U.S. patent number 3,726,613 [Application Number 05/080,115] was granted by the patent office on 1973-04-10 for pulsefree peristaltic pump.
Invention is credited to Wolf von Casimir.
United States Patent |
3,726,613 |
von Casimir |
April 10, 1973 |
**Please see images for:
( Certificate of Correction ) ** |
PULSEFREE PERISTALTIC PUMP
Abstract
To smooth the pulsations in the flow rate of a fluid conveyed by
a peristaltic pump, a cam-controlled pusher is synchronized with
the driving elements (rollers or plungers) acting upon the wall of
a flexible tube to constrict that wall, at a location downstream of
the driving elements, when these elements advance the fluid toward
the tube outlet and to allow its expansion at the beginning of
every new operating cycle when a new pressure wave is initiated at
a location remote from that outlet.
Inventors: |
von Casimir; Wolf (Munich,
DT) |
Family
ID: |
22155356 |
Appl.
No.: |
05/080,115 |
Filed: |
October 12, 1970 |
Current U.S.
Class: |
417/477.1 |
Current CPC
Class: |
F04B
11/0075 (20130101); F04B 43/082 (20130101); F04B
43/1253 (20130101) |
Current International
Class: |
F04B
11/00 (20060101); F04B 43/08 (20060101); F04B
43/12 (20060101); F04B 43/00 (20060101); F04b
043/08 (); F04b 043/12 (); F04b 045/06 () |
Field of
Search: |
;417/474,475,476,477 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Freeh; William L.
Assistant Examiner: Gluck; Richard E.
Claims
I claim:
1. A peristaltic pump comprising:
a tube provided with a flexible wall having an inlet for a fluid to
be conveyed, an outlet for said fluid and an operating zone between
said inlet and outlet;
driving means periodically engageable with said tube along said
operating zone for deforming the wall thereof to advance said fluid
toward said outlet in a series of recurrent operating cycles, said
driving means comprising a set of driving elements and shaft means
for intermittently moving each driving element into contact with
said tube to obstruct same completely at a point advancing from
said inlet toward said outlet in the course of an operating
cycle;
a pusher movable substantially at right angles to the wall of said
tube at a location downstream of said zone, said pusher being
capable of only a partial blocking effect; and
cam means synchronized with said driving means for actuating said
pusher to constrict said tube upstream of said outlet at a stage of
each operatinc cycle in which the driving element closest to said
pusher is substantially fully withdrawn from said wall for
progressively allowing the tube to expand at said location during
the remainder of an operating cycle, thereby smoothing the flow of
said fluid through said outlet.
2. A pump as defined in claim 1 wherein said cam means is mounted
on said shaft means.
3. A pump as defined in claim 2 wherein said driving elements are a
plurality of rollers and a rotatable support therefor coaxially
mounted with said cam means for moving each roller in contact with
said tube along an arc centered on said shaft means.
4. A peristaltic pump comprising:
a tube provided with a flexible wall having an inlet for a fluid to
be conveyed, an outlet for said fluid and an operating zone between
said inlet and outlet, said operating zone being substantially
semicircularly curved about an axis;
a support rotatable about said axis;
a pair of diametrically opposite driving rollers mounted on said
support for alternate engagement with said tube along said
operating zone for deforming the wall thereof to advance said fluid
toward said outlet in a series of recurrent operating cycles by
obstructing said tube completely at a point advancing from said
inlet toward said outlet in the course of an operating cycle;
a pusher movable substantially at right angles to the wall of said
tube at a location downstream of said zone with a partial blocking
effect; and
cam means on said shaft for actuating said member to constrict said
tube upstream of said outlet at the beginning of each operating
cycle and for progressively allowing the tube to expand at said
location during the remainder of an operating cycle, thereby
smoothing the flow of said fluid through said outlet.
Description
My present invention relates generally to the art of pumping
liquids or gