REMOTELY MOUNTED ELECTRIC MOTOR DRIVING A VALVE PIN IN AN INJECTION MOLDING APPARATUS

Abstract

An injection molding apparatus comprising a valve comprised of: an actuator having a rotor interconnected to a distal end of an elongated shaft adapted to drivably transmit rotational motion of the rotor to rotational motion of the shaft, the shaft being interconnected at a proximal end to a converter adapted to transmit rotational motion of the shaft directly to driven linear motion of a valve pin, the shaft having a length or configuration selected such that the actuator is mountable on the apparatus in a position or disposition that is isolated or insulated from significant or substantial exposure to or transmission of heat from a heated manifold.

Claims

1. An injection molding apparatus comprising an injection molding machine (IMM), a heated manifold (60) having a distribution channel (120) into which injection fluid (9), a mold (70) having a cavity (80) communicating with a fluid delivery channel (130) that receives injection fluid (9) from the distribution channel (120), the fluid delivery channel (130) delivering fluid (9) at a downstream end to a gate (110) that communicates with the cavity (80), the gate (110) being controllably opened and closed to control flow of the fluid (9) into the cavity (80) during the course of an injection cycle, the apparatus including a valve (50) comprised of: an actuator (200) having a rotor (12) rotatably driven (R1) at a rotor speed (R1s), the rotor (12) being interconnected to a distal end (22) of an elongated shaft (20) and adapted to drivably transmit rotational motion (R1) of the rotor to rotational motion (R2) of the elongated shaft (20) for rotation at a shaft speed (R2s), the actuator (200) being mounted to one or the other of a top clamp plate (140) or the injection molding machine (IMM), the elongated shaft (20) being interconnected at a proximal end (24) to a converter (40), the converter (40) being adapted to transmit rotational motion (R2) of the elongated shaft (20) directly to driven linear motion (A) of a linear drive member (26), the linear drive member (26) being interconnected to a valve pin (100) arranged within the fluid delivery channel for upstream and downstream movement along a linear path of travel (A) between gate closed and gate open positions via the driven linear motion (A) of the linear drive member (26), the elongated shaft (20) having a shaft axis (DA), a length or configuration (LC) selected and adapted such that the actuator (200) is mountable on the apparatus in a position or disposition that is isolated, separated or insulated from significant or substantial exposure to or transmission of heat from the heated manifold (60) through air or metal to metal contact between the heated manifold (60) and the actuator (200).

2. The apparatus of claim 1 wherein the valve (50) includes a torque increasing or rotational speed reducing device (11) interconnected to and between the rotor (12) and the elongated shaft (20) in an arrangement wherein rotational movement (R1) of the rotor is transmitted to rotational movement (R2) of the elongated shaft (20).

3. An apparatus according to claim 2 wherein the torque increasing or rotational speed reducing device (11) is adapted to convert the rotational speed (R1s) and a torque (T1) generated by the rotor (12) to a different rotational speed (R2s) and a different torque (T2) generated by the elongated shaft (20).

4. An apparatus according to claim 2 wherein the torque increasing or rotational speed reducing device (11) is adapted to convert the rotational speed (R1s) and a torque (T1) generated by the rotor (12) to a lower rotational speed (R2s) and a higher torque (T2) generated by the elongated shaft (20).

5. An apparatus according to claim 1 wherein the actuator (200) is controllably rotationally (R1) drivable to controllably drive the valve pin (100) linearly (A) via the interconnection of the rotor (12) to the elongated shaft (20) and the interconnection of the elongated shaft to the converter (40) and the interconnection of the converter (40) to the linear drive member (26) and the interconnection of the linear drive member (26) to the valve pin (100).

6. An apparatus according to claim 1 wherein the shaft (20) is rigid or comprised of a rigid metal material.

7. An apparatus according to claim 1 further including a position sensor (PS) that senses position of the valve pin (100, 130) or the linear drive member (26).

8. An apparatus according to claim 7 wherein the position sensor (PS) sends a signal indicative of the position of the valve pin to a controller (800) that uses the signal in a program having instructions that use the position of the valve pin (100, 130) or linear drive member (26) to control opening and closing of the gate (110) by the pin (100, 1300 or control rate of flow of injection fluid (9) through the gate (110) via controlled positioning of a tip end (100t) of the pin (100, 130) relative to the gate.

