U.S. patent number RE31,608 [Application Number 06/220,622] was granted by the patent office on 1984-06-19 for fluid pump mechanism.
This patent grant is currently assigned to Altex Scientific, Inc.. Invention is credited to Haakon T. Magnussen, Jr..
United States Patent |
RE31,608 |
Magnussen, Jr. |
June 19, 1984 |
Fluid pump mechanism
Abstract
A fluid pump mechanism for delivering a smooth output of fluids
to a system utilizing at least one piston in a chamber
reciprocative therewithin. The piston has strokes that fill and
empty the chamber in conjunction with the action of valve means
located at the inlet and outlet of the chamber. Motive means causes
reciprocation of the piston within the chamber. Control means is
also included for minimizing the time during the piston cycle in
which the piston is not emptying the chamber. The invention's scope
also encompasses a pressure metering device for a fluid forcing
means motivated by an electrical motor.
Inventors: |
Magnussen, Jr.; Haakon T.
(Pinole, CA) |
Assignee: |
Altex Scientific, Inc.
(Berkeley, CA)
|
Family
ID: |
26915029 |
Appl.
No.: |
06/220,622 |
Filed: |
December 29, 1980 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
Issue Date |
|
Reissue of: |
761433 |
Jan 21, 1977 |
04131393 |
Dec 26, 1978 |
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Current U.S.
Class: |
417/22; 417/45;
417/53 |
Current CPC
Class: |
B01D
15/14 (20130101); F04B 9/042 (20130101); F04B
49/06 (20130101); G01N 30/32 (20130101); G01N
30/36 (20130101); F04B 49/20 (20130101); G01N
2030/326 (20130101); F04B 2201/0201 (20130101) |
Current International
Class: |
B01D
15/08 (20060101); F04B 9/04 (20060101); F04B
9/02 (20060101); F04B 49/20 (20060101); F04B
49/06 (20060101); G01N 30/36 (20060101); G01N
30/00 (20060101); G01N 30/32 (20060101); F04B
049/00 () |
Field of
Search: |
;417/18-22,43
;210/198.1,101 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Freeh; William L.
Attorney, Agent or Firm: Steinmeyer; R. J. Meads; Robert
R.
Claims
What is claimed is:
1. A fluid pump mechanism for delivering fluid against a back
pressure comprising:
a. piston, at least a portion of which is reciprocative within a
chamber having a fluid inlet and fluid outlet said piston having a
first end portion and a second end portion, said first end portion
contacting the fluid, said piston being capable of filling and
emptying said chamber;
b. motive means for reciprocating said piston within said chamber
at a selected substantially constant speed, said substantially
constant speed determined by constant speed setting means for
setting said motive means at a substantially constant speed, said
motive means at a substantially constant speed, said motive means
contacting said second end portion of said piston;
c. valve means for permitting the filling and emptying of said
chamber coordinated with the pressure exerted by said piston within
said chamber; said piston, motive means and valve means cooperating
to produce a time duration of fluid flow from said chamber ralative
to said selected substantially constant speed;
d. control means for changing the speed of said motive means at a
preselected portion of the time period of said reciprocation of
said piston within said chamber, said control means including
detection means for detecting and signaling the inception of the
chamber filling stroke of said piston and the termination of said
chamber filling stroke of said piston; filling means for changing
said constant speed of said motive means at the inception of the
chamber filling stroke of said piston and returning said motive
means to said constant speed at the termination of said chamber
filling stroke of said piston said filling means being activated
and deactivated by said detection means signal.
2. The fluid pump mechanism of claim 1 in which said control means
additionally comprises pump-up means for changing the speed of said
motive means at the termination of said chamber filling stroke of
said piston and returning said motive means to said predetermined
constant speed after a certain distance of travel of said piston's
emptying stroke, said pump-up means activated upon receipt of said
chamber filling stroke termination signal from said detection
means.
3. The fluid pump mechanism of claim 2 in which said motive means
includes an electrical motor rotating a shaft and said pump-up
means includes:
a. pressure measuring means for measuring and signaling the back
pressure on said chamber outlet;
b. pump-up gain means for producing a selected ramp signal
proportional to piston displacement.
c. comparitor means for producing a stepped-up signal to said
electric motor, said signal turning said shaft a certain angular
distance in proportion to the time duration of said ramp signal
substantially equaling said pressure signal.
4. The fluid pump mechanism of claim 3 in which said pump-up gain
means comprises:
a. tachometer means for measuring the axial rotational rate of said
shaft and transforming the same into a pulse signal;
b. gain means for receiving said pulse signal and adjusting the
amplitude of said pulse signal;
c. charge integrator means for receiving said amplitude adjusted
pulse signal from said gain means and producing said ramp signal
proportional to said amplitude adjusted pulse signal, and certain
number of pulses received.
5. The fluid pump mechanism of claim 4 which additionally comprises
torque measuring means for measuring the torque load on said
electrical motor and for transforming said torque load measurement
into a measurement of back pressure on said piston during its
emptying stroke.
6. The fluid pump mechanism of claim 5 in which said electrical
motor is a direct current motor and said torque measuring means
measures said torque load on said direct current motor in terms of
a current supplied to said direct current motor and said torque
measuring means signals said value of current supplied to a readout
indicating the value of said back pressure associated with said
piston.
7. The fluid pump mechanism of claim 5 which additionally includes
means for deactivating said electrical motor at a selected value of
said back pressure associated with said piston.
8. The fluid pump mechanism of claim 7 in which said means for
deactivating said electrical motor comprises high pressure limiting
means for deactivating said electrical motor at a predetermined
back pressure, associated with said piston, above a selected
working pressure range of said piston and low pressure limiting
means for deactivating said electrical motor at a predetermined
back pressure associated with said piston below said selected
working pressure range of said piston.
9. The fluid pump mechanism of claim 8 in which said high pressure
limiting means for deactivating said electrical motor also
comprises hysteresis means for reactivating said electrical motor
upon return of said back pressure associated with said piston to
said selected working pressure range of said piston.
10. The fluid pump mechanism of claim 9 in which said reciprocating
means comprises a cam shaft connected to said motor shaft, a cam,
and a cam follower connected to said second end portion of said
piston.
11. A fluid pump mechanism for delivering fluid against a back
pressure comprising:
a. piston, at least a portion of which is reciprocative within a
chamber having a fluid outlet said piston having a first end
portion and a second end portion, said first end portion contacting
the fluid, said piston being capable of filling and emptying said
chamber;
b. motive means for reciprocating said piston within said chamber
at a selected substantially constant speed, said substantially
constant speed, said substantially constant speed determined by
constant speed setting means for setting said motive means at a
substantially constant speed, said motive means contacting said
second end portion of said piston;
c. valve means for permitting the filling and emptying of said
chamber coordinated with the pressure exerted by said piston within
said chamber; said piston, motive means and valve means cooperating
to produce a time duration of fluid flow from said chamber relative
to said selected substantially constant speed;
d. control means for changing the speed of said motive means at a
preselected portion of the time period of said reciprocation of
said piston within said chamber, said control means including pump
up means for changing the speed of said motive means at the
termination of the chamber filling stroke of said piston and
returning said motive means to said predetermined constant speed
after a certain distance of travel of said piston during its
emptying stroke; and detection means for detecting and signaling
the termination of said chamber filling stroke of said piston, said
pump up means activated upon receipt of said chamber filling stroke
termination signal from said detection means.
12. The fluid pump mechanism of claim 1 in which said filling means
comprises:
a. filling amplifier coupled to said detection means and receiving
a signal therefrom, said filling amplifier producing a signal
representing the inception of said filling stroke of said
piston;
b. constant speed decoupling means for disabling said constant
speed setting means, upon receipt of a signal from said filling
means;
c. filling speed control means for determining the speed of said
motive means during said filling stroke of said piston.
13. The fluid pump mechanism of claim 11 in which said pump-up
means comprises:
a. pump-up speed control means for determining the speed of said
motive means during the pump-up period of the emptying stroke of
said piston;
b. pump-up gain means for producing an amplitude adjusted signal
proportional to the speed of said motive means during said pump-up
period;
c. charge integrator receiving said pump-up gain means signal and
producing a ramp signal proportional to the displacement of said
motive means;
d. pressure measuring means for measuring the back pressure on said
piston and transforming said back pressure measurement a
signal;
e. comparitor receiving said ramp signal and said back pressure
signal, said comparitor producing a signal when said ramp signal
substantially equals said back pressure signal, said comparitor
signal disabling said pump-up speed control means and
reestablishing the speed of said motive means in accordance with
said constant speed setting means.
14. The fluid pump mechanism of claim 11 in which said certain
distance of travel of said piston's emptying stroke is proportional
to a predetermined value of chamber pressure during normal
delivery.
15. The fluid pump mechanism of claim 14 in which said motive means
includes a motor rotating a shaft, said shaft actuating
reciprocating means for reciprocating said piston within said
chamber, and said detection means further comprises a photon
intercepting flag rotatable with the axial rotation of said shaft,
and a photon interrupter module, said flag intercepting the photon
beam within said module during a certain portion of the arc of
rotation of said shaft corresponding to the period between
inception and termination of said chamber filling stroke of said
piston.
16. The fluid pump mechanism of claim 14 in which said motive means
includes a motor rotating a shaft, said shaft actuating
reciprocating means for reciprocating said piston within said
chamber, and said detection means comprises a pulsing tachometer of
said shaft's rotation, and a digital counter summing pulses from
said tachometer during a certain portion of the arc of rotation of
said shaft corresponding to the period between inception and
termination of said chamber filling stroke of said piston.
17. The fluid pump mechanism of claim 11 which additionally
comprises torque measuring means for measuring the torque load on
said motive means and for transforming said torque load measurement
into a measurement of the value back torque on said piston during
its emptying stroke, and blanking means for interrupting said
measurement of torque load on said motive means during filling, and
pump up said chamber.
18. The fluid pump mechanism of claim 17 which additionally
comprises a readout indicating said back pressure value associated
with said piston, and holding means for retaining said back
pressure value indicated on said readout immediately before
interruption of torque measurement by said blanking means.
19. The fluid pump mechanism of claim 18 in which said blanking
means interrupts said torque measurement during a selected time
period after said pump-up period. .[.20. Pressure signal device
comprising:
a. electrical motor;
b. fluid forcing means for displacing fluid against a back
pressure, said fluid forcing means motivated by said electrical
motor;
c. torque measuring means for measuring the torque load on said
electrical motor and transforming said torque load measurement into
a value of said back pressure associated with said fluid forcing
means; and
d. means for deactivating said electrical motor at a selected value
of said back pressure associated with said fluid forcing means..].
.[.21. The device of claim 20 in which said electrical motor is a
direct current motor and said torque measuring means measures said
torque load on said direct current motor in terms of a current
supplied to said direct current motor, and said torque measuring
means signals said value of current supplied to a readout
indicating the value of said back pressure associated with said
fluid forcing means..]. .[.22. The fluid pump mechanism of claim 20
which additionally comprises blanking means for interrupting said
measurement of torque load on said electrical motor during selected
periods of the operation of said fluid forcing means..]. .[.23. The
device of claim 20 in which said means for deactivating said
electrical motor comprises high pressure limiting means for
deactivating said electrical motor at predetermined back pressure
associated with said fluid forcing means above a selected working
pressure range of said fluid forcing means and a low pressure
limiting means for deactivating said electrical motor at a
predetermined back pressure associated with said fluid forcing
means below said selected working pressure range of said fluid
forcing means..]. .[.24. The device of claim 23 in which said high
pressure limiting means for deactivating said electrical motor also
comprises hysteresis means for reactivating said electrical motor
upon return of said back pressure associated with said fluid
forcing means to
said selected working pressure range of said fluid forcing
means..]. 25. A fluid pump mechanism for delivering fluid against a
back pressure comprising:
a. piston, at least a portion of which is reciprocative within a
chamber having a fluid inlet and fluid outlet said piston having a
first end portion and a second end portion, said first end portion
contacting the fluid, said piston being capable of filling and
emptying said chamber;
b. motive means for reciprocating said piston within said chamber
at a selected substantially constant speed, said substantially
constant speed determined by constant speed setting means for
setting said motive means at a substantially constant speed, said
motive means contacting said second end portion of said piston;
c. valve means for permitting the filling and emptying of said
chamber coordinated with the pressure exerted by said piston within
said chamber; said piston, motive means and valve means cooperating
to produce a time duration of fluid flow from said chamber relative
to said selected substantially constant speed;
d. control means for changing the speed of said motive means at a
preselected portion of the time period of said reciprocation of
said piston within said chamber, said control means comprising
detection means for signaling the inception and termination of the
emptying of said chamber by said piston; current sensing resistor
producing a signal proportional to the instantaneous torque load on
said motive means; summing amplifier producing a torque error
signal; integrator receiving said torque error signal from said
summing amplifier and a signal from ground, said summing amplifier
receiving as inputs said current sensing sensing resistor signal
and the output of said integrator; tachometer means producing a
signal proportional to the speed of said motive means said constant
speed setting means producing a reference signal corresponding to a
desired speed of said motive means; and servo summing amplifier,
said torque error signal from said summing amplifier, said
tachometer means signal and said normal speed setting means signal
and said normal speed setting means signal serving as inputs to
said servo summing amplifier, said servo summing amplifier
producing an amplified
error signal to said motive means. 26. The fluid pump mechanism of
claim 25 which additionally includes a differentiator producing a
signal proportional to the acceleration of said motive means, said
differentiator signal serving as a subtractive input to said
summing amplifier. .[.27. A method of obtaining the value of back
pressure acting against a fluid forcing means for control of the
same comprising the steps of:
a. providing an electrical motor and motivating the fluid forcing
means with said electrical motor;
b. measuring the torque load on said electrical motor at a selected
time;
c. transforming said torque load measurement into a value of the
back pressure acting against fluid forcing means; and
d. deactivating said electrical motor at a selected value of said
back pressure associated with said fluid forcing means..]. .Iadd.
28. A fluid pump mechanism for delivering fluid against a back
pressure comprising:
a piston movable within a chamber for drawing fluid into the
chamber during a chamber filling interval, pressurizing the fluid
during a pressurizing interval wherein the fluid pressure attains
an effective delivery value prior to delivery from the chamber and
delivering the pressurized fluid from the chamber during a delivery
interval of piston movement; and
means for controlling the rate of piston movement such that the
piston moves at a predetermined rate during delivery of the
pressurized fluid, said controlling means including "pump-up" means
for establishing a greater rate of piston movement during the
pressurizing of the fluid, for signalling completion of fluid
pressurization, and for thereupon establishing the predetermined
rate of piston movement for effecting delivery of the pressurized
fluid from the chamber. .Iaddend..Iadd. 29. The pump mechanism of
claim 28 wherein said controlling means includes:
means for generating a signal having a value related to the
pressure of fluid in the chamber;
means for storing the value of the signal generated during a
delivery interval;
means for comparing a present value of the signal during the
chamber pressurizing interval with the stored value; and
means for changing the rate of piston movement during at least a
portion of the chamber pressurizing interval to a rate exceeding
the predetermined rate by an amount related to any difference
between said present and stored values. .Iaddend. .Iadd. 30. The
mechanism of claim 28 or claim 29 wherein the controlling means
further includes means for detecting and signalling the inception
and termination of the filling interval and means responsive to the
detecting and signalling means for changing the rate of piston
movement during the chamber filling interval to a rate exceeding
the predetermined rate. .Iaddend..Iadd. 31. The mechanism of claim
28 wherein the "pump-up" means includes:
means for storing a first signal indicative of a predetermined
chamber pressure effective to deliver pressurized fluid from the
chamber;
means for generating a second signal indicative of chamber pressure
during the pressurizing interval; and
means for comparing the first and second signals and signalling
completion of fluid pressurization when such comparison indicates
that the chamber pressure has attained the predetermined effective
delivery value thereof. .Iaddend..Iadd. 32. The mechanism of claim
30 wherein the "pump-up" means includes:
means for storing a first signal indicative of a predetermined
chamber pressure effective to deliver pressurized fluid from the
chamber;
means for generating a second signal indicative of chamber pressure
during the pressurizing interval; and
means for comparing the first and second signals and signalling
completion of fluid pressurization when such comparison indicates
that the chamber pressure has attained the predetermined effective
delivery value thereof. .Iaddend. .Iadd. 33. Pressure signal device
comprising:
a. electrical motor;
b. fluid forcing means for displacing fluid against a back
pressure, said fluid forcing means motivated by said electrical
motor;
c. torque measuring means for measuring the torque load on said
electrical motor and transforming said torque load measurement into
a value of said back pressure associated with said fluid forcing
means;
d. means for deactivating said electrical motor at a selected value
of said back pressure associated with said fluid forcing means;
and
e. blanking means for interrupting said measurement of torque load
on said electrical motor during selected periods of the operation
of said fluid
forcing means. .Iaddend..Iadd. 34. Pressure signal device
comprising:
a. electrical motor;
b. fluid forcing means for displacing fluid against a back
pressure, said fluid forcing means motivated by said electrical
motor;
c. torque measuring means for measuring the torque load on said
electrical motor and transforming said torque load measurement into
a value of said back pressure associated with said fluid forcing
means;
d. means for deactivating said electrical motor at a selected value
of said back pressure associated with said fluid forcing means;
and
e. wherein said means for deactivating said electrical motor
comprises high pressure limiting means for deactivating said
electrical motor at predetermined back pressure associated with
said fluid forcing means above a selected working pressure range of
said fluid forcing means and a low pressure limiting means for
deactivating said electrical motor at a predetermined back pressure
associated with said fluid forcing means below said selected
working pressure range of said fluid forcing means. .Iaddend.
.Iadd. 35. The device of claim 34 in which said high pressure
limiting means for deactivating said electrical motor also
comprises hysteresis means for reactivating said electrical motor
upon return of said back pressure associated with said forcing
means to said selected working pressure range of said fluid forcing
means.
Description
BACKGROUND OF THE INVENTION
The present invention relates to a novel fluid pump mechanism which
will deliver fluid or fluids at a given flow rate and with a
greatly reduced pulsation. The present invention is particularly
useful, although not limited, delivering liquid solvents at very
high pressures.
For example, a typical liquid chromatographic column contains
packing of finely divided particles for solute separation of a
liquid sample. These packed columns create a very high back
pressure on the fluid forcing means, i.e.: a positive displacement
pump. Moreover, such a pump usually produces a pulsing flow due to
the normal action of a piston within a chamber, which can distort
the analysis of the solute.
Prior devices have employed pulse dampeners on the output side of
the pump as well as dual pistons with overlapping cam methods to
overcome such problems. Flow feedback and pressure feedback pumps
have been used also. However, these mechanisms work inefficiently
and are susceptible to breakdown because of the complexity of the
components in their makeup. Such prior pumps still deliver pulsed
flow because of chamber compliance compressibility of the fluid
being pumped and other factors.
Moreover, constant speed motors driving single piston pumps will
produce a pulsing flow and deliver reduced flow rate at high back
pressures unless corrected. Additional components such as pressure
transducers are expensive and necessarily add to the unreliability
of the liquid solvent delivery system.
There is a need for a simple, reliable, metering pump which has
greatly reduced pulsations in the delivery of fluids, especially
liquid chromatographic solvents.
SUMMARY OF THE INVENTION
In accordance in its the present invention a novel fluid pump
mechanism is provided.
The mechanism in its basic form includes a piston having a portion
reciprocative within a chamber. Valve means permits the filling and
empyting of the chamber with the corresponding strokes of the
piston. To generate a smooth and relatively pulse free flow of
fluid from the mechanism, control means masters the reciprocation
of the piston when the chamber is not in the process of emptying or
delivering the fluid being pumped. Generally, this would
externalize in a speeding up of the piston during its filling
stroke and a speeding up of the piston during the "pump-up" period,
which is the time when the piston moves to deliver the fluid being
pumped, but before the fluid leaves the chamber. Pump-up results
from the exertion of back pressure on the chamber outlet, as well
as fluid and piston compressibility, seal compliance, and other
factors.
Motive means such as, but not limited to an electric motor, drives
the piston through its reciprocations within the chamber at a
normal or base speed commensurate with the desired flow rate of
fluid during the emptying stroke of the piston.
The control means during the filling period may include detection
means to acquire and signal the inception of the filling stroke of
the piston. Such detection means may take many forms such as a
light or photon intercepting flag rotatable with a shaft actuating
a reciprocating means when the motive means includes such elements.
A light or photon interceptor module would generate such a signal.
Interception of this photon signal would then generate an
electrical signal announcing the beginning of the piston filling
stroke to filling means which would change the normal speed of the
motive means to a speed, usually higher, which would cause filling
or refilling of the chamber as quickly as possible. The speed of
filling setting would depend on such criteria as check valve
response and, degassing or cavitation characteristics of the fluid
being pumped. Thus, the pump mechanism completes the filling or
refilling phase as quickly as possible so that the piston may
devote its greatest effort toward pushing the fluid from the
chamber.
Likewise, the detection means may be constructed along the lines of
a digital counter having a pulsing tachometer measuring the turning
of the motive means shaft. A digital counter would sum these pulses
from the pulsing tachometer during the filling period and effect
the change of speed of the motive means and piston. Further, the
analog equivalent of this digital integration, i.e.: analog
integration, may perform the same function.
Where the motive means has reciprocating means, such a format may
include a cam shaft, linked to the shaft of the motive means; cam
surface; and a cam follower connected to one end of the piston. The
detection means would be coordinated with the corresponding
portions of the piston cycle devoted the filling of the chamber.
After filling, the piston returns to pump the fluid from the newly
filled chamber but the flow of fluid delays for a number of
reasons. For instance, the back pressure of the body to which the
fluid is being pumped, will permit the valve means on the outer
check valve to open only when the back pressure is equaled by the
fluid pressure within the chamber. This "pump-up" portion of the
cycle also depends on fluid compressibility, seal compliance, and
piston and chamber compliance. Under most conditions, the pump-up
portion of the piston cycle extends for a finite time during which
no fluid passes from the chamber. The mechanism also embraces
pump-up means to increase the speed of the motive means immediately
after the termination of the chamber filling stroke of the piston
and returns the motive means to a predetermined normal speed when
the chamber reaches the proper pressure to open the valve means on
the chamber outlet. The pump-up means may be mated with the fast
filling or fast refilling cycle of the piston heretofore
described.
In one aspect, the pump-up means may include a running or variable
system to fix the increased speed of the motive means according to
the value of the back pressure encountered. For example, pressure
signal means would acquire and transmit the valve of the back
pressure to comparitor means. Pump-up gain means would produce a
selected reference ramp signal to the comparitor which would step
up the motive means for an angular duration i.e.: a certain number
or fraction of turns of the motor shaft. The pump-up gain means
might include tachometer means for measuring the axial rotational
rate of the motor shaft and transforming the same into a pulse
signal. Gain means would receive the pulse signal and adjust its
amplitude to a certain value. Charge integrator means integrates
the amplitude adjusted signal from the gain means and produces a
reference ramp signal proportional to the motive means angular
duration.
The invention also devises a novel means for deducing the pressure
on the motive means if it is an electric motor actuating a fluid
forcing means for displacing the fluid against a back pressure.
Pressure measuring means transforms the torque load measured on the
electrical motor to a value of pressure for the fluid forcing
means. In the case of a shunt wound or permanent magnet D.C. motor
torque load is measured in terms of a current supplied to the
motor.
The pressure signal means associated with the pump-up means may be
of a torque load type. Likewise, the pressure signal means may
indicate the pressure of the system only while the fluid pumps out
from the chamber and not during filling or pump-up. The pressure
determined from the motor's torque load may be fed to a readout as
well as to means for deactivating the electrical motor at a
preselected high and/or low value of pressure. Blanking means may
be included to interrupt the pressure measuring means during a
portion of the piston cycle e.g.: filling and pump-up.
Thus, a novel and useful pump mechanism has been invented which
minimizes the time duration of filling and pump-up of a pumping
piston and maximizes the time duration of fluid flow at high
pressures with a minimum pulsation.
It is therefore an object of the present invention to provide a low
cost, reliable, and efficient pump mechanism for delivering fluids
at high pressures in a pulseless state.
It is another object of the present invention to provide a pump
mechanism compatible with liquid chromatographic systems including
but not limited to packed columns.
It is yet another object of the present invention to provide a pump
mechanism which will increase the time during which fluid is
delivered to a receiving system and decreases the time of filling
or refilling and pump-up prior to such delivery.
Another object of the present invention is to provide a pump
mechanism which meters fluid flow under high pressures.
Still another object of the present invention is to provide a pump
mechanism which measures pressure from the torque load on its
motive means and feeds this value back to the motive means as a
method of motive means speed control.
Another object of the present invention is to provide pressure
signal means for an electric motor in combination with fluid
forcing means in terms of the measurement of torque load on such an
electric motor.
The invention possesses other objects and advantages especially as
concerns particular features and characteristics thereof which will
become apparent as the specification continues.
Various aspects of the present invention will evolve from the
following detailed description of the preferred embodiment thereof
which should be taken in conjunction with the accompanying
drawings.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 is a top plan view of the mechanism with the piston section
shown in section
FIG. 2 is a view taken along line 2--2 of FIG. 1
FIG. 3 is a view taken along line 3--3 of FIG. 1
FIG. 4 is a view taken along line 4--4 of FIG. 1
FIG. 5 is a broken side view of the tachometer section shown in
FIG. 4.
FIG. 6 is a block diagram of the electrical control means.
FIG. 7 is an electrical schematic diagram of a preferred embodiment
of the invention.
FIG. 8 is a block diagram of a preferred embodiment of the
invention.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS
The pump mechanism of the present invention as a whole is indicated
in the drawings by reference character 10 and includes as one of
its elements a piston 12 which reciprocates within chamber 14.
Piston first end portion 16 contacts the fluid traveling into and
out of chamber 14, and piston second end portion 18 contacts motive
means 20. Piston 12 moves back and forth within chamber 14 to fill
and empty the chamber of fluid. As depicted in FIG. 1, the chamber
fills when piston 12 moves from right to left.
Chamber housing 22 includes set screws 24 and studs 26 which engage
pump body 28 to hold the chamber housing 22 in place. Plunger 30
rides within plunger barrel 32 and on bearing 33, and connects to
piston second end portion 18 via ferrule 34. Seal 36 maintains the
pressure integrity of chamber 14. Valve means 38, FIG. 2, includes
an inlet check valve 40 and an outlet check valve 42 which
threadingly engage chamber housing 22. Opening 44 permits the
removal and inspection or repair of the connection of piston 12 to
ferrule 34.
Plunger 30 terminates at the end opposite to piston second end
portion 18 in a cam follower 46 which rolls or slides on cam
surface 48 of cam 50. Cam support 74 further stabilizes cam
follower 46. Spring means 52 bears on collar 54 of plunger 30 and
shoulder 56 of pump body 28. Plate 58 and connecting bolts 60
permit access to the cam 50. Motive means further includes cam
shaft 62 which turns by dint of the rotational force of electric
motor 64, FIG. 1. The cam shaft 62 turns hub 66, within bearing 68
and seals 70, which in turn connects to hub 72 holding cam 50. Cam
shaft 62 is reduced, by any conventional means, to a slower speed,
on the order of 50:1, than shaft 73 which turns without reduction
on the opposite of electric motor 64.
Control means 76, including detection means 77, shown in block
diagram FIG. 6, interfaces with the mechanical elements of FIGS. 1
and 2 with a detector 75 such as photon intercepting flag 78 which
turns with cam shaft 62 on hub 66, FIG. 3. Detector 75 further
includes photon intercepting module 80 which fastens to motor
housing 82 by means of bracket 84 and set screws 86. Terminals 88
relay the photon interruption of flag 78 to filling means 79.
Similarly, shaft 73 terminates in tachometer means 90, FIGS. 1, 4,
and 5, which has a graduated wheel 92 and an optical detector 94.
The wheel 92 is graduated into 360 transitions one for each degree
of turn. Again terminals 88 transmit the light interruption in a
series of electrical pulses. Disc 98 holds graduated wheel 92 onto
shaft 74 with the aid of friction wheel 100. Optical detector 94 is
supported by bracket 102 and set screws 104 in place. Appendage
106, fixed to motor housing 82 supports brackets 84, and 102 as
desired.
Control means 76, FIG. 6, changes the speed of motive means 20
during the time period other than the time period when the chamber
14 is being emptied of fluid.
