US 6,430,466 B1Grant

System for controlling clamp pressure in an automatic molding machine

Issue Date:2002-08-06

•19 Claims

•9 Drawing Sheets

Abstract

The present invention provides a apparatus and method for controlling the force and velocity of a piston within the clamp assembly of a injection molding machine. The control unit comprises the following elements: a PI based cascade compensator; an estimator coupled to the clamp assembly and the cascade compensator, wherein the estimator is utilized to estimate the position of the clamp assembly piston; a velocity position controller coupled to the clamp assembly and the estimator, wherein the velocity position controller is adapted to generate a velocity error signal based on the piston velocity signal; and an auto selector coupled to the cascade compensator, wherein the auto selector is adapted to select between the velocity error signal and the force error signal to generate a valve command signal. The present invention additionally employs a method for determining the velocity profile of the piston of a clamp assembly. The method comprises the following steps: determining the maximum displacement x_sof the servo valve; selecting a final velocity v_sof the piston; choosing a ratio α of the piston ramp-down interval to the servo valve displacement “x” during a ramp-up interval, selecting a desired maximum piston velocity (v_max) during the ramp-up interval and a constant speed interval; and determining servo valve displacement x_ufrom simulations or estimate from previous cycles.

Metadata

Assignee

General Electric Company

Inventor

Suresh Baddam Reddy

Application Information

Application Number:US 09/378,958

Filing Date:1999-08-23

Priority Date:1999-08-23

Art Unit:7

Classifications

IPC:

G05B 1302B29C 4500

Field of Search:

700197700200700 32700 33700 37700 73700 8700 44700 45264 403264 405425145425146425149

Patent Drawings (9 sheets)

Description

Background of the Invention

[0002] The present invention relates to the regulation of a clamp assembly in a injection molding machine and, more particularly, to a closed loop system for controlling the pressure of a clamp assembly to optimize production efficiency in an injection molding machine.

[0003] Injection molding machines are used to mass produce plastic parts by automated injection of plastic into a mold that is opened and closed by a clamp assembly. At the end of an injection molding cycle, the clamp assembly is retracted, and the part is ejected. The next cycle is initiated by motion of the clamp from its retracted position to a position where the mold is nearly closed. During the cycle the mold machine should not be subjected to excessive pressure and forces generated by parts left behind in the mold, or incorrect positioning of the mold. In the event that parts are left behind nor incorrectly positioned in the mold the machine must be stopped and the piece removed. This causes production delay which impacts production efficiency.

[0004] More particularly, a typical injection molding process utilizes a injection molding machine 10, illustrated in FIG. 1, wherein plastic pellets (not shown) are melted and forced into a mold 20, by a clamp assembly 113 that opens and closes mold 20 during the mold injection cycle.

[0005] The clamp assembly 113 comprises a hydraulic cylinder which is mechanically coupled to a piston 27. Clamp assembly 113 further comprises a stationary platen 13 which is mechanically affixed to a mold 20, and a moving platen 12, which is coupled to piston 27. Piston 27 is adapted to hydraulically traverse from a clamp closed position to a clamp open position in an injection molding cycle by variable force applied to piston 27. A hydraulic cylinder 11 is movably coupled to piston 27. The variable force applied to piston 27 by the fluid in hydraulic cylinder 11 may be controlled by a control unit 28.

[0006] The injection molding process comprises four successive stages. The first stage called “plastication” comprises steps wherein the plastic pellets are pushed forward from a hopper 17 through a barrel 21 towards a nozzle 14 by a rotating screw 22 while being heated in barrel 21 by electric heater bands 23 surrounding barrel 21. The second stage called “injection,” occurs when the plastic is pushed through nozzle 14 into a mold 20 by clamp assembly 113. The third stage called “packing,” occurs when mold 20 is packed with the molten plastic. The fourth stage called “cooling,” occurs when mold 20 is cooled to solidify the plastic part therein. After the completion of the solidification and cooling stages, piston 27 is retracted and the part is ejected. The injection molding machine 10 is thus ready for the process to be repeated in the next cycle.