9. An apparatus according to claim 8 wherein the program includes instructions that instruct the actuator (10, 200) to drive the valve pin (100, 130), based on the use of the signal indicative of position, from a gate closed position upstream at a reduced velocity relative to a maximum velocity over the course of a selected path of travel between the gate closed position and a full upstream valve pin position.

10. An apparatus according to claim 8 wherein the program includes instructions that instruct the actuator (10, 200) to drive the valve pin (100, 130) based on the use of the signal indicative of position, downstream from a selected position upstream of the gate closed position at a reduced velocity relative to a maximum velocity over the course of a selected path of travel between the selected position upstream and the gate closed position.

11. An apparatus according to claim 7 wherein the position sensor (PS) comprises a Hall Effect Sensor that senses a magnetic field generator or magnet (M) that travels linearly together with the linear drive member (26) or valve pin (100, 130).

12. An apparatus according to claim 1 wherein the heated manifold (60) is mounted between the upstream top clamp plate (140) and the mold (70), the heated manifold (60) being expandable or translationally movable relative to the top clamp plate (140) or the injection molding machine.

13. An apparatus according to claim 1 wherein the converter (40) is mounted to the apparatus such that the converter (40) travels laterally or in a direction along a lateral axis of the shaft (LS) relative to the actuator (200) on heating of the manifold (60) or upon assembly of the apparatus, the elongated shaft (20) being interconnected to the converter (40) or the actuator (200) by one or more connectors (15, 30) that are adapted to enable lateral movement (LS) between the converter (40) and the actuator (200) while maintaining a rotational interconnection between the elongated shaft and the converter.

14. An apparatus according to claim 13 wherein the one or more connectors (15, 30) include a spline device (202s, 32s, 17s, 42s).

15. An apparatus according to claim 1 wherein the converter is mounted to the apparatus such that the converter (40) travels in a direction radially or front to back (FBS), axially (AS) or along another direction relative to the actuator (200) on heating of the manifold (60) or upon assembly of the apparatus, the elongated shaft (20) being interconnected to the converter (40) or the actuator (200) by one or more connectors (15, 30) that are adapted to enable translational movement of the converter (40) in a radial or front to back (FBS), or axial (AS) direction of the converter (40) and maintain a rotational interconnection of the elongated shaft (20) to the actuator (200) and to the converter (40).

16. An apparatus according to claim 15 wherein the one or more connectors (15, 30) include one or more hinges (15h1, 15h2) that are pivotably interconnected in an arrangement that enables the one or more hinges (15h1, 15h2) to co rotate with each other and simultaneously pivot relative to each other.

17. An apparatus according to claim 1 wherein the elongated shaft (20) is interconnected to the converter (40) in an arrangement wherein the shaft axis (DA) is disposed generally radially normal to the linear path of travel (A) of the valve pin.

18. An apparatus according to claim 1 wherein the valve pin (100) is mounted to the manifold (60).

19. An apparatus according to claim 1 wherein the converter (40) is mounted to the heated manifold (60) such that the converter (40) travels together with movement of the heated manifold (60) and the actuator (200) is mounted to the top clamp plate (140), the top clamp plate (140) and the heated manifold moving relative to each other on heating of the heated manifold (60) to operating temperature.

20. An apparatus according to claim 1 wherein the converter (40) and the actuator (200) are mounted to the top clamp plate (140), the top clamp plate (140) and the heated manifold (60) moving relative to each other on heating of the heated manifold to operating temperature.

21. An apparatus according to claim 1 wherein the converter (40) is mounted to the heated manifold (60) in an arrangement wherein the converter (40) and converter housing (40h) receive heat generated by the heated manifold (60), the apparatus including a cooling device (300) comprised of a heat conductive plate (300p) having a first downstream facing heat conductive undersurface (300s2) mounted onto or into heat conductive engagement with a heat conductive surface (40ss) of the converter (40), the cooling device including heat conductive wings or projections (300w) that laterally extend from the plate (300p) having surfaces (300s1) adapted to engage a heat conductive surface (140ps) of the top clamp plate (140, 140p), the heat conductive plate (300p) transmitting heat received by the converter (40) and the housing (40h) from the heat conductive surface (40ss) through the wings or projections (300w) to the top clamp plate (140, 140p).