Turning to the block diagram, FIG. 6, normal or constant speed
setting means 108 directs voltage to current sink converter 110 to
pull a current proportional to constant speed setting means 108.
Summing node 116 measures the error current between the current
determined by the constant speed setting means 108 and the current
from frequency charge pump 118 which produces a current
proportional to the speed of motive means 20 measured by tachometer
means 90. Summing amplifier 120, a high gain amplifier, delivers a
servo error signal according to reference voltage 122 in comparison
with the instantaneous error current at summing node 116. Servo
gain and compensation means 124 provides feedback to summing node
116, but is a relatively small current when compared to the current
from frequency charge pump 118.
Pulse width modulator generator driver 126 generates pulse width
modulated signal which has a duty cycle proportional to the input
error signal from summing amplifier 120. Pulse width modulator
generator driver 126 then provides a changing voltage to motive
means 20, which may be a D.C. motor. Thus, constant speed setting
means 108 determined the speed of motive means 20 through a null
circuit, including summing node 116, servogain and compensation
means 124, summing amplifier 120, and reference voltage 122, and
pulse width modulator generator driver 126.
After delivery of the fluid in chamber 14 by the emptying action of
piston 12, at a selected normal or substantially constant speed,
detection means 77 will acquire and signal the inception of the
filling or refilling stroke of piston 12, and signal the
termination of such filling stroke. As previously discussed, such
detection means 77 may be accomplished in the preferred embodiment
by a photon intercepting flag 78 interrupting module 80, during the
filling stroke of piston 12. Likewise, detection means 77 may take
the form of a pulsing tachometer coupled with a triggered or
resetting digital counter to sum pulses therefrom, to indicate the
period of the filling stroke of piston 12. For example, in the
present embodiment, the onset of the filling of chamber 14, where
motive means 20 includes a D.C. motor, reverses the load upon such
motor because of the negative slope 51 on cam 50. The sudden drop
in motor current may be detected and employed to start a digital
counter. This indication of the beginning of filling stroke of
piston 12 may be accomplished by other timing or shaft rotational
measuring devices known to persons of ordinary skill in this art.
The digital counter would determine the angular duration of the
filling period. An analog integrator could also be employed for
this purpose, by integrating a tachometer signal and producing an
output proportional to angular duration for the filling period. The
digital count would be compared to a standard count representing
the filling movement of piston 12. The analog integrator, on the
other hand, would be compared to a fixed or reference voltage
representing the end of the piston's filling stroke. A typical
value of the angular duration of the filling or refilling stroke of
piston 12 is about 50 degrees.
Filling amplifier 128 coupled to a detector 75 senses the beginning
of the filling stroke of piston 12 and signals and activates first
switch means 114 via "OR" gate 130 and second switch means 132
directly. First switch means 114 in conjunction with constant speed
decoupling means 112 effectively bypasses the voltage to current
sink converter 110 and pump-up speed control 152 from summing node
116. Thus, filling speed control means 134 determines the speed of
motive means 20 while the piston 12 moves through its filling or
refilling stroke. Filling speed control means 134 increases the
speed of motive means 20 in most cases at a rate commensurate with
such considerations as, the cavitation and degassing
characteristics of the fluid, liquid, solvent, or the like, being
pumped by mechanism 10.
Furthermore, the speed of valve means 38, as well as the hydraulic
geometry of the mechanism 10 must be considered as a limiting
factor for pumped liquids. At very fast normal speeds, the motive
means may slow during filling because of these factors. This is
especially true of low boiling point solvents such as pentane,
ethyl ether and the like.
The inception of filling speed-up by filling means 79 also sets
charge integrator 136 to a very low value and it remains there
during the refilling stroke of piston 12. The termination of the
refilling stroke of piston, 12 signaled by detection means 77,
deactivates switch means 114 and 132. However, fluid is not
delivered until the emptying stroke of piston 12 overcomes the back
pressure on outlet check valve 42 and piston seal compressibility,
liquid compressibility, chamber deformation and like phenomena,
generally referred to as "compliance". For a typical liquid
chromatographic system piston 12 must travel along its emptying
strokes approximately seven (7) micro-liters for a 140
kilogram/square centimeter back pressure, with a generally linear
increase thereafter. This period in piston 12's reciprocations is
called "pump-up".
At the beginning of pump-up, pump-up means 138 changes the speed of
motive means 20. Pump-up means encompasses pump-up gain means 142
which includes tachometer means 90 measuring the axial rotational
rate of shaft 73 and transforming this measurement of axial
rotation into a pulse signal received by frequency charge pump 118.
Gain means 144 which may be coupled with frequency charge pump 118
adjusts the amplitude of the pulse signal from the tachometer means
90 or the frequency charge pump 118 and transmits the amplitude
adjusted pulse signal to charge integrator 136. A ramp signal
results which feeds into comparitor means 140. Such a ramp signal
is proportional to shaft 73 rotation, cam 50 rotation or the linear
displacement of piston 12.
Comparitor means 140 utilizes comparitor 146 which also receives a
back pressure signal from pressure measuring means 148. The output
of comparitor 146 travels through "and" gate 150 while the charge
integrator 136 output increases but is less than the back pressure
signal, i.e.: during the pump-up period. The comparitor 146 outputs
adds an additional current to ground from summing node 116 via
pump-up speed control means 152. The "step-up" of pump-up speed
control increases the speed of motive means 20 until the ramp
signal substantially equals the back pressure signal from pressure
measuring means 148. This, of course, means that the piston 12 has
generated enough fluid pressure to overcome the back pressure on
outlet check valve 42, provided that gain means 144 has been
properly adjusted, and the pump mechanism 10 reverts to its normal
or constant filling speed. Integrator 136 stays high until the next
refilling cycle. There is essentially an instantaneous switch from
filling speed change to pump-up speed change to minimize or
eliminate any slack when fluid is not being delivered. Pump-up
speed control isolator 154 prevents activation of pump-up speed
control during normal operation.
Pump-up gain means 142 may increase or decrease the pump-up period
measured in piston linear displacement or in the angular rotation
of the shaft 73 for a given back pressure signal. Gain means 144
specifically increases or decreases the slope of the ramp signal to
this end. Changing the pump-up period is necessary to correct for
different liquid solvent viscosities, chromatographic column
resistance and other factors affecting flow rate.
Since the time span of filling and pump-up are finite, the desired
flow rate determined at the normal speed setting means 108 may not
equal the actual average flow rate from the outlet of chamber 14.
Thus "pump-up" may exceed the time when outlet check valve 42 opens
in some cases. Also, the back pressure on check valve 42 may drop
during filling and "pump-up" producing a slight pulse in the fluid
flow. Gain means 144 also reduces this pulse by matching the flow
rate setting with the actual flow rate delivered by mechanism
10.
The preferred embodiment is deemed to be drawn to a pressure signal
device alone or in combination with the heretofore described pump
mechanism 10. Pressure measuring means or torque measuring means
148 measures the torque on motive means 20 and transforms the same
into a measurement of back pressure associated with a fluid forcing
means such as piston 12 and chamber 14. Motive means 20 may include
a direct current electric motor in which case, the current
delivered to the motor would be proportional to the torque load on
the motor and therefore would be transformable into a measurement
of back pressure by pressure measuring means 148.