[0007] It is desirable to protect the injection mold machine 10 during motion of piston 27 by “smoothing” the response of the clamp assembly cycle during clamp closure of piston 27 so as to prevent damage to the machine from plastic parts, remaining in the mold after having been jammed in mold 20 during the previous cycle. It is also desirable to control the stroke of piston 27 during the injection molding cycle so as to minimize the duration of the clamp cycle.

Brief Summary of the Invention

[0008] The present invention provides an apparatus and method for controlling the force and velocity of a piston within the clamp assembly of a injection molding machine. The control unit comprises the following elements: a cascade compensator, wherein the cascade compensator is adapted to generate a force error signal having lead and lag compensation based on the desired force minus the actual force of the piston; an estimator coupled to the clamp assembly, wherein the estimator is utilized to estimate the position of the servo valve and to generate a corresponding actual force signal; a velocity and position controller coupled to the clamp assembly and the estimator, wherein the velocity and position controller is adapted to generate a velocity error signal based on the piston velocity signal; and an auto selector coupled to the cascade compensator, wherein the auto selector is adapted to select between the velocity error signal and the force error signal so as to generate the valve position command signal.

[0009] The present invention additionally employs a method for determining the velocity profile of the piston of a clamp assembly, wherein the velocity profile having a ramp-up interval, a constant speed interval, ramp-down interval; and a final touchdown interval. The method comprises the following steps: determining the maximum displacement x_fof the servo valve; selecting a final touch down velocity v_sof the piston; choosing a ratio α of the piston ramp-down interval to the servo valve displacement “x_v” during the ramp-up interval, selecting a desired maximum piston velocity (v_max) during the ramp-up interval and constant speed interval; and determining servo valve displacement x_ufrom simulations or estimate from previous cycles.

Brief Description of the Drawings

[0010] FIG. 1 is a prior art illustration of an injection molding machine;

[0011] FIG. 2 is a functional block diagram of the piston portion of the clamp assembly of FIG. 1;

[0012] FIG. 3 is a functional block diagram of the clamp assembly and control unit of the present invention;

[0013] FIG. 4 is a schematic block diagram of a typical velocity position controller;

[0014] FIG. 5 is a graphical illustration of the piston velocity profile of the velocity position controller of FIG. 8;

[0015] FIGS. 6A and 6B are process flow block diagrams of the velocity position controller of FIG. 5;

[0016] FIG. 7A is a graphical illustration of a piston velocity and servo valve position profile of the present invention which employs a linear response to the servo valve error signal;

[0017] FIG. 7B is a graphical illustration of a piston velocity and servo valve position profile of the present invention which employs a quadratic response to the servo valve error signal; and

[0018] FIG. 8 is a schematic block diagram of the velocity position controller of the present invention.

Detailed Description of the Invention

[0019] Referring now to FIGS. 1 and 2, in which like elements have like reference numbers, a prior art illustration of an injection molding machine 10 is shown. Control unit 28 generates a servo valve position command signal 122 that acts to control the velocity of piston 27 enabling piston to traverse from a clamp open position to a clamp closed position. More particularly, piston assembly 50 comprises servo valve 52 which is actuated by control unit 28 to cause servo valve 52 to be displaced a distance “x_v” from a null position 53 during normal operation. This displacement regulates the net pressure (P₂inlet pressure minus P₁return pressure) of hydraulic fluid on piston 27 so as to cause piston 27 to traverse from the clamp open position to the clamp closed position at a desired velocity.

[0020] The present invention is employed to estimate and regulate the force of clamp assembly 113 on the mold/plastic part as it is forged during the clamp cycle. The force exerted by piston 27 on mold 20 may be estimated by equation (1) listed below:

[0021] F=(P₃A₂−P₄A₄)−Ma equation 1

[0022] where “F” is the force exerted by piston 27 on the mold, P₃is the hydraulic pressure on a first surface of piston 27, P₄is the hydraulic pressure on a second surface of piston 27, A₂is the first surface area of piston 27, A₄is the second surface area of piston 27, “M” is the mass of mold, 20 and “a” is the acceleration of piston 27.

[0023] Generally, the hydraulic fluid flow rate “Q” is related to the difference in pressure on both sides of servo valve 52 and the area of the servo valve opening according to the general mathematical relationship illustrated in equation 2

\begin{matrix} Q = C_{d} A \sqrt{\frac{2 Δ P}{ρ}} & equation 2 \end{matrix}

[0024] where C_dis a fluid pressure coefficient, “ρ” is the fluid density, “A” is the area of the orifice through with the fluid passes, and ΔP is the pressure differential across the orifice. Additionally, the compressibility effect in the hydraulic fluid is defined by equation 3 illustrated below,

\begin{matrix} \frac{ⅆ V}{ⅆ t} = \frac{V}{β} \frac{ⅆ P}{ⅆ t} & equation 3 \end{matrix}

[0025] where “V” is the volume of the hydraulic fluid, β is the bulk modulus, and dP/dt is the derivative of the pressure with respect to time. From these three equations the following first order, non-linear differential equations relating to pressures, velocity and valve opening were derived,

[0026] F=P₃A₂−P₄A₄−Ma equation 4

[0027] where “F” is force exerted by piston 27 on mold 20 and “a” is the acceleration of the piston.

\begin{matrix} \frac{ⅆ p_{3}}{ⅆ t} = \frac{β (Q_{4} - A_{2} v)}{V_{1} + A_{2} x} & equation 5 \end{matrix}

[0028] where dp₃/dt is the derivative of pressure on the first surface A₂of piston 27 with respect to time, and Q₄is the flow rate of the hydraulic fluid into the left chamber, V₁is the initial volume of the fluid in the left chamber, “x” is displacement of the piston from initial position and “v” is the velocity of the piston

\begin{matrix} \frac{ⅆ p_{4}}{ⅆ t} = \frac{β (- Q_{2} + A_{4} v)}{V_{2} - A_{4} x} & equation 6 \end{matrix}

[0029] where dp₄/dt is the derivative of the pressure on the second surface A₄of piston 27 with respect to time, Q₂is the flow rate of the hydraulic fluid returning from piston 27 to servo valve 52 and V₂is the initial volume of the fluid in contact with area A₄. Simulations were conducted using equations 4-6 having the following limitations. The maximum velocity of piston 27 did not exceed about 2,000 millimeters/second. The maximum displacement “x_v” of servo valve 52 was not be greater than about 650 millimeters. The above limitations were employed using a mold mass “M” having values in a range from about 1800 kg to about 5400 kg.

[0030] From the simulations performed using equations 2 through 7, control algorithms were developed to regulate the force exerted by piston 27 on mold 20 and the stroke duration of piston 27, as further described below.

[0031] Referring now to FIG. 3, which illustrates a functional block diagram of the clamp assembly controller 100 and to FIGS. 4 and 8, showing further detail of a velocity position controller 115, in which like elements have like reference numbers.

[0032] Clamp assembly controller 100, comprises desired force limit 118, summer 117, cascade compensator 111, auto selector 112, clamp assembly 113, estimator 114, and velocity position controller 115. Clamp assembly controller 100 optionally may further comprise feedback compensator 116.

[0033] Desired force limit “F” 118 provides a maximum force “F” that piston 27 may generate. This force limit is established by the maximum force that the piston assembly 50 may generate so as not to cause excessive force on mold 20. The maximum force “F” is selectable and depends on the size of the machine and mold.

[0034] Force summer 117 generates a difference signal, referred to as the force difference signal, between the desired force “F” and actual force signal 121 produced by clamp assembly 113. Alternatively, force summer 117 generates force difference signal that is the difference between the desired force signal “F” and the force feedback signal generated by feedback compensator 116.

[0035] Cascade comparator 111 is a lead/lag controller, having proportional and integral gains, that provides lead and lag compensation to the force difference signal generated by force summer 117. The proportional and integral gains values are chosen to provide damped response without oscillations, within a specified bandwidth. The gains are selected through conventional compensation techniques and simulations.

[0036] Velocity and position controller 115 generates a piston velocity signal having a piston velocity profile, illustrated in FIG. 5, in correspondence with the servo valve displacement “x_v” as represented by piston velocity signal 120. Piston velocity profile 200 (FIG. 5) is a graphical illustration of an exemplary piston velocity waveform 210. A maximum velocity (v_max) is the maximum mechanical velocity of piston 27. A final velocity (v_f) is the final estimated velocity of piston 27. A ramp up section 212, having a servo valve displacement interval extending from x_v=0 to x_v=x_u, is defined as the interval where the piston velocity increases from about zero to about 99 percent of v_max. A constant speed interval 214, having a servo valve displacement interval extending from x_uto x_d, is the phase where the piston velocity is substantially constant, typically about 99% of v_max. A ramp down interval 216, having a servo valve displacement interval extending from x_dto x_s, is the phase in which the piston velocity is reduced to v_f, typically much less than v_max. In one exemplary embodiment v_maxmay be about 2000 meters/second and v_fmay be about 40 meters/second. A touchdown interval 218, having a servo valve displacement interval extending from x_sto x_f, is the phase where the piston velocity is constant at about v_f. Each of the intervals x_u, x_d, and x_sare selected based on the velocity and position control process described below.

[0037] Auto selector 112 selects a force control function 123 or a velocity control function 124 to control clamp assembly 113. The force control function 123 is represented by the signal generated by cascade compensator 111 and the velocity control function 124 is represented by the output of the velocity and position controller 115 (e). Auto selector 112 selects the minimum of the two control functions as valve command 122. Servo valve command signal 122 is coupled to clamp assembly 113.

[0038] Clamp assembly 113 operates as described above to open and close mold 20. Clamp assembly 113 generates a piston velocity signal 120 in correspondence with displacement “x_v” of the servo valve 52.

[0039] Estimator 114 operates to measure the actual force generated by piston 27. Alternatively, estimator 114 operates to estimate the force of piston 27 utilizing equation 4, where the acceleration of piston 27 is calculated using piston velocity signal 120 (based on approximate differentiation), P₃, and P₄. If piston velocity is not directly measured, it can be estimated from the piston position signal. Estimator 114 generates actual force signal 121 in correspondence with the measured or calculated force of piston 27.

[0040] In another alternative embodiment of the present invention, feedback compensator 116 may be employed in control 100 to provide lead/lag compensation to actual force signal 121. The compensator may be designed to cancel sensor lags and add damping to the closed loop system.

[0041] Desired final position 119 provides a final position x_fset point for piston 27. The final position x_fis determined based on the desired position for clamp closing. Summer 125 generates a position error signal, referred to as the position error signal (e), which is the difference between the desired final position and the actual position generated by the clamp assembly 113. Desired velocity schedule 154 is a schedule of position error signal (e) versus the desired piston velocity, as illustrated in FIGS. 7A and 7B. Desired velocity schedule 154 generates a desired velocity signal (v). Between zero and small error e_f, i.e., near final position, the desired velocity is the touch down velocity, v_f. The final velocity is established by the maximum necessary velocity of piston 27 in touchdown interval 218 (FIG. 5). This final velocity must be low enough to provide safe mold closing and high enough to minimize the cycle time of clamp assembly 113. In an exemplary embodiment the final velocity is in a range from about 10 to about 50 meters/second. At very high position error, i.e., near the initial position, the desired velocity is the maximum velocity, v_max.

[0042] In between v_maxand v_f, the profile of desired velocity verses error depends on the designer's choice. Here, consideration is given to two choices: 1) constant deceleration (dt) with respect to time, and 2) constant deceleration (d_x) with respect to position. If the deceleration is constant with respect to position and is equal to d_x, then v=v_f+d_x(e−e_f) from e=e_fonwards, until “v” becomes v_max. If the deceleration is constant with respect to time and is equal to dt, then v={square root over (v_f²+2+L d_t+L (e−e_f+L ))} from e=e_fonwards, until “v” becomes v_max.

[0043] The profile of velocity schedule 154 is selected to minimize the cycle time of clamp assembly 113 while at the same time insuring system stability.

[0044] Servo valve displacement look-up table 156 may be employed to provide a valve drive signal which corresponds with the desired velocity, as output by 154. Servo valve limiter 158 limits the valve command to reasonable, physical limits—these may be the same as saturation limits for servo valve 52.

[0045] FIG. 8 provides further detail of an alternative velocity and position controller 115 of the present invention, illustrated in FIG. 3. The present position and velocity controller 115 is adapted to employ a closed loop around the piston force, velocity, and position. Velocity and position controller 115, described in FIG. 4, further comprises a lead/lag controller 157 which is coupled to limiter 158. Clamp assembly 113 generates an actual force signal 159, a piston position signal 120, and a piston velocity signal 161. The force signal 159 is coupled to controller 157. Piston position signal 120 is coupled to a sample and hold block 152 and the piston velocity signal 161 is coupled to a summer 126 via a sample & hold 152. Piston and velocity controller 115 is adapted to control the piston position based on piston force, velocity, and position. Each component operates as described above to regulate piston force, velocity, and position to limit the piston force and the maximize the cycle time of the piston.

[0046] The following steps, illustrated in FIGS. 6A and 6B, identify a process 220 that may be performed by a computer or circuit to determine the velocity profile of piston 27, identified in FIGS. 6A and 6B.

[0047] Step 222. Determine the total servo valve displacement x_ffrom the initial to the final position x_v=0 to x_v=x_fwhen mold 20 is closing.

[0048] Step 224. Select a servo valve displacement (x_s) for mold closing position for the beginning of touchdown phase x_sat v_f. The closer x_sis to x_fthe less the cycle time. For example, x_shas a value that is about 99 percent of x_f.

[0049] Step 226. Choose a ratio α of the servo valve displacement “x_v” during ramp-down interval 216 to the servo valve displacement “x_v” during ramp-up interval 212, according to equation 7 illustrated below.

\begin{matrix} α = \frac{(x_{s} - x_{d})}{x_{u}} & equation 7 \end{matrix}

[0050] x_uis the displacement reached by the piston, by the time “v” reaches about 99% of v_max. x_dis the displacement where the ramp down phase begins. Note that x_d>=x_u. A numerical value for α of about 1.0 or slightly higher/lower may be chosen. Values of α much less than 1.0 should not be selected because they result in mold injection system instability during a rapid ramp down phase. Very high values of α lead to larger cycle time.

[0051] Step 228. Select a piston maximum velocity (v_max) during the ramp-up interval 212 and constant speed interval 214. The desired piston velocity depends on the machine and mold size.

[0052] Step 230. Determine x_ufrom simulations or estimate from previous cycles. It is noted that x_uis approximately proportional to mold mass “M”. X_ucan also be estimated from previous cycles. X_ushould be chosen according to the mathematical relationship

\begin{matrix} x_{u} \leq \frac{x_{s}}{(α + 1)} & equation 8 \end{matrix}

[0053] so that x_dis greater than or equal to x_u. In the event that x_udoes not satisfy equation 8, v_maxmay be reduced to satisfy the relationship between x_uand x_sin equation 8.

[0054] Step 236. Begin ramp up phase with v_max.

[0055] Step 232. If

x_{u} < \frac{x_{s}}{(α + 1)},

[0056] choose x_d=x_s−αx_u. If

x_{u} = \frac{x_{s}}{(α + 1)},

[0057] choose x_d=x_u.