22. An apparatus according to claim 21 wherein the wings or projections (300w) of the cooling device comprise a resilient or resiliently deformable spring, the clamp plate (140, 140p), cooling device (300), mold, manifold and converter (40) being adapted such that when assembled together in an operative arrangement, the wings or projections 300w are spring loaded urging the upstream facing surfaces (300s) into compressed thermally conductive engagement with a complementary surface (140ps) of the top clamp plate (140, 140p).

23. An apparatus according to claim 1 wherein the elongated shaft (20) is interconnected between the actuator (200) and the converter (40) by a movement accommodation connector (15, 30) adapted to enable translational movement of the converter (40) relative to the actuator (200) and to simultaneously interconnect the actuator (200), the elongated shaft (20) and the converter (40) such that the elongated shaft (20) and the converter (40) are rotatably drivable by the actuator (200).

24. An apparatus according to claim 23 wherein the movement accommodation connector (15, 30) is adapted to enable translational movement of the converter (40) in three axial directions normal to each other or in three dimensions.

25. An apparatus according to claim 23 wherein the movement accommodation connector (15, 30) comprises one or more of a spline connector, a universal joint, a flexible connector and a socket connector.

26. A method of performing an injection molding cycle comprising injecting an injection fluid into a cavity of a mold employing an apparatus according to claim 1.

27. An injection molding apparatus comprised of an injection molding machine (IMM), a heated manifold (60) having a distribution channel (120) into which injection fluid (9), a mold (70) having a cavity (80) communicating with a fluid delivery channel (130) that receives injection fluid (9) from the distribution channel (120), the fluid delivery channel (130) delivering fluid (9) at a downstream end to a gate (110) that communicates with the cavity (80), the gate (110) being controllably opened and closed to control flow of the fluid (9) into the cavity (80) during the course of an injection cycle, a valve assembly (50) comprising: an actuator (200) having a rotor (12) rotatably driven (R1) at a rotor speed (R1s) and rotor torque (T1), the rotor (12) being interconnected to a distal end (22) of an elongated shaft (20) and adapted to drivably transmit rotational motion (R1) of the rotor to rotational motion (R2) of the elongated shaft (20) for rotation at a shaft speed (R2s) and shaft torque (T2) different from the rotor speed (R1s) and rotor torque (T1), the elongated shaft (20) being interconnected at a proximal end (24) to a converter (40), the converter (40) being adapted to convert rotational motion (R2) of the elongated shaft (20) to driven linear motion (A) of a linear drive member (26), the linear drive member (26) being interconnected to a valve pin (100) arranged within the fluid delivery channel for upstream and downstream movement along a linear path of travel (A) between gate closed and gate open positions, the elongated shaft (20) being rigid and having a shaft axis (DA) and a fixed length or configuration (LC) selected such that the actuator (200) is mountable on the apparatus in a position or disposition that is isolated or insulated from significant or substantial exposure to or transmission of heat from the heated manifold through air or through metal to metal contacts between the heated manifold (60) and the actuator (200).

28. The apparatus of claim 27 wherein the valve (50) includes a torque increasing or rotational speed reducing device (11) interconnected to and between the rotor (12) and the elongated shaft (20) in an arrangement wherein rotational movement (R1) of the rotor is transmitted to rotational movement (R2) of the elongated shaft (20).

29. The apparatus of claim 28 wherein the torque increasing or rotational speed reducing device (11) is adapted to convert the rotational speed (R1s) and a torque (T1) generated by the rotor (12) to a different rotational speed (R2s) and a different torque (T2) generated by the elongated shaft (20).

30. The apparatus of claim 28 wherein the torque increasing or rotational speed reducing device (11) is adapted to convert the rotational speed (R1s) and a torque (T1) generated by the rotor (12) to a lower rotational speed (R2s) and a higher torque (T2) generated by the elongated shaft (20).

31. The apparatus of claim 1 wherein the actuator (200) is controllably rotationally (R1) drivable to controllably drive the valve pin (100) linearly (A) via the interconnection of the rotor (12) to the elongated shaft (20) and the interconnection of the elongated shaft to the converter (40) and the interconnection of the converter (40) to the linear drive member (26) and the interconnection of the linear drive member (26) to the valve pin (100).

32. An apparatus according to claim 27 wherein the shaft (20) is comprised of a rigid metal material.

33. An apparatus according to claim 27 further including a position sensor (PS) that senses position of the valve pin (100, 130) or the linear drive member (26).

34. An apparatus according to claim 33 wherein the position sensor (PS) sends a signal indicative of the position of the valve pin to a controller (800) that uses the signal in a program having instructions that use the position of the valve pin (100, 130) or linear drive member (26) to control opening and closing of the gate (110) by the pin (100, 1300 or control rate of flow of injection fluid (9) through the gate (110) via controlled positioning of a tip end (100t) of the pin (100, 130) relative to the gate.

35. An apparatus according to claim 34 wherein the program includes instructions that instruct the actuator (10, 200) to drive the valve pin (100, 130), based on the use of the signal indicative of position, from a gate closed position upstream at a reduced velocity relative to a maximum velocity over the course of a selected path of travel between the gate closed position and a full upstream valve pin position.

36. An apparatus according to claim 34 wherein the program includes instructions that instruct the actuator (10, 200) to drive the valve pin (100, 130) based on the use of the signal indicative of position, downstream from a selected position upstream of the gate closed position at a reduced velocity relative to a maximum velocity over the course of a selected path of travel between the selected position upstream and the gate closed position.

37. An apparatus according to claim 33 wherein the position sensor (PS) comprises a Hall Effect Sensor that senses a magnetic field generator or magnet (M) that travels linearly together with the linear drive member (26) or valve pin (100, 130).

38. An apparatus according to claim 27 wherein the heated manifold (60) is mounted between an upstream top clamp plate (140) and the mold (70), the actuator (10, 200) being mounted to one or the other of the top clamp plate (140) or the injection molding machine (IMM), the converter (40) being housed in a housing (40h) that is spaced apart from the actuator (10, 200) and connected via the elongated shaft (20).

39. An apparatus according to claim 27 wherein the housing (40h) is mounted to the heated manifold (60).

Description

BRIEF DESCRIPTION DRAWINGS

[0096] FIG. 1 is a side sectional schematic view of an injection molding system showing electric actuators mounted on a top clamp plate in extended spaced apart interconnected relationship to a linear drive converter device and valve pins driven by the actuator, the linear drive converter device also being mounted to the top clamp plate.

[0097] FIG. 2. is a fragmentary enlarged detail side view of a distal end of an elongated rotatably driven shaft component of an actuator as shown in FIG. 1 also showing in schematic section a beveled gear interconnection of the elongated shaft to a linearly driven member that is interconnected to a valve pin for controlled linear drive.

[0098] FIG. 3 is a cross sectional plan view of a pin connector along lines 3-3 of FIG. 2.

[0099] FIG. 4 is a side view similar to FIG. 2 showing an alternative embodiment of a geared interconnection between the enlongated shaft and the valve pin components of the system.

[0100] FIG. 5 is a fragmentary side sectional view similar to FIG. 1 showing an alternate arrangement for mounting the linear drive converter device to the heated manifold.

[0101] FIG. 6 is a fragmentary side schematic sectional view similar to FIG. 1 showing an alternate embodiment where the linear drive converter device is mounted to the heated manifold and cooled by a convection cooling member in contact with the top clamp plate and drive converter housing.

[0102] FIG. 7 is a fragmentary sectional view similar to FIG. 5 showing an alternative rack and pinion linear converter device mounted to the heated manifold.

[0103] FIG. 7A is a fragmentary section view similar to FIG. 7 showing in schematic detail the linkages and connections between the elongated rigid shaft component and the motor and the converter.

[0104] FIG. 8 is a fragmentary perspective view of the rack and pinion subassembly of FIG. 7 showing three axial directions or axes (LS, AS, FBS) in which the converter can move translationally relative to the actuator.

[0105] FIG. 9 is an enlarged detail of the rack and pinion device of the FIG. 7 system mounted to a water cooled mount intermediate the heated manifold and rack and pinion device.

[0106] FIG. 10 is a side schematic view of a generic valve in an apparatus according to the invention showing an electrically powered actuator interconnected first downstream to a rotational speed reducing device such as a gear box.