Means 158 for deactivating the motive means 20 at selected back
pressure values, either high or low or both, may take the form of a
high low pressure detector 160 with a limit indicator 162. High
pressure limiting means 164 may be provided with hysteresis means
164 for reactivating the motive means 20 when the back pressure
again falls within the selected working range.
Drive detector means 168 and time delay means 170 as well as
comparitor output 146 through inverter 172 and "and" gate 150 feed
to "and" gate 174. The output of "and" gate 174 and the output of
high low pressure detector 160 travel through "or" gate 176 and
inverter 178 to deactivate pressure measuring means, and form
blanking means 180. This prevents the measurement of pressure
during filling, pump-up and a coasting down period after pump-up
for a set time period, provided by time delay means 170.
Block diagram, FIG. 8, shows a variation of the invention 10, in
particular, control means 76. Detection means 77 could signal the
inception of the chamber filling stroke of piston 12 and may take
the form of the photon interruption flag 78 and associated elements
and other equipment structures previously described. However,
detection means 77 is shown as signaling the inception of the pump
out of fluid during the normal pumping period of piston 12. At this
time switch means 182 is "on" and switch means 184 is "off". Switch
means 182 and 184 may take the form of analog transmission gates.
At this point, the torque load on motive means 20 is constant and
proportional to the back pressure of the liquid being pumped.
Normal or constant speed setting means 108, previously delineated,
determines the speed of motive means 20 via servo summing amplifier
186 which produces an amplified error signal from the tachometer 90
and normal speed setting means 108 inputs.
During normal flow, a negative feedback loop 187, consisting of
summing amplifier 188, integrator 190 and switch means 182,
produces an average torque error signal at node 192 of zero.
Summing amplifier 188 compares the instantaneous motor current from
sensing resistor R-25, which is proportional to torque when motive
means 20 is a D.C. motor, to the output of integrator 190.
Integrator 190, in turn, receives the torque error signal of the
negative feedback loop 187 and an input from ground.
In other words, the output signal of integrator 190 equals the
average signal across the current sensing resistor R-25, during
normal pumping.
At the inception of the filling period detection means 77 cause
switch means 182 to turn "off" breaking the negative feedback loop
187, and freezing the output of integrator 190, to its last value.
Switch mens 184 is turned "on" via inverter 185. During filling,
the torque on motive means 20 greatly reduces such that the torque
signal input to summing amplifier 188 is less than the output
signal of integrator 190. The torque error signal i.e.: summing
amplifier 188 output, travels through switch means 184 to servo
summing amplifier 186. The addition of the torque error signal,
thereto, will cause motive means 20 to run at maximum speed because
of the large amplified error signal received from servo summing
amplifier 186.
At the end of refill, and the beginning of pump-up, the load on
motive means 20 increases and the torque error signal begins to
drop. As the load continues to increase the torque error signal
further decrease until motive means 20 begins to decrease. By the
end of the pump-up period, the torque error signal decreases to
zero and has no further effect on servo summing amplifier 186.
Therefore, motive means 20 returns to the normal speed for pumping
the fluid. Detection means 77 again signals the inception of the
normal pumping period which turns switch means 184 "off" and switch
means 182 "on".
Differentiator 194 produces a signal proportional to the
acceleration of motive means 20. This acceleration signal is
subtracted from the torque signal of R-25. The net result is a true
torque error signal to servo amplifier 186 during filling and
pump-up. As may be surmized the embodiment of FIG. 8 does not
require a compressibility adjustment necessitating gain means 144
in the prior embodiment.
Now considering the schematic circuit drawing FIG. 7 the following
Table I is a list of the elements found in the circuit with the
model number or values used in the preferred embodiment:
TABLE I ______________________________________ TABLE OF ELEMENTS
______________________________________ INTEGRATED CIRCUITS Z-1
National Semi-conductor LM 2907N Z-2 National Semi-conductor LM
339N Z-3 National Semi-conductor LM 324N Z-4 R.C.A. CD 4066 AE
(QUAD BILATERAL Switch) DIODES CR 3 through CR 17, IN 914 CR 22, CR
23, CR 24 CR 18, CR 19 MR 850 TRANSISTORS Q-3, Q-4 2N 930 Q-11 2N
5189 Q-9, Q-10 MPS 3638A Q-1, Q-8, Q-7, MPS 6531 Q-13 R.C.A. 2N6386
Q-2, Q-5, Q-6 M.P.S. 4355 Q-12 R.C.A. 40375 CAPACITORS C-16, C-19
15 .mu.f, 20 v C-4, C-9, C-12, 0.1 .mu.f, 50 v C-17, C-18 C-5 0.02
.mu.f, 100 v (.+-.20%) C-6, C-13 2.2 .mu.f 50 v (ceramic) C-7 C20
Pf .+-. 2.5% C-8 0.001 .mu.f .+-. 20% C-11 100 .mu.f, 50 v
(electrolytic) C-14 1.0 .mu.f C-15 0.01 .mu.f RESISTORS R-25, R-27
0.3 ohms, 2 w R-26 68 ohms, 2 w R-20 47 ohms, 1/4 w R-22 68 ohms,
1/4 w R-17 470 ohms, 1/4 w R-2, R-21, R-45, 1 Kohm, 1/4 w R-73,
R-28, R-18 1.5 Kohm, 1/4 w R-5, R-14 2.2 Kohms, 1/4 w R-29, R-43
3.3 Kohms, 1/4 w R-16 3.9 Kohms, 1.4 w R-9, R-41, R-49 4.7 Kohms,
1/4 w R-13, R-33, R-38, 10 Kohms, 1/4 w R-52, R-54, R-65, R-68,
R-69 R-51, R-53 15 Kohms, 1/4 w R-12, R-4, R-67 22 Kohms, 1/4 w
R-11, R-44, R-48, 30 Kohms, 1/4 w R-74. R-10, R-30 39 Kohms, 1/4 w
R-15, R-46 47 Kohms, 1/4 w R-64, R-8, R-34, 100 Kohms, 1/4 w R-70,
R-72 R-31 120 Kohms, 1/4 w R-14 200 kohms, 1/4 w R-39, R-40 220
Kohms, 1/4 w R-35 150 Kohms, 1/4 w R-42 390 Kohms, 1/4 w R-47 420
Kohms, 1/4 w R-7, R-6, R-71 10 Mohms, 1/4 w R-37 7.5 Kohms, 1/4 w
R-58 499 Kohms, 1/4 w R-59 12.1 Kohms, 1/4 w R-57 42.4 Kohms, 1/4 w
R-56 27 Mohms, 1/4 w R-3 560 ohms, 1/2 w R-41 4.7 Mohms, 1/4 w
R-32, R-55, R-60 10 Kohms, (trimpot) R-36 100 Kohms, (trimpot) R-50
10 Kohms, (trimpot) R-66 75 Kohms, 1/4 w R-101 10K, ratio 100/10.0
(Digital Potentiometer) R-102 10 Kohms R-103 10 Kohms MISCELLANEOUS
OD-1, OD-2 Optical Detector - G.E. photon coupled interrupter
Module # 13A1 T-1 Thermister 250 Kohms at 25.degree. C., 50 Kohms
at 70.degree. C. S-1 Electrical motor, permanent magnet motor, 1/30
H.P., 12 v D.C., amps, 0-3000 RPMs, 50:1 gear ratio. M-1 Meter, 0-1
milli amps (full scale) I-102 Light emitting diode #HP5082-4940-
44403 SW-1 Single pole single throw, slider switch. L-2 300 U
Henry, 3 amps. ______________________________________
The power inputs are denoted by a small circle with the approximate
voltage value in the vicinity of the power input, in volts D.C.
