the movable cylinder 130 is a hollow, generally cylindrical structure that is received within the stationary cylinder 132 for axial, sliding movement along the inner surface thereof.
- the movable cylinder 130 includes an annular lower wall 136 that extends transversely to seal against the inside the cylinder 132 .
- the lower end wall 136 includes an outer peripheral recess 168 to receive a first outer sealing ring 170 that is slidable along and that sealingly engages the inner surface of the cylinder 132 .
- Extending axially from the periphery of the lower end wall 136 adjacent and along the inner surface of the wall 158 of the cylinder 132 and toward the end cap 138 is a tubular side wall 172 .
- the annular upper end wall 134 extends across the interior of the end of the movable cylinder 130 adjacent the end cap 138 .
- the upper end wall 134 is held in place by retaining rings 186 in grooves 184 in the side wall 172 .
- Four outer sealing rings 174 are each carried in annular recesses 176 on the outer periphery of the side wall 172 in axially spaced relationship with the first outer sealing ring 170 and in axially spaced relationship with each other.
- Each of the outer sealing rings 174 is slidable along and sealingly engages the inner surface of the side wall 158 of the stationary cylinder 132 .
- a support post 150 that passes through the upper end wall 134 of the cylinder 130 and extends into the interior of the cylinder 130 to terminate at a transversely-extending, first fixed piston 154 .
- a second fixed piston 155 is attached to the support post 150 by suitable means, such as retaining rings 156 , at a position intermediate the end cap 138 and the first fixed piston 154 .
- the fixed pistons 154 , 155 are disk-shaped members that are sized to be received within the tubular side wall 172 .
- the peripheral edge of each of the fixed pistons 154 , 155 includes an annular recess 160 to receive a peripheral sealing ring 162 .
- an intermediate wall 135 Spaced axially along the side wall 172 from the lower end wall 136 and between the fixed pistons 154 , 155 is an intermediate wall 135 that extends across the interior of the movable cylinder 130 and is attached to the side wall 172 by retaining rings 186 .
- the intermediate wall 135 and upper end wall 134 can include interior and peripheral recess 188 , 192 to receive an annular sealing rings 190 , 194 , as shown.
- the volume between the lower end wall 136 and the first fixed piston 154 defines a first chamber 195 within the movable cylinder 130 .
- the annular volume between the first fixed piston 154 and the intermediate wall 135 defines a second chamber 196 .
- the annular volume between the intermediate wall 135 and the second fixed piston 155 defines a third chamber 197 , and the annular volume between the upper end wall 134 and the second fixed piston 155 defines a fourth chamber 198 within the movable cylinder 130 .
- the side wall 172 includes radially extending openings 146 to allow fluid communication between the first inner chamber 195 and the first passage 208 through the end opening 211 .
- openings 149 provide a passage between the second inner chamber 196 and the annular channel 218
- openings 148 provide a passage between the third inner chamber 197 and the annular channel 219
- openings 147 provide a passage between the fourth inner chamber 198 and the annular channel 216 .
- the actuator 125 constructed as described, the upper chamber 140 , the first chamber 195 and the third chamber 197 are in continuous fluid communication with the first passage 208 , and thereby with the first port 202 via annular channel 206 .
- the second chamber 196 and fourth chamber 198 are in continuous communication with the second passage 214 and thereby with the second port 204 via channel 212 .
- the actuator 125 is shown in FIG. 7 with the movable cylinder 130 and rod 128 (and the associated valve pin) each in their retracted positions, relative to the stationary cylinder 132 .
- pressurized fluid is introduced through the first port 202 , while the second port 204 is in fluid communication with a lower pressure fluid reservoir, or the like.
- the introduction of pressurized fluid at the first port 202 causes the pressurized fluid to enter into and to flow through the annular channel 206 and into the first passage 208 .
- each of the upper chamber 140 , the third chamber 197 and the first chamber 195 are at an elevated pressure relative to the second and fourth chambers 196 , 198 .
- the resultant pressure differentials acting against each of the upper end wall 134 , intermediate wall 135 and lower end wall 136 cause the movable cylinder 130 to move toward the bottom wall 127 , i.e., from the positions shown in FIG. 7 to the positions shown in FIG. 8.
- the first port 202 is disconnected from the source of pressurized fluid and is placed in communication with a lower pressure reservoir, or the like.
- the second port 204 is then connected with the source of pressurized fluid, and pressurized fluid enters the channel 212 , flows into the passage 214 , and then into the annular channels 216 , 218 via the openings 215 , 217 .
- the pressurized fluid flows through the openings 147 , 149 in the side wall 172 and into the fourth chamber 198 and second chamber 196 .
- the increased pressure against the inner surface of the upper end wall 143 and intermediate wall 135 causes the movable cylinder 130 to retract into the stationary cylinder 132 .
- the valve pin retracts away from the gate to allow molding material to flow through the nozzle.
- the reduced air pressure that would otherwise be generated between the lower end wall 136 and the bottom wall 127 is relieved by admitting ambient air through the bore 145 surrounding the rod 128 .