[0107] FIGS. 11A, 11B, 11C and 11D are generic illustrations of alternative rotational speed reducing or torque increasing devices that can be used in conjunction with an electrically powered actuator in an apparatus according to the invention.

DETAILED DESCRIPTION

[0108] FIG. 1 shows a generic system or apparatus 5 according to the invention comprising an injection molding machine IMM that feeds a selected fluid 9 into an inlet 9a that in turns feeds into a distribution channel 120 of a heat manifold 60. As shown the manifold is disposed between an upstream mounted top clamp plate 140 and a downstream mounted mold 70 that forms a cavity 80 in which the part to be molded is formed from injection fluid 9 that is routed into the cavity via downstream gate 110 that communicates with nozzle channel 130 in which valve pin 100 is disposed for controlled upstream and downstream reciprocal movement along linear axis A between gate open and gate closed positions, the gate open position shown in FIG. 1 with respect to nozzle 132 and the gate open position shown with respect to nozzle 134.

[0109] As shown in FIGS. 1, 2, a valve 50 is provided for controlling movement of the valve pin 100, the valve 50 comprising an electrically powered actuator 200 having, typically an electric motor having a rotor 12 rotatably driven by an electrically powered coil such as disclosed in U.S. Pat. No. 6,294,122 the disclosure of which is incorporated by reference as if fully set forth herein. The valve 50 includes a rigid, typically comprised of metal such as steel, elongated shaft 20 that is coupled to the rotating rotor 12 via coupling 15 at an upstream end 22 of the shaft 20 and a rotary to linear converter 40 that is coupled to a downstream end 24 of the elongated shaft 20 by coupling 30 such as a universal joint. The elongated and rigid configuration of the shaft 20 is selected so that the motor 200 and rotor 12 is necessarily disposed and mounted in a location or position that is isolated or insulated from transmission of heat from the heated manifold 60. The shaft 20 is selected to be comprised of a rigid metal material so that energy and torque force R2s derived from driven rotation R2 of the shaft 20 is reliably transmitted from the remotely mounted motor 200 to the rotary to linear converter assembly 40.

[0110] The converter 40 comprises a housing 40h that houses a rotary to linear device. In the embodiment shown in FIG. 1, the rotary to linear device comprises a bevel gear 42g that has a gear shaft 42 coupled to the elongated shaft 20 and mounted to housing 40h by bearings 42b for rotation R2 in unison with the shaft 20, rotation R2 of the gear shaft 42 in turn drivably rotates the bevel gear 42g. Bevel gear 42g is meshed with complementary bevel gear 44g that is rotatably mounted to the housing 40h via screw shaft 44 that is rotatably mounted to housing 40h via bearings 44b. As shown, the bevel gears 42g, 44g and their respective shafts 42, 44 are configured and arranged to transmit rotation around elongated shaft axis DA to a valve pin drive axis A that is non coaxial with axis DA. Driven rotation of bevel gear 42g results in driven rotation of screw shaft 44 that is screwably engaged with linearly travelling nut 26 which is in turn coupled to the head 100h of valve pin 100. Thus driven rotation of screw shaft 44 results in rotation of screw threads 44s that in turn results in linear driven movement along axis A of nut 26 and its interconnected valve pin 100.

[0111] When the system 5 is assembled and the heated manifold 60 is heated to a typical high operating temperature, the manifold 60 body will tend to physically expand in size thus causing translational movement of the body of the manifold 60 relative to the top clamp plate 140 and the mold body 70. Similarly components of the valve assembly such as the converter housing 40h and valve pin 100 that may be mounted to the heated manifold will translationally move in several directions such as laterally LS, axially AS and from front to back FBS, FIG. 8, namely in a direction in and out of the page as shown in FIGS. 4-7, while the motor 200 is stationarily mounted on the top clamp plate 140 or to another stationary structure of the system 5. To accommodate such in and out or front to back FBS movement, the joints 15, 30 are adapted to enable the shaft 20 to pivot in or along the FBS direction or axis together with movement of the housing 40 or motor 200 along the same FBS direction or axis. Joints 15, 30 that comprise a universal joint comprised of hinges such as hinges 15h1, 15h2 that may be pivotably connected to each other by a cross shaft 15cs. The cross shaft 15cs connections connects the hinge such that the two hinges 15h1, 15h2 can co rotate with each other along their respective rotational axes and simultaneously also to pivot in the FBS axis or direction relative to each other around the axis of the connecting cross shaft 15cs while still continuing to co rotate when the rigid shaft 20 is being rotatably driven.