Normal speed setting means 108 may take the specific embodiment
shown where R - 101, a variable resistor combines with R - 58 and C
- 14 which act as a low pass filter that averages the alternating
current variations from a direct current signal i.e.: a pulse width
modulated signal. This is especially true when the signal comes
from a remote programer not shown. R - 55, R - 56, R - 6, and R -
57 inject a zero offset to normal speed setting means 108.
Therefore, the R - 55 zero setting becomes a true zero.
Voltage to current sink converter 110 corresponds to operational
amplifier Z - 3 - b in whose outputs enter Q - 4, a high gain
transistor. Q - 4's collector pulls current through R - 59 and R -
60 to match the inputs to amplifier Z - 3 - b. It should be noted R
- 60 is a variable resistor which may be used as a calibration
control for the voltage to current sink converter. R - 61 and CR -
7 combine to correct for non-linearity of the normal speed setting
means 108 and its flow rate determination because of the filling
means 79. This is especially useful at low flow rates where the
distortion is greatest.
R - 65 serves as the normal speed decoupling means 112. It has
equal voltage on the order of 7.5 volts on either side for
decoupling normal speed setting means 108 and pump-up means 138
when Z - 4 - b, which is first switch means 114, is turned "on" by
filling means 79.
The summing node 116 leads directly into Z- 1 which corresponds to
frequency charge pump 118, a frequency to current converter with
frequency doubling characteristics. Z - 1 also includes summing
amplifier 120, a high gain amplifier.
Tachometer means 90, OD - 1, sends to Z - 1, a pulsating current
whose frequency is proportional to the speed of motive means 20. R
- 4 serves as a pull-up load resistor while C - 4 acts as a
decoupling capacitor to block the D.C. component of the A.C. signal
coming from the chopping action of OD - 1. The A.C. signal passes
to Z - 1 and is referenced to ground through R - 67. C - 7
determines the quantity of charge delivered, for each axis crossing
of the A.C. signal, by the frequency charge pump 118; hence C - 7
determines the gain of the charge pump. R - 9 is a pull-down
resistor from the output of the summing amplifier 120 within
Z-1.
Frequency charge pump 118 passes current from Z - 1 to R 53 and
finally to summing node 116. Likewise, the output of summing
amplifier 120 with the aid of pull-down resistor R - 9 produces a
very small negative feedback current through R - 7 to summing node
116. CR 3, and Cr 4 are used for clamping limits on the error
signal at the summing node 116. In this case, the output of the
summing amplifier 120 and summing node 116 can not go below 7
volts. Thus the recovery time of the summing amplifier 120 is
reduced if it becomes overloaded.
C - 5, R - 8, and C - 6 determine the high frequency gain rolloff
characteristics. i.e.: the values have been predetermined such that
the whole servo loop does not oscillate and has proper damping
charcteristics as well as maximum response time. R - 5 provides a
pull-up current to a portion of the summing amplifier 120 within Z
- 1, R - 6 injects a small positive current into summing node 116
which adjusts R - 55 to a true zero value, as previously
discussed.
Summing amplifier 120 also feeds Z - 2 - C which comprises a part
of the generator section of pulse width modulator generator drive
126. The error signal from summing amplifier 120 in Z - 1 is
compared to a triangular wave signal from the triangular wave from
the generator composed of Z - 2 - b, in conjunction with passive
components C - 8, R - 11, R - 13, R - 10, R - 12, and CR 5. The
resulting output of Z - 2 - C is a pulse width modulated signal
which passes to the driver section of generator drive 126. The duty
cycle of the pulse width modulated signal is directly proportional
to the error signal from amplifier 120.
Q - 8, Q - 9, Q - 10 and Q - 11 drive Q - 12 "on" and "off"
synchronously at a very fast rate. R - 19 is a pull-up resistor for
Z - 2 - C while C - 19 filters the power supplied, thereto. R - 20
functions to limit the peak current through Q - 8. When Q - 8 goes
"on", Q - 9 turns "off", thus Q - 8 and Q - 9 are complimentary.
The pulse width modulated signal, having a frequency of about 25
Kilohertz, is initially high and positive, flowing current through
CR - 15, and C - 9, R - 21, R - 22, Q - 10, and to the base of Q -
11.
Q - 10 bypasses to ground, through CR - 16, any excess current
exceeding approximately 10 milliamperes coming from Q - 8. The
current through R - 22, the portion not bypassed, passes to the
base of Q - 11 turning it off. The limiting action of Q - 10
prevents Q - 11 from being overdriven on initial turn on, allowing
it to turn off more quickly. After the charge-up of C - 9, R - 21
limits the drive current through Q - 8 to approximately 10
milliamperes such that Q - 10 bypasses essentially no current to
ground after the charge up period C - 9, Q - 12 turns on within a
time period of 200 nanoseconds from the beginning of the turn on
sequence causing the voltage on its collector to reach a low value.
When the pulse width modulated signal goes low, Q - 9 turns "on"
and Q - 8 turns "off" allowing the voltage at the emitter of Q - 9
(top of C - 9) to go low. C - 9 supplies a source of negative bias
in order to sink large currents very rapidly from the bases of Q -
11 and Q - 12 through CR - 17. This turns Q - 11 and Q - 12 "off"
very rapidly permitting the voltage on the collectors of Q - 11 and
Q - 12 to go high. This "on"-"off", high/low sequence takes place
at a relatively high frequency of 25 kilohertz which eliminates any
audio sounds eminating from motive means 20. The need of a large
heat sink to dissipate heat from Q - 12 is eliminated because of
high/low switching which takes place in 200 nanoseconds, as
heretofore described.
The embodiment described also performs current limiting through Q -
12 using current sensing resistor R - 27 and Z - 2 - d and its
associated circuiting. Z - 2 - d is a comparitor which compares a
reference voltage, established by R - 14, R - 15, and R - 16, and a
signal voltage developed cross C - 15. Such a signal voltage
averages the voltage drop across the current sensing resistor R -
27, with a weighted dual time constant originating from R - 17, R -
18, and CR - 12. For instance, when the voltage drop across R - 27
exceeds the voltage across C - 15, CR - 12 is forward biased so
that R - 17 determines the time constant with C - 15. A typical
value would be 4.7 microseconds in this case. On the other hand,
when the voltage drop across R - 27 is less than the voltage across
C - 15, CR - 12 is reversed biased so that R - 17 and R - 18
determines the time constant with C - 15 e.g.: 20 microseconds.