- an actuator in accordance with the present invention provides a greater output force within the same cylinder diameter, thereby allowing such an actuator to be utilized in confined spaces that would preclude larger diameter cylinders if higher actuation forces were needed. If a similar space limitation existed but a higher actuation force than would be available using a single piston were needed with only a relatively low fluid pressure source available, the actuator in accordance with the present invention would provide an increased actuation force at that lower fluid pressure.
- the actuation force can be further multiplied, as desired, by repeating the described arrangement of the fixed pistons and intermediate movable cylinder walls, thereby increasing the number of actuating surfaces.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Manufacturing & Machinery (AREA)
- Moulds For Moulding Plastics Or The Like (AREA)
- Fluid-Driven Valves (AREA)
- Actuator (AREA)
Abstract
Description
- 1. Field of the Invention
- The present invention relates to a linear actuator having a plurality of piston surfaces for providing a higher output force upon application of a pressurized fluid to a given diameter actuator. More particularly, the present invention relates to a pressurized-fluid actuator of compact size and that includes a movable cylinder having one or more axially spaced piston surfaces for applying an actuating force for movement of the cylinder in a retraction direction, and at least one additional piston surface for applying additional actuating force for moving the cylinder in an extension direction.
- 2. Description of the Related Art
- Linear actuators incorporating pistons that move within cylinders upon application of a pressurized fluid are well known in the art and are used for many different purposes. Generally, the output force provided by such actuators can be increased either by increasing the pressure of the fluid supplied to operate the actuator, or by increasing the diameter of the piston to increase the surface area of the piston. However, some applications require the actuator to be contained within a very limited space (so that the diameter of the piston cannot be increased). In such applications, the pressure necessary to provide the required actuating force may exceed practical limits. Accordingly, an alternative design is needed that will provide the required actuating force in a limited space at a reasonable pressure.
- A number of actuator constructions have been devised in an effort to respond to the shortcoming described above. Although the prior art discloses various devices for providing increased output force from a pressurized-fluid operated actuator, the devices typically either involve a complex mechanism or otherwise fail to reduce the size of the actuator sufficiently to enable its use in a confined space.
- Briefly stated, in accordance with one aspect of the present invention an actuator is provided that includes a stationary cylinder of tubular form that defines an inner cylindrical surface. A movable cylinder is slidably carried within the stationary cylinder and has a rod affixed thereto, the rod extending from the movable cylinder in an axial direction relative to the stationary cylinder. The movable cylinder divides the stationary cylinder into an upper chamber and a lower chamber. The movable cylinder also includes an inner cylindrical space.
- A fixed piston extends transversely across the inner cylindrical space of the movable cylinder, thereby dividing the inner cylindrical space into a first inner chamber and a second inner chamber. A first fluid conduit is in communication with the upper chamber of the stationary cylinder and with the first inner chamber of the movable cylinder. Supplying a pressurized fluid to the first fluid conduit thus initiates movement of the movable cylinder and rod in a forward direction relative to the stationary cylinder, thereby providing a rod extension stroke. A second fluid conduit is in fluid communication with the second inner chamber for moving the movable cylinder and rod in a reverse direction relative to the stationary cylinder when pressurized fluid is introduced, thereby providing a rod retraction stroke.
- In accordance with another aspect of the present invention, the actuator includes a stationary cylinder containing a movable cylinder that is divided into multiple inner chambers by fixed (stationary) pistons. The inner chambers are in fluid communication with extension and retraction ports provided in the cylinder wall. Introduction of pressurized fluid into the retraction port causes the fluid pressure to act on “n” piston surface(s) to retract the movable cylinder and rod, while introduction of pressurized fluid into the extension port causes the fluid pressure to act on “n+1” axially-spaced piston surfaces to extend the movable cylinder and rod. Accordingly, the actuator provides an increased extension force without increasing the overall diameter of the actuator and without increasing the pressure of the fluid.
- FIG. 1 is a fragmentary, side elevational view, partially in cross-section, of a portion of a mold assembly in an injection molding machine incorporating a linear actuator in accordance with the present invention operatively associated with a valve gate for controlling the flow of plasticated material to a mold cavity, wherein the movable cylinder is in a fully retracted position so that the valve pin is in the open position to allow flow of plastic melt into the mold cavity.
- FIG. 2 is an enlarged view of the portion of FIG. 1 contained within the
circle 2. - FIG. 3 is a cross-sectional view of the actuator in accordance with the present invention, taken along the line3-3 of FIG. 1.
- FIG. 4 is a cross-sectional view of the actuator in accordance with the present invention, taken along the line4-4 of FIG. 1.
- FIG. 5 is a partial side elevational view similar to that of FIG. 1, showing the movable cylinder of the actuator in an intermediate position between fully retracted and fully extended positions.
- FIG. 6 is a partial side elevational view similar to that of FIGS. 1 and 5 showing the movable cylinder of the actuator in a fully extended position.
- FIG. 7 is a fragmentary, side elevational view, partially in cross-section, of a portion of a mold assembly, showing an alternate embodiment of an actuator in accordance with the present invention capable of providing increased actuating force, wherein the movable cylinder of the actuator is in a fully retracted position.