[0112] Thus any components that may be mounted to the manifold 60 such as the converter housing 40 or valve pin 100 may translationally move relative to the motor 200 when the system is brought to operating temperature.

[0113] To accommodate such movement LS, FIGS. 7A, 8 and avoid breakage of the rigid shaft 20 or the connectors 15, 30, the connectors or couplings 15, 30 preferably include lateral movement connectors such as female 202s, 32s and complementary interconnected male 17s, 42s splines that enable and accommodate lateral movement LS of the converter housing 40h and valve pin relative to the stationary mounted actuator or motor 200 when the converter 40 is mounted to the heated manifold 60 as shown in FIGS. 5, 6, 7, 7A. The same or similar lateral movement connectors 202s, 32s, 17s, 42s also enable and accommodate any lateral movement LS, R of the converter housing 40h that may occur when the converter 40 is mounted to the top clamp plate as shown in FIGS. 1, 2, 4. Such lateral movement connectors 15, 30 are typically adapted to enable lateral sliding LS of the pivotably connected components of the connectors 15, 30 relative to each other, such via slidably and rotatably interconnected hinges 15h1 and 15h2 which are respectively rigidly connected to the rotatable rigid shaft 20 and motor rotor 12 thus enabling the shaft 20 and rotor 12 to move laterally LS relative to each other.

[0114] Couplings 15, 30 can comprise any flexible connection mechanism or connector such as as a spline, socket, universal joint or other flexible coupling. The flexible connection mechanism or connector 15, 30 further enables and accommodates translational movement of the converter housing 40h relative to the top clamp plate 140 and motor 200 in the axial direction AS and in a front to back, in and out or radial direction FBS, FIGS. 7A, 8 such axial and front to back movement occurring also when the heated manifold 60 expands upon being heated up to a typical high operating temperature. Where the connectors comprise universal joints, the hinges of the joints 15, 30 such as hinges 15h1, 15h2 enable and accommodate such axial and front to back movement by being typically pivotably connected to each other by a cross shaft 15cs. The cross shaft 15cs connections connects the hinge such that the two hinges 15h1, 15h2 can co rotate with each other along their respective rotational axes and also to pivot relative to each other around the axis of the connecting cross shaft 15cs while still continuing to co rotate when the rigid shaft 20 is being rotatably driven.

[0115] As shown in FIGS. 2, 3, 4 the head 100h of pin 100 is coupled to the downstream coupling end 26a of shaft 26. The coupling 26a and head 100h are adapted to enable the pin 100 to travel radially R relative to travel axis A to allow for radial movement R of pin 100 that can occur upon thermal expansion of manifold 60 in which pin 100 is mounted downstream. Such a coupling can comprise a configuration as disclosed in U.S. Pat. No. 9,492,960, disclosure of which is incorporated by reference as if fully set forth herein.

[0116] FIG. 4 shows an alternative embodiment of the FIGS. 1, 2 embodiment where the gear shaft 44 comprises a nut 44n that is rotatably driven and screwably engaged with a linearly moving screw 26 that is in turn coupled downstream 26a to the head 100h of the valve pin 100.

[0117] In the FIGS. 1-4 embodiments, the rotary to linear converter 40 is mounted to the top clamp plate 140 such that a highly heat conductive surface 40s of the housing 40 (which itself is typically comprised of a highly heat conductive material such as metal, steel or the like) is compressibly engaged against a surface 140s of the top clamp plate 140 which is also typically comprised of a highly heat conductive material such as metal, steel or the like. The compressed engagement of surfaces 40s and 140s with each other enables heat to be readily transmitted from housing 40h to the cooled or cooler body of the top clamp plate 140. The top clamp plate 140 is typically cooled via water that flows through cooling channels 145 bored within the top clamp plate 140.