When the signal voltage exceeds the reference voltage in comparitor
Z - 2 - d, the output of comparitor Z - 2 - d overrides the pulse
width modulated signal from Z - 2 - c, thereby shutting down the
driver section of 126. R - 15 drops the reference voltage to a low
level which guarantees the driver will remain "off" for about 30
microseconds. When the signal from C - 15 is discharged below the
lowered reference signal, Z - 2 - c is re-enabled to reactivate the
driver section of 126. The "on- off" action of this current
limiting occurs at an ultrasonic frequency of about 25 kilohertz
again, preventing disturbing sympathetic sonic frequencies from
arising. Current limiting may occur at a value of about 4 amps
measured through R - 27.
L - 2 and C 11, a low pass filter, react slowly to current changes
from the driver section of 126, and thereby convert the pulse width
modulated signal therefrom to a D.C. signal supplied to S - 1. R -
26, Q - 13, and CR 19 form a dynamic break to prevent overspeeding
of S - 1. In other words, when CR 19 is forward biased, Q - 13 is
"off" and the L - 2 and C - 11 combination runs S - 1. In other
words, when CR 19 is forward biased, Q - 13 is "off" and the L - 2
and C - 11 combination runs S - 1. However, if the D.C. voltage
generated by motor S - 1 exceeds the D.C. supplied across C - 11,
CR - 19 will reverse bias and Q - 13 goes "on" thereby short
circuiting and braking S - 1. The CR 18 diode clamps the voltage on
the collectors of Q - 11 and Q - 12 to the 35 volt source, when Q -
12 is turned off.
Pressure measuring means 148 employs current sensing resistor R -
25 which effectively measures the current load on S - 1. This
current load is proportional to the torque load on S - 1 which is
proportional to the back pressure exerted on mechanism 10, which
may include fluid forcing means as previously described in FIGS. 1
and 2. A motor current sensing common emitter amplifier is embodied
by Q - 6 and accompanying resistors R - 28, R - 30, R - 32, and R -
33, Q - 7 and R - 31 form a current biasing network for Q - 6. C -
17 and R - 29 filter high frequency noise from the current
amplification at this point.
T - 1 reduces the gain of the pressure sensing amplifier Q - 6, as
the torque constant of S - 1 decreases with increased
temperature.
R - 30 serves to limit the potential across the R - 32 pot to 15
volts, consequently R - 32 serves as a span adjustment for meter M
- 1, which will be hereinafter discussed.
Signal conditioning of the signal from R - 32 is provided by low
pass filter R - 34, R - 70, and C - 16. This R - C element may have
a time constant of about 3 seconds. Z - 4 - D is a switch that
maintains the charge on C - 16 when in the "off" position. The
charge on C - 16 represents the average voltage at R - 32 i.e.: the
output of the motor current sense amplifier Z - 3 - d is a non
inverting unity gain amplifier which subtracts an adjustable offset
due to R - 36. The output of Z - 3 - d equals zero volts, by the
adjustment of R - 36; no back pressure is found on piston 2 at this
point. Meter M - 1 and R - 37 provide a pressure readout.
Switch Z - 4 - d will turn off during filling, pump-up, and a time
period following pump-up where the piston coasts down to a normal
speed. This aspect of the invention shown on FIG. 6 as blanking
means will be fully explained hereafter.
High/low pressure detector 160 includes an upper limit voltage
setting means R - 102 and a lower limit voltage setting means R -
103. Z - 3 - C compares the upper limit to lower limit through
resistors R - 39, R - 40, R - 41 and R - 42. CR - 13 and CR 14 are
forward biased between upper limit pot R - 102 and lower limit pot
R - 103. The output of Z - 3 - C remains low when the upper limit
input is greater than the lower limit input, and the pressure
voltage at the Z - 3 - d output is within such limits. When the
output of Z - 3 - d exceeds the upper limit, CR 13 reverse biases
causing the output of Z - 3 - C to go high, activating first
switching means 114. R - 65 becomes shorted stopping motive means
20. When the pressure on the system reduces, R - 38, R - 40, R - 41
and R - 42, comprising hysteresis means of high pressure limiting
means 164, restart motive means 20. When the output of Z - 3 - d
goes below limit voltage, CR 14 reverse biaser causing Z - 3 - c
output to go high shutting off motor S - 1. R - 103 is then
adjusted to restart motor S - 1. Limit indicator 162 is formed by R
- 43 and light emitting diode I - 102.
Filling means 79 includes detection means 77, which encompasses
photon intercepting flag 78 and module 80. OD-2 represents flag 78
and module 80. Z - 3 - A and R - 47, a noise supressor, would
function as filing amplifier 128. SW - 1 is a switch to disable
detection means 77. The generated signal from OD-2 in conjunction
with filling amplifier 128 turns on Z - 4 - B, first switching
means 114, through CR 10 and R - 44 which compose "OR" gate 130.
Thus, R - 66 determines the speed of S - 1 during filling, since R
- 65 has equal potential on either side. Also, the output of Z - 3
- A enters Q - 1, through current limiting reistor R - 48, which
sets C - 13 to a low value (i.e.: zero). C - 13 would be an
embodiment of charge integrator 136. The output of Z - 3 - A
controls Z - 4 - C, which is turned "on" by the flag intercepting
the photon beam in module 80. Z - 4 - C and Z - 2 - A serve as
"and" gate 150 and inverter 172. CR 22 and R - 73 form "and" gate
174. CR 23 and R - 74 comprise "OR" gate 176 and inverter 178. R -
54 is a passive pull-up resistor to maintain a positive voltage on
Z - 4 - C when Z - 2 - A and Z - 4 - C are off. Thus, a blanking
signal to Z - 4 - D results during fast refill, deactivating
pressure measuring means 148, as previously discussed. When such a
blanking signal is received by Z - 4 - D, holding means C - 16 will
hold the value of the current sense amplifier previously described
in conjunction with Q - 6 at R - 32. The result will be a steady
pressure reading on pressure measuring means 148 during the refill
and pump-up period of the cycle of piston 12.
As soon as the flat 78 signals the end of the filling period,
pump-up will begin. A ramp signal will be produced and sent to Z -
2 - A which corresponds to comparitor 146. A second signal from Z -
3 - D indicates the back pressure on the mechanism 10. The advent
of pump-up removes R - 66 from motor speed determination and
substitutes the R - 64 and R - 65 combination. In other words, the
preferred embodiment adds a step to the normal speed setting during
pump-up. Also, Z - 4 - D receives another blanking signal via CR
22, and reacts as during the filling sequence. After pump-up has
been completed C - 18 will continue the blanking signal for a set
time period to prevent pressure measurement during the "coasting
down" of motor S - 1 to the normal speed setting and normal flow
rate delivery.
The ramp signal arriving at Z - 2 - A is generated by Q - 2 and Q -
3 and resistors R - 49, R - 50, and R - 52, which form a current
mirror that tracks the current flow from the Z - 1 frequency charge
pump, flowing through R - 53. These combined elements form pump-up
gain means 142. R - 50 corresponds to gain means 144 for the
amplitude adjustment of the pulse signal of frequency charge pump
118 of Z - 1.
During high or low limiting CR - 23 gurantees that switch Z - 4 - d
is on, preventing "latch-up" of high pressure limiting means 160.
Thus, high pressure limiting means resets automatically.
While in the foregoing specification embodiments of the invention
have been set forth in considerable detail for purposes of making a
complete disclosure of the invention, it will be apparent to those
skilled in the art that numerous changes may be made in such
details without departing from the spirit and principles of the
invention.
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