- FIG. 8 is a partial side elevational view of the same alternate embodiment shown in FIG. 7, wherein the movable cylinder of the actuator in a fully extended position.
- Referring first to FIGS. 1 and 2 of the drawings, there is shown a
valve actuator 10 in accordance with the present invention. Operatively associated with theactuator 10 is aflow nozzle 12 for receiving a flow of molten plastic material from an injection unit (not shown) supplied via amolding material passageway 14. Thenozzle 12 conveys and controls the supply of plastic melt to amold cavity 16 that is defined by respective opposed, suitably-shaped recesses formed in afirst mold segment 18 and a cooperatingsecond mold segment 20. As will be appreciated by those skilled in the art, thefirst mold segment 18 is maintained in a stationary condition. Thesecond mold segment 20 is supported for movement relative to thefirst mold segment 18 to define the closedmold cavity 16 when themold segments mold segments mold cavity 16. - During operation, the plastic melt from the injection unit is caused to flow through the
molding material passageway 14 and into thenozzle 12. Thenozzle 12 includes a discharge outlet orgate 22 that communicates directly with themold cavity 16. Flow of the plastic melt through thenozzle 12 is controlled by avalve pin 26 that is movable toward and away from thegate 22 to close and open selectively thegate 22 at appropriate times during a molding cycle. As shown in FIG. 1, thevalve pin 26 is in the retracted or open position, which will allow flow of plastic melt through thenozzle 12 and into themold cavity 16. - The
valve pin 26 is an end portion of anelongated rod 28 that has its opposite end connected to theactuator 10. More specifically, theactuator 10 includes two concentric cylinders, amovable cylinder 30 that connects to therod 28, and astationary cylinder 32 that slidably receives themovable cylinder 30. Anupper end wall 34 and alower end wall 36 serve to close themovable cylinder 30, so that it functions as a piston within thestationary cylinder 32, as will be more fully described later. Anend cap 38 closes one end of thestationary cylinder 32 to define anupper chamber 40 between theend cap 38 and theupper end wall 34 of themovable cylinder 30. Preferably, theactuator 10 is contained within an appropriately sizedbore 24 in amold plate 44, and is held in place by appropriate fasteners, such asbolts 42 through theend cap 38. Themold plate 44 is suitably secured relative to thenozzle 12 inmold segment 18 so that therod 28 and associatedvalve pin 26 are properly oriented relative to thevalve seat 46 in thenozzle 12. As shown, thevalve seat 46 includes a tapered passageway that diverges from thegate 22 to acylindrical bore 48 that interconnects with thepassageway 14. - Preferably, the
stationary cylinder 32 has a stepped diameter to be received by the similarly steppedbore 24 inmold plate 44. This stepped design facilitates an economical assembly, using a fluid-tight seal between thestationary cylinder 32 and thebore 24, so that the lower portion of thebore 24 and thestationary cylinder 32 work together to contain themovable cylinder 30. This minimizes the overall length of thestationary cylinder 32 since thelower end wall 36 of the movingcylinder 30 seals against the lower portion of thebore 24 in themold plate 44. Alternatively, thebore 24 in themold plate 44 could be machined with a constant diameter to receive astationary cylinder 32 having a straight diameter and extending to the bottom of thebore 24 to fully contain themovable cylinder 30. In either case, alower chamber 41 is defined by the space between thelower end wall 36 and thebottom wall 25 of thebore 24 inplate 44. Abore 45 in theplate 44 is sized to allow passage of therod 28 with sufficient clearance to provide a vent to ambient atmosphere for thelower chamber 41. - Within the stationary cylinder32 a
support post 50 rigidly connected to theend cap 38, as by abolt 52, extends downwardly and passes through theupper end wall 34 and into the interior of themovable cylinder 30. Thesupport post 50 terminates at a transversely-extendingfixed piston 54. The fixedpiston 54 is a disk-shaped member that has aperipheral edge 56 that is spaced inwardly of the inner surface of thecylinder side wall 58 of thestationary cylinder 32, so that thepiston 54 is contained within themovable cylinder 30. Theperipheral edge 56 preferably includes anannular recess 60 to receive aperipheral sealing ring 62. - The
movable cylinder 30 is a hollow, generally cylindrical structure that is received within thestationary cylinder 32 and bore 24 for axial, sliding movement along the inner surfaces thereof. The annularlower end wall 36 of thecylinder 30 extends transversely inside thebore 24 just below thestationary cylinder 32. As shown, thelower end wall 36 can comprise two portions fastened together bybolts 64 to facilitate manufacture, as well as attachment of therod 28 to themovable cylinder 30. Thelower end wall 36 includes aflanged portion 66 with an outerperipheral recess 68 to receive a firstouter sealing ring 70 on themovable cylinder 30, which is slidable along and that sealingly engages the inner surface of thebore 24. As shown, thelower end wall 36 withflanged portion 66 is positioned between the fixedpiston 54 and thebottom wall 25 of thebore 24. - Extending axially from the periphery of the
lower end wall 36 adjacent and along the inner surface of thecylinder side wall 58 and toward theend cap 38 is atubular side wall 72 of themovable cylinder 30. A second outer sealing ring 74 and a third outer sealing ring 76 are each carried inannular recesses side wall 72 of themovable cylinder 30, in axially spaced relationship with the firstouter sealing ring 70 and in axially spaced relationship with each other. Each of the second and third sealing rings 74, 76 are slidable along and sealingly engage the inner surface of thecylinder side wall 58. Theend 82 of therod 28 opposite from thevalve pin 26 is securely received within theflanged portion 66 of thelower end wall 36, so that both themovable cylinder 30 and thevalve pin 26 move together. - Spaced axially along the
side wall 72 from thelower end wall 36 and on the opposite side of the fixedpiston 54 from thelower end wall 36 is theupper end wall 34 of themovable cylinder 30, extending across the interior space defined by theside wall 72. As shown most clearly in FIG. 2, the inner surface of theside wall 72 includes aradial step 84 against which theupper end wall 34 rests, and anannular retaining ring 86 is received in an innerperipheral groove 88 formed in the inner surface of theside wall 72 to retain theupper end wall 34 in position relative to theside wall 72. Additionally, theupper end wall 34 preferably includes an outerperipheral recess 89 to receive a sealingring 90, as well as an innerannular recess 92 to receive a sealingring 94, to facilitate a fluid tight seal of theupper end wall 34 with theside wall 72 andsupport post 50, respectively. - As best seen in FIG. 5, the volume between the
lower end wall 36 and the fixedpiston 54 defines a firstinner chamber 96 within thecylinder 30, and the annular volume between theupper end wall 34 and the fixedpiston 54 defines a secondinner chamber 98 within thecylinder 30. Theside wall 72 includes radially-extendingopenings 100 that provide fluid communication with the secondinner chamber 98, as will be more fully explained later. - A
first port 102 andsecond port 104 in themold plate 44 open into thebore 24, each of theports ports first port 102 connects with anannular chamber 106 surrounding the lower portion of the stationarycylinder side wall 58 and adjacent thelower end wall 36 of themovable cylinder 30. Theannular chamber 106 communicates with both the firstinner chamber 96 and theupper chamber 40 of thestationary cylinder 32 via apassage 108 in thelower end wall 36. More specifically, thepassage 108 opens into the firstinner chamber 96, which communicates with theupper chamber 40 via asecond passage 110 andradial openings 118 in thesupport post 50 of the fixedpiston 54, thus enabling fluid communication of thefirst port 102 with both the firstinner chamber 96 andupper chamber 40. - The
second port 104 terminates at achannel 112 that connects withradial openings 114 through theside wall 58 of thestationary cylinder 32. Theradial openings 114 communicate with anannular chamber 116 around the upper portion of themovable cylinder 30. Theannular chamber 116 connects with the secondinner chamber 98 through the radially-extendingopenings 100 in theside wall 72 just below theradial step 84, thereby enabling fluid communication between thesecond port 104 and the secondinner chamber 98 of themovable cylinder 30. - The
actuator 10 is shown in FIGS. 1 and 2 with themovable cylinder 30,rod 28, andvalve pin 26 each in their retracted positions, relative to thestationary cylinder 32 and to thevalve seat 46. In operation, to cause thevalve pin 26 andcylinder 30 to move from their retracted positions, pressurized fluid is introduced through thefirst port 102, while thesecond port 104 is in fluid communication with a lower pressure fluid reservoir, or the like. The introduction of pressurized fluid at thefirst port 102 causes the pressurized fluid to enter into and to flow through theannular channel 106, then through thefirst passage 108 and into the firstinner chamber 96 within thecylinder 30. Simultaneously, a portion of the pressurized fluid flows from the firstinner chamber 96 into and through thesecond passage 110 andradial openings 118 to enter into theupper chamber 40. Consequently, each of theupper chamber 40 and the firstinner chamber 96 are at an elevated pressure, relative to thelower chamber 41, which is vented to the atmosphere through thebore 45 aroundrod 28, and relative to the secondinner chamber 98. The secondinner chamber 98 is in fluid communication with the lower pressure fluid reservoir through theopenings 100,annular chamber 116,radial openings 114,annular channel 112, andsecond port 104. - The resultant pressure differentials acting against each of the
upper end wall 34 andlower end wall 36 cause thecylinder 30 to move toward thebottom wall 25 of thebore 24, which causes thevalve pin 26 to move toward thevalve seat 46; i.e., from the position shown in FIG. 1 through an intermediate position, such as that shown in FIG. 5. For the time during which thecylinder 30 andvalve pin 26 are moving in this manner, the volume of each of thelower chamber 41 and the secondinner chamber 98 is decreasing, while the volume of each of the firstinner chamber 96 andupper chamber 40 is increasing. At the same time, any fluid within the secondinner chamber 98 passes through theopenings 100, intoannular chamber 116, throughradial openings 114, intoannular channel 112, and finally out through thesecond port 104, which is at a lower pressure than thefirst port 102. The continued application of greater fluid pressure at thefirst port 102 will cause thecylinder 30 to travel to the end of its extension stroke, as shown in FIG. 6. Upon completion of the extension stroke, theupper end wall 34 makes contact with aforward cushion 120 attached to the fixedpiston 54 and the end of thevalve pin 26 is held tightly against thevalve seat 46 to block flow through thegate 22. To avoid a pressure build-up that would act against thelower end wall 36, air contained within thelower chamber 41 is exhausted through thebore 45. - In order to move the actuator10 from the extended position shown in FIG. 6, thereby opening the
gate 22 and allowing the flow of molten plastic material into themold cavity 16, thefirst port 102 must be disconnected from the source of pressurized fluid and is placed in communication with a lower pressure reservoir, or the like. Thesecond port 104 is then connected with the source of pressurized fluid, and pressurized fluid enters theannular channel 112 through thesecond port 104. From theannular channel 112 the pressurized fluid flows through theradial openings 114 in theside wall 58 and into the secondinner chamber 98 within thecylinder 30. The entry of pressurized fluid into the secondinner chamber 98 applies a force against the inner surface theupper end wall 34, causing thecylinder 30 and thevalve pin 26 to retract into thestationary cylinder 32 until it reaches the position shown in FIG. 1, where thelower end wall 36 makes contact with a retract cushion 122 attached to the fixedpiston 54. As a result, thevalve pin 26 retracts into thenozzle 12 and away from thegate 22 to allow molding material to flow through thenozzle 12 and into themold cavity 16. The partial vacuum that would otherwise be generated within thelower chamber 41 is relieved by allowing ambient air to enter thelower chamber 41 through thebore 25 around therod 28. - FIGS. 7 and 8 show an alternate embodiment of a
valve actuator 125 in accordance with the present invention that employs additional surfaces to further enhance the actuation force. Theactuator 125 has anouter housing 126 andend cap 138 that are received in amold plate 143. Astationary cylinder 132 is received within the interior space defined by thehousing 126, theend cap 138 and abore 124 inadjacent mold plate 144 that matches the inside diameter of thehousing 126. Preferably,bolts 142 passthrough theend cap 138 andhousing 126 to engage theunderlying mold plate 144 to fix theactuator 125 in the mold assembly. Alternatively, thestationary cylinder 132 could be received within mating bores in themold plates outer housing 126. Amovable cylinder 130 is slidably received within thestationary cylinder 132. Anelongated rod 128 has oneend 182 securely received within alower end wall 136 of themovable cylinder 130, so that both themovable cylinder 130 and therod 128 move together, with the opposite end of therod 128 functioning as a valve pin, as previously described. Theend cap 138 closes one end of thestationary cylinder 132 to define anupper chamber 140 between anupper wall 134 of themovable cylinder 130 and theend cap 138. Abottom wall 127 of thebore 124 closes the opposite end of thestationary cylinder 132 to fully contain themovable cylinder 130. - The
actuator 125 includes afirst port 202 and asecond port 204, each of which is alternately adapted to be in communication with a source of pressurized fluid (not shown), such as pressurized gas or pressurized hydraulic fluid, and with a lower pressure fluid reservoir (not shown), as described previously. Thefirst port 202 extends through theouter housing 126 and terminates at achannel 206 that connects with afirst passage 208 contained in atubular side wall 158 of thecylinder 132. Thefirst passage 208 opens at oneend 209 into theupper chamber 140, as well as anintermediate point 210 and anopposite end 211 to enable fluid communication between thefirst port 202 and the interior of themovable cylinder 130 for purposes that will be hereinafter explained. Thesecond port 204 extends through theouter housing 126 and terminates at achannel 212 that connects with asecond passage 214 contained in thewall 158 of thecylinder 132. Thesecond passage 214 opens at oneend 215 into anannular channel 216, as well as at anopening 217 to a secondannular channel 218 to enable fluid communication between thesecond port 204 and the interior of themovable cylinder 130. - The
movable cylinder 130 is a hollow, generally cylindrical structure that is received within thestationary cylinder 132 for axial, sliding movement along the inner surface thereof. Themovable cylinder 130 includes an annularlower wall 136 that extends transversely to seal against the inside thecylinder 132. Thelower end wall 136 includes an outerperipheral recess 168 to receive a firstouter sealing ring 170 that is slidable along and that sealingly engages the inner surface of thecylinder 132. Extending axially from the periphery of thelower end wall 136 adjacent and along the inner surface of thewall 158 of thecylinder 132 and toward theend cap 138 is atubular side wall 172. The annularupper end wall 134 extends across the interior of the end of themovable cylinder 130 adjacent theend cap 138. Theupper end wall 134 is held in place by retainingrings 186 ingrooves 184 in theside wall 172. Four outer sealing rings 174 are each carried inannular recesses 176 on the outer periphery of theside wall 172 in axially spaced relationship with the firstouter sealing ring 170 and in axially spaced relationship with each other. Each of the outer sealing rings 174 is slidable along and sealingly engages the inner surface of theside wall 158 of thestationary cylinder 132. - Attached to the
end cap 138 by abolt 152 is asupport post 150 that passes through theupper end wall 134 of thecylinder 130 and extends into the interior of thecylinder 130 to terminate at a transversely-extending, first fixedpiston 154. A second fixedpiston 155 is attached to thesupport post 150 by suitable means, such as retaining rings 156, at a position intermediate theend cap 138 and the first fixedpiston 154. The fixedpistons tubular side wall 172. The peripheral edge of each of the fixedpistons annular recess 160 to receive aperipheral sealing ring 162. Spaced axially along theside wall 172 from thelower end wall 136 and between thefixed pistons intermediate wall 135 that extends across the interior of themovable cylinder 130 and is attached to theside wall 172 by retainingrings 186. Theintermediate wall 135 andupper end wall 134 can include interior andperipheral recess - The volume between the