[0118] FIG. 5 shows an alternative embodiment of the FIGS. 1-4 embodiments where the electrically powered actuator 200 is mounted on side surface 140ss of the top clamp plate 140 and the elongated shaft 20 and converter 40 are mounted within apertures or channels 140us, 140uc formed on the interior or underside of the top clamp plate. Again, the top clamp plate 140 is typically cooled via water that flows through cooling channels 145 bored within the top clamp plate 140. In the FIG. 5 embodiment, the converter 40 is mounted to the heated manifold 60 via bolts 58 and springs 56. The bolts 58 cause the converter housing 40h and its interconnected valve pin 100to travel radially R together with radial expansion or travel of the heated manifold thus minimizing the necessity for prevention of pin decoupling or pin deformation due to radial expansion of the heated manifold 60. The springs 56 are resiliently compressibly engaged between an upstream surface 60u of the manifold 60 and a downstream surface 40hd of the housing 40h to cause an upstream facing heat conductive surface 40s of the housing 40 to compressibly engage with a downstream facing heat conductive surface 140s of the cooled top clamp plate thus working to cause heat from the manifold 60 that is transmitted to housing 40 to be transmitted from housing 40 to the cooled top clamp plate 140 thus cooling the converter housing 40 and the converter components 40c generally.

[0119] FIG. 6 shows another embodiment where the housing 40 is mounted to the manifold 60 via bolts 58 and the electric actuator 200 is adapted and arranged to be mounted in a non-coaxial arrangement as shown along a side surface 140ss of the top clamp plate 140. As shown the converter 40 is mounted within an enclosed cut out or aperture 140a formed within the body of the top clamp plate 140 with the aperture 140a being covered or enclosed by an upstream or top cover or plate 140p, the cover or plate 140p being comprised of a highly heat conductive material such as metal, steel or the like and being readily attachable to and detachable from the top clamp plate 140 for ready insertion and removal of the converter 40 to and from the aperture 140a. A cooling device typically comprising a highly heat conductive resiliently compressible spring 300 is disposed between an upstream facing surface 40ss of the housing 40 and a downstream facing surface 140ps of the cover 140p. The top clamp plate 140 is comprised of the cover 140p which is cooled together with the top clamp plate 140 via heat conductive contact between the top clamp plate 140 and the removable cover 140p. The spring 300 is compressed so that an upstream facing surface of the spring 300s1 makes compressed heat conductive contact with a downstream facing surface 140ps of the cover 140p and a downstream facing surface of the spring 300s2 makes compressed heat conductive contact with an upstream facing surface 40ss of the convertor housing 40h thus causing heat from the housing 40h to be conducted to the top clamp plate cover 140p and to the top clamp plate 140 generally. The top clamp plate 140 is typically cooled via water flow that is injected through cooling channels 140c provided within the body of the plate 140.

[0120] As shown in FIG. 7 the cooling device 300 is configured such that it comprises a plate 300p having a first downstream facing heat conductive undersurface 300s2 for mounting onto and into heat conductive engagement with the upstream surface 40ss of the heat conductive converter housing 40. The cooling device includes a pair of laterally and upstream extending wings or projections 300w that laterally extend to a distal end 300de that has opposing upstream facing surfaces 300s1 that engage the opposing downstream facing body surface 140ps of the top clamp plate cover 140ps. The projections 300w preferably comprise a resilient spring. The clamp plate 140, 140p, the cooling device 300, the mold, the manifold, the converter 40 are all configured, adapted, mounted or arranged such when assembled together in an operative arrangement, the wings or projections 300w are spring loaded urging the upstream facing surfaces 300s into compressed thermally conductive engagement with the top clamp plate 140, 140p.

[0121] FIG. 7 shows an alternative embodiment where the actuator 200 is mounted on a side surface 140ss of the top clamp plate 140 and the elongated or extended shaft 20 is disposed within an aperture 140aa formed in a downstream end of the top clamp plate 140. The converter 40 is mounted to the manifold 60 via intermediate mounts 40m, 40mm and bolts 58. In the FIGS. 7, 8 embodiment the converter 40 comprises a rack 26p and pinion 42g assembly where the gear of the pinion 26p is drivably rotatable R2 to cause, via engagement with teeth of the rack 26p, linear upstream downstream A movement of the rack 26p and its interconnected valve pin 100. As shown in FIG. 9, an intermediate cooling mount 40mc having cooling channels 40mcc is preferably disposed in heat conductive communication with housing 40 and is disposed and arranged between the housing 40h and the heated manifold 60 to effect such cooling.