[0058] Step 233. If at

x = \frac{x_{s}}{(α + 1)},

[0059] v<99% of v_max, it implies that x_u>x_s/(α+1). Then, change v_max, x_u, and x_das follows:

[0060] v_max=v at x=x_s/(α+1), x_u=x_s/(α+1), and set x_d=x_u.

[0061] Step 234. Select the piston deceleration profile during ramp-down interval 218 according to a linear profile as further described below. For the linear deceleration profile the slope (dx) is estimated, according to equation 9, based on linear trajectory from x_dto x_s. The linear deceleration profile is illustrated in FIG. 7A.

\begin{matrix} dx = \frac{(v_{\max} - v_{f})}{α x_{u}} & equation 9 \end{matrix}

[0062] Alternatively, a quadratic profile is a more accurate estimate of the deceleration profile of piston 27. When the quadratic deceleration profile is utilized the profile is estimated according to equation 10. The quadratic deceleration profile is illustrated in FIG. 7B.

\begin{matrix} dt = \frac{(v_{\max}^{2} - v_{f}^{2})}{2 α x_{u}} & equation 10 \end{matrix}

[0063] It should be noted that steps 222 through 230 may be executed on the “fly”, that is, during a mold machine cycle after piston 27 has complete the ramp-up interval 212 of it trajectory or off line.

[0064] It will be apparent to those skilled in the art that, while the invention has been illustrated and described herein in accordance with the patent statutes, modifications and changes may be made in the disclosed embodiments without departing from the true spirit and scope of the invention. It is, therefore, to be understood that the appended claims are intended to cover all such modifications and changes as fall within the true spirit of the invention.

Claims

What is claimed is:

1. A control unit for controlling the force and velocity of a piston on a mold within the clamp assembly of a injection molding machine, based on a servo valve command signal which acts to operate a servo valve, said control unit comprising:

a cascade compensator, wherein said cascade compensator is adapted to generate the valve command signal, based on comparison of a desired force and an estimated actual force of the piston on the mold;

an estimator coupled to the clamp assembly, wherein said estimator is adapted to estimate an actual force using cylinder pressure and a piston position signal;

a position and velocity controller being coupled to the clamp assembly and coupled to said estimator, wherein said position and velocity controller is adapted to generate the valve command signal based on desired position and velocity profiles; and

an auto selector being coupled to said cascade compensator, wherein said auto selector is adapted to select between a velocity control function signal and a force control function signal so as to generate the servo valve command signal.

2. The control unit as recited in claim 1, further comprising a desired force limit, wherein said desired force limit is adapted to generate a desired force limit signal.

3. The control unit as recited in claim 1, further comprising a feedback compensator being coupled to said estimator, wherein said feedback compensator is adapted to generate a feedback signal in correspondence with said estimated actual force signal.

4. The control unit as recited in claim 1, wherein said position and velocity controller further comprises:

a desired velocity scheduler adapted to generate a velocity request signal based on a position error signal (e); and

a servo valve look-up table being coupled to said desired velocity scheduler, wherein said servo valve look-up table is adapted to generate the servo valve command signal in correspondence with said velocity request signal.

5. The control unit as recited in claim 4, wherein said desired velocity scheduler is adapted to generate said velocity schedule signal based on said position error signal (e).

6. The control unit as recited in claim 5, further comprising a lead/lag controller coupled to said clamp assembly and said estimator, wherein said lead/lag controller provides a closed loop response between the desired velocity and actual velocity.

7. The control unit as recited in claim 6, wherein a ramp up velocity of the servo valve has an upper limit of v_max, wherein the final touch down velocity of the servo valve is v_fbased on error signal (e), and wherein a ramp down deceleration of the servo valve is constant with respect to time and position.

8. The control unit as recited in claim 7, wherein the ramp down velocity of the servo valve is constant with respect to time.

9. The control unit as recited in claim 7, wherein the ramp down velocity of the servo valve is constant with respect to position.