lower end wall 136 and the first fixedpiston 154 defines afirst chamber 195 within themovable cylinder 130. The annular volume between the first fixedpiston 154 and theintermediate wall 135 defines asecond chamber 196. The annular volume between theintermediate wall 135 and the second fixedpiston 155 defines athird chamber 197, and the annular volume between theupper end wall 134 and the second fixedpiston 155 defines afourth chamber 198 within themovable cylinder 130. Theside wall 172 includes radially extendingopenings 146 to allow fluid communication between the firstinner chamber 195 and thefirst passage 208 through theend opening 211.Similar openings 149 provide a passage between the secondinner chamber 196 and theannular channel 218,openings 148 provide a passage between the thirdinner chamber 197 and theannular channel 219, andopenings 147 provide a passage between the fourthinner chamber 198 and theannular channel 216. - With the
actuator 125 constructed as described, theupper chamber 140, thefirst chamber 195 and thethird chamber 197 are in continuous fluid communication with thefirst passage 208, and thereby with thefirst port 202 viaannular channel 206. Similarly, thesecond chamber 196 andfourth chamber 198 are in continuous communication with thesecond passage 214 and thereby with thesecond port 204 viachannel 212. - The
actuator 125 is shown in FIG. 7 with themovable cylinder 130 and rod 128 (and the associated valve pin) each in their retracted positions, relative to thestationary cylinder 132. In operation, to cause the valve pin andmovable cylinder 130 to move from their retracted positions, pressurized fluid is introduced through thefirst port 202, while thesecond port 204 is in fluid communication with a lower pressure fluid reservoir, or the like. The introduction of pressurized fluid at thefirst port 202 causes the pressurized fluid to enter into and to flow through theannular channel 206 and into thefirst passage 208. The fluid then flows simultaneously through (a)opening 209 into theupper chamber 140, (b) opening 210 to channel 219, through theopenings 148 and into thethird chamber 197, and (c)opening 211, throughopenings 146 and into thefirst chamber 195. Consequently, each of theupper chamber 140, thethird chamber 197 and thefirst chamber 195 are at an elevated pressure relative to the second andfourth chambers upper end wall 134,intermediate wall 135 andlower end wall 136 cause themovable cylinder 130 to move toward thebottom wall 127, i.e., from the positions shown in FIG. 7 to the positions shown in FIG. 8. - As the
movable cylinder 130 moves from the retracted position to the extended position, the volume of each of thefourth chamber 198 and thesecond chamber 196 is decreasing, while the volume of each of thefirst chamber 195,third chamber 197 andupper chamber 140 is increasing. At the same time, any fluid within theforth chamber 198 andsecond chamber 196 passes through thechannels passage 214 and out thesecond port 204, which is at a lower pressure than is thefirst port 202. The continued application of greater fluid pressure at thefirst port 202 will cause themovable cylinder 130 to travel to the end of its extension stroke, as shown in FIG. 8, at which position thelower end wall 136 is in abutment with aforward cushion 164 attached to thebottom wall 127, and the valve pin will be against the valve seat to block flow through the mold gate. To avoid the resistance that would otherwise act against thelower end wall 136, air contained between thelower end wall 136 and thebottom wall 127 is exhausted through abore 145 in themold plate 144 through which therod 128 also passes. - In order to open the valve and allow the flow of molten plastic material into the mold cavity, the
first port 202 is disconnected from the source of pressurized fluid and is placed in communication with a lower pressure reservoir, or the like. Thesecond port 204 is then connected with the source of pressurized fluid, and pressurized fluid enters thechannel 212, flows into thepassage 214, and then into theannular channels openings annular channels openings side wall 172 and into thefourth chamber 198 andsecond chamber 196. The increased pressure against the inner surface of theupper end wall 143 andintermediate wall 135 causes themovable cylinder 130 to retract into thestationary cylinder 132. As a result, the valve pin retracts away from the gate to allow molding material to flow through the nozzle. The reduced air pressure that would otherwise be generated between thelower end wall 136 and thebottom wall 127 is relieved by admitting ambient air through thebore 145 surrounding therod 128. - It will therefore be apparent that an actuator in accordance with the present invention provides a greater output force within the same cylinder diameter, thereby allowing such an actuator to be utilized in confined spaces that would preclude larger diameter cylinders if higher actuation forces were needed. If a similar space limitation existed but a higher actuation force than would be available using a single piston were needed with only a relatively low fluid pressure source available, the actuator in accordance with the present invention would provide an increased actuation force at that lower fluid pressure. In addition, as illustrated by the alternate embodiment, the actuation force can be further multiplied, as desired, by repeating the described arrangement of the fixed pistons and intermediate movable cylinder walls, thereby increasing the number of actuating surfaces.