[0122] FIG. 8 shows in greater detail an embodiment of a rack 26p and pinion 42g type of rotary to linear conversion device 40 with the valve pin 100 attached to and linearly drivable by driven linear axial A movement of the rack 26p.

[0123] As shown in FIG. 8 the converter housing 40 can move translationally in any of three dimensions or directions AS (axially), LS (laterally) and front to back, radial or in and out (FBS). The same is true of the converter housings 40 described herein with regard to all other embodiments. Most preferably in all embodiments described herein, the elongated shaft (20) is interconnected between the actuator (200) and the converter (40) by a movement accommodation connector (15, 30) that is adapted to enable translational movement of the converter (40) relative to the actuator (200) and to simultaneously interconnect the actuator (200), the elongated shaft (20) and the converter (40) such that the elongated shaft (20) and the converter (40) are rotatably drivable by the actuator (200). The movement accommodation connector (15, 30) is preferably adapted to enable translational movement of the converter (40) in three axial directions normal to each other or in three dimensions, AS, FBS, LS. The movement accommodation connector (15, 30) preferably comprises one or more of a spline connector (32s, 42s, 202s, 17s) such as shown in FIGS. 2, 7A, a universal joint 15, 30 comprised of hinges such as hinges 15h1, 15h2 and a cross shaft 15cs, a flexible connector and a socket connector.

[0124] In an embodiment shown in schematic in FIG. 10, the actuator 200 comprises a rotational speed changing or torque changing assembly 11 connected between the rotor 12 of the electrically powered motor 10 and the elongated shaft 20. The assembly 11 is interconnected to the rotor 12 in an arrangement that converts and transmits the rotational speed R1s and torque T1 of the rotor 12 to an intermediate shaft 16 that is rotated by the assembly 11 at a different, typically lower, rotational speed R2s and torque T2, typically higher, relative to the speed R1s and torque T1 of the motor or rotatably driven rotor 12. As shown in FIG. 10 an upstream end 16u of the intermediate shaft 16 is interconnected to the downstream end 22 of the rigid elongated shaft 20 in an arrangement where the shaft 20 is rotated at the same rotational speed R2 as the intermediate shaft 16. In another embodiment (not shown) the downstream end 22 of the elongated shaft 20 could be connected to the assembly 11 directly. Such torque increasing assemblies 11, 500, 502, 504, FIGS. 10, 11A-11D, are preferred for use in connection with an electric motor containing actuator 10 where conventional normal sized electric motors that are capable of being mounted in an injection molding environment typically do not have sufficient power to generate torque of high enough degree necessary to drive the rotary to linear conversion device 40 and its interconnected valve pin 100, 130 in a controlled, precise, accurate manner against the high upstream force exerted on the tip end 100t by the high pressure injection fluid flowing through the gate 110.

[0125] The rotational speed changing or torque changing assembly 11 can comprise an assembly 500, 502, 504 such as shown in FIGS. 11A, 11B (worm gear assembly 500), 11C (spur gear assembly 502), 11D (planetary gear assembly 504) where the rotor 12 of the motor 10 is connected to and rotates the highest speed rotating gear or gear tooth containing component 600 of the assembly and the intermediate shaft 16 is connected to and rotated by the lowest speed rotating gear or gear tooth containing component 700 of the assembly to effectively reduce the rotational speed and increase the torque output of the rotor 12 by transmission of lower speed, higher torque rotation of and to the elongated shaft 20. Other assemblies such as helical gear assemblies or belts and pulley arrangements and assemblies 11, 500, 502, 504 can be used to effect such speed changing and torque changing transmission.

[0126] The elongated shaft 20 is adapted to have a length or configuration LC that is selected such that the actuator 200 is mountable on the apparatus 5 in a position or in a disposition relative to the heated manifold 60 such that actuator 200 and electric motor 12 is isolated or insulated from significant or substantial exposure to or transmission of heat from the heated manifold through air or through metal to metal contacts between the heated manifold 60 and the actuator 200.