10. A method for determining the velocity profile of the piston of a clamp assembly, wherein the piston velocity is controlled by the operation of a servo valve within the clamp assembly, and wherein the displacement of the servo valve is controllable, the velocity profile having a ramp-up interval, a constant speed interval, ramp-down interval; and a touchdown interval, said method comprising the following steps:

where x_uis a servo valve displacement and x_dis a displacement where a ramp down interval begins;

determining a maximum displacement x_sof the servo valve;

selecting a final velocity of the piston (v_f);

choosing a ratio α of a piston ramp-down interval to the servo valve displacement “x” during the ramp-up interval, according to equation

α = \frac{(x_{s} - x_{d})}{x_{u}}

selecting a desired maximum piston velocity (v_max) during the ramp-up interval and constant speed interval; and

determining the servo valve displacement x_ufrom simulations or estimate from previous cycles according to a mathematical relationship

x_{u} \leq \frac{x_{s}}{(α + 1)} .

11. The method as recited in claim 10, further comprising the step of choosing a servo valve displacement of x_d=x_s−αx_uwherein

x_{u} < \frac{x_{s}}{(α + 1)} .

12. The method as recited in claim 11, further comprising the step of choosing a servo valve displacement of x_d=x_uwherein

x_{u} = \frac{x_{s}}{(a + 1)} .

13. The method as recited in claim 12, further comprising the step of selecting a piston deceleration profile during the ramp-down interval according to a linear and a quadratic velocity profile.

14. The method as recited in claim 13, further comprising the step of determining said linear velocity profile having a slope (d_x) according to the equation

d_{x} = \frac{(v_{\max} - v_{f})}{α x_{u}}

based on the piston having a linear velocity trajectory from x_dto x_s.

15. The method as recited in claim 12, further comprising the step of selecting the piston deceleration profile during the ramp-down interval according to a quadratic velocity profile.

16. The method as recited in claim 15, further comprising the step of determining said quadratic velocity profile (d_t) according to the equation

d_{t} = \frac{(v_{\max}^{2} - v_{f}^{2})}{2 α x_{u}} .

17. A control unit for controlling the force and velocity of a piston on a mold within the clamp assembly of a injection molding machine, based on a servo valve command signal which acts to operate a servo valve, said control unit comprising:

a desired force limit, wherein said desired force limit is adapted to generate a desired force limit signal;

a cascade compensator connected to the desired force limit, wherein said cascade compensator is adapted to generate the valve command signal, based on comparison of the desired force and an estimated actual force of the piston on the mold;

an estimator coupled to the clamp assembly, wherein said estimator is adapted to estimate an actual force using cylinder pressure and a piston position signal;

a feedback compensator being coupled to said estimator, wherein said feedback compensator is adapted to generate a feedback signal in correspondence with said estimated actual force signal.

18. A method for determining the velocity profile of the piston of a clamp assembly, wherein the piston velocity is controlled by the operation of a servo valve within the clamp assembly, and wherein the displacement of the servo valve is controllable, the velocity profile having a ramp-up interval, a constant speed interval, ramp-down interval; and a touchdown interval, said method comprising the steps of:

and

determining a maximum displacement x_sof the servo valve;

selecting a final velocity of the piston (v_f);

choosing a ratio α of a piston ramp-down interval to the servo valve displacement “x” during the ramp-up interval, according to equation α=(x_s−x_d)/x_uwhere x_uis a servo valve displacement and x_dis a displacement where a ramp down interval begins;

selecting a desired maximum piston velocity (v_max) during the ramp-up interval and constant speed interval;

determining the servo valve displacement x_ufrom simulations or estimate from previous cycles according to a mathematical relationship

x_{u} \leq \frac{x_{s}}{(α + 1)};

selecting a piston deceleration profile during the ramp-down interval according to a linear velocity profile.

19. The method as recited in claim 18 wherein the step of selecting the piston deceleration profile during the ramp-down interval also selects the piston deceleration according to a quadratic velocity profile.

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Abstract