- The foregoing discussion and the illustrated embodiments of the invention have been in the context of the use of the actuator in a plastics injection molding machine for controlling the flow of molten plastic material from an injection unit to a mold cavity, to provide increased actuation forces where space is limited or where available fluid pressures are low. It will be apparent to those skilled in the art that various changes and modification can be made without departing from the concepts of the present invention. It is therefore intended to encompass within the appended claims all such changes and modification that fall within the scope of the present invention.
Claims (7)
Priority Applications (10)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US10/246,961 US6719263B1 (en) | 2002-09-20 | 2002-09-20 | Multi-piston valve actuator |
BR0314620-0A BR0314620A (en) | 2002-09-20 | 2003-09-18 | Multi Piston Valve Activator |
JP2004538514A JP2006500528A (en) | 2002-09-20 | 2003-09-18 | Multi-piston valve actuator |
CA002496768A CA2496768C (en) | 2002-09-20 | 2003-09-18 | Multi-piston valve actuator |
AT03770578T ATE357620T1 (en) | 2002-09-20 | 2003-09-18 | MULTI PISTON VALVE ACTUATOR |
PCT/US2003/030798 WO2004027302A1 (en) | 2002-09-20 | 2003-09-18 | Multi-piston valve actuator |
PT03770578T PT1543263E (en) | 2002-09-20 | 2003-09-18 | Multi-piston valve actuator |
AU2003279069A AU2003279069B2 (en) | 2002-09-20 | 2003-09-18 | Multi-piston valve actuator |
DE60312705T DE60312705T2 (en) | 2002-09-20 | 2003-09-18 | MORE PISTON VALVE ACTUATOR |
EP03770578A EP1543263B1 (en) | 2002-09-20 | 2003-09-18 | Multi-piston valve actuator |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US10/246,961 US6719263B1 (en) | 2002-09-20 | 2002-09-20 | Multi-piston valve actuator |
Publications (2)
Publication Number | Publication Date |
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US20040056225A1 true US20040056225A1 (en) | 2004-03-25 |
US6719263B1 US6719263B1 (en) | 2004-04-13 |
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US10/246,961 Expired - Lifetime US6719263B1 (en) | 2002-09-20 | 2002-09-20 | Multi-piston valve actuator |
Country Status (10)
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---|---|
US (1) | US6719263B1 (en) |
EP (1) | EP1543263B1 (en) |
JP (1) | JP2006500528A (en) |
AT (1) | ATE357620T1 (en) |
AU (1) | AU2003279069B2 (en) |
BR (1) | BR0314620A (en) |
CA (1) | CA2496768C (en) |
DE (1) | DE60312705T2 (en) |
PT (1) | PT1543263E (en) |
WO (1) | WO2004027302A1 (en) |
Cited By (7)
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US20110042603A1 (en) * | 2009-03-06 | 2011-02-24 | Gerhard Loeffler | Flow-control valve for heating/cooling system |
US20130287886A1 (en) * | 2011-01-12 | 2013-10-31 | Mht Mold & Hotrunner Technology Ag | Injection-Moulding Machine |
US20160052184A1 (en) * | 2013-05-28 | 2016-02-25 | Synventive Molding Solutions, Inc. | End of stroke actuator bleed |
WO2016053478A1 (en) * | 2014-08-11 | 2016-04-07 | Synventive Molding Solutions, Inc. | Actuator apparatus and method enabling multiple piston velocities |
US9993953B2 (en) | 2014-12-11 | 2018-06-12 | Syneventive Molding Solutions, Inc. | Actuator apparatus and method enabling multiple piston velocities |
US10422439B2 (en) * | 2015-11-09 | 2019-09-24 | Kmatic Aps | Multifunctional sanitary valve and method of operating such |
GB2561716B (en) * | 2015-09-01 | 2022-10-19 | Fulcrum Bioenergy Inc | Fuels and fuel additives that have high biogenic content derived from renewable organic feedstock |
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US20070250258A1 (en) * | 2005-07-21 | 2007-10-25 | Iimap, Llc | Method and System for Accurate Reconstruction of Mileage Reports |
IT201900013278A1 (en) | 2019-07-30 | 2021-01-30 | Inglass Spa | "Method for operating a fluid actuator" |
IT202100005306A1 (en) | 2021-03-08 | 2022-09-08 | Inglass Spa | "METHOD AND SYSTEM FOR ACTIVATING A FLUID ACTUATOR" |
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US2675204A (en) * | 1948-09-30 | 1954-04-13 | Johnson Clarence | Noncorrodible fluid-pressure operated valve |
US4335744A (en) * | 1980-04-07 | 1982-06-22 | Control Components, Inc. | Quiet safety relief valve |
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US3752040A (en) | 1971-10-26 | 1973-08-14 | J Pawloski | Multi piston power pack unit for fluid actuated tool |
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US4872360A (en) * | 1988-05-12 | 1989-10-10 | Lew Hyok S | Moving cylinder actuator |
JPH04320820A (en) | 1991-04-19 | 1992-11-11 | Victor Co Of Japan Ltd | Mold device for injection molding |
DE4206318C2 (en) | 1992-02-29 | 1994-06-16 | Otto Maenner | Multiple needle valve nozzle for injection molds |
DE4206319C2 (en) | 1992-02-29 | 1994-04-28 | Otto Maenner | Needle valve with piston drive |
US5191825A (en) | 1992-06-12 | 1993-03-09 | Doben Limited | Low-impact air cylinder |
DE4324275C2 (en) | 1993-07-20 | 1996-05-02 | Incoe Corp | Pneumatic control device for hot runner needle valves for injection molding tools |
DE4405938A1 (en) * | 1994-02-24 | 1995-08-31 | Werner Prof Dr Ing Moeller | Piston cylinder unit for fluid pressure media |
JP2623075B2 (en) | 1995-02-03 | 1997-06-25 | 悦男 安藤 | Fluid cylinder |
US6386508B1 (en) * | 2000-06-05 | 2002-05-14 | D-M-E Company | Actuator having dual piston surfaces |
-
2002
- 2002-09-20 US US10/246,961 patent/US6719263B1/en not_active Expired - Lifetime
-
2003
- 2003-09-18 AT AT03770578T patent/ATE357620T1/en not_active IP Right Cessation
- 2003-09-18 BR BR0314620-0A patent/BR0314620A/en not_active IP Right Cessation
- 2003-09-18 WO PCT/US2003/030798 patent/WO2004027302A1/en active IP Right Grant
- 2003-09-18 JP JP2004538514A patent/JP2006500528A/en active Pending
- 2003-09-18 AU AU2003279069A patent/AU2003279069B2/en not_active Ceased
- 2003-09-18 EP EP03770578A patent/EP1543263B1/en not_active Expired - Lifetime
- 2003-09-18 DE DE60312705T patent/DE60312705T2/en not_active Expired - Lifetime
- 2003-09-18 CA CA002496768A patent/CA2496768C/en not_active Expired - Lifetime
- 2003-09-18 PT PT03770578T patent/PT1543263E/en unknown
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US2675204A (en) * | 1948-09-30 | 1954-04-13 | Johnson Clarence | Noncorrodible fluid-pressure operated valve |
US4335744A (en) * | 1980-04-07 | 1982-06-22 | Control Components, Inc. | Quiet safety relief valve |
Cited By (11)
Publication number | Priority date | Publication date | Assignee | Title |
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US20110042603A1 (en) * | 2009-03-06 | 2011-02-24 | Gerhard Loeffler | Flow-control valve for heating/cooling system |
US8231102B2 (en) * | 2009-03-06 | 2012-07-31 | F. W. Oventrop Gmbh & Co. Kg | Flow-control valve for heating/cooling system |
US20130287886A1 (en) * | 2011-01-12 | 2013-10-31 | Mht Mold & Hotrunner Technology Ag | Injection-Moulding Machine |
US9296138B2 (en) * | 2011-01-12 | 2016-03-29 | Mht Mold & Hotrunner Technology Ag | Injection-moulding machine |
US20160052184A1 (en) * | 2013-05-28 | 2016-02-25 | Synventive Molding Solutions, Inc. | End of stroke actuator bleed |
US10052801B2 (en) * | 2013-05-28 | 2018-08-21 | Synventive Molding Solutions, Inc. | End of stroke actuator bleed |
WO2016053478A1 (en) * | 2014-08-11 | 2016-04-07 | Synventive Molding Solutions, Inc. | Actuator apparatus and method enabling multiple piston velocities |
US10414079B2 (en) | 2014-08-11 | 2019-09-17 | Synventive Molding Solutions, Inc. | Actuator apparatus and method enabling multiple piston velocities |
US9993953B2 (en) | 2014-12-11 | 2018-06-12 | Syneventive Molding Solutions, Inc. | Actuator apparatus and method enabling multiple piston velocities |
GB2561716B (en) * | 2015-09-01 | 2022-10-19 | Fulcrum Bioenergy Inc | Fuels and fuel additives that have high biogenic content derived from renewable organic feedstock |
US10422439B2 (en) * | 2015-11-09 | 2019-09-24 | Kmatic Aps | Multifunctional sanitary valve and method of operating such |
Also Published As
Publication number | Publication date |
---|---|
CA2496768C (en) | 2009-05-19 |
CA2496768A1 (en) | 2004-04-01 |
EP1543263A1 (en) | 2005-06-22 |
PT1543263E (en) | 2007-05-31 |
AU2003279069B2 (en) | 2006-08-24 |
EP1543263B1 (en) | 2007-03-21 |
DE60312705D1 (en) | 2007-05-03 |
JP2006500528A (en) | 2006-01-05 |
EP1543263A4 (en) | 2006-02-01 |
ATE357620T1 (en) | 2007-04-15 |
US6719263B1 (en) | 2004-04-13 |
AU2003279069A1 (en) | 2004-04-08 |
WO2004027302A1 (en) | 2004-04-01 |
BR0314620A (en) | 2005-07-26 |
DE60312705T2 (en) | 2007-12-06 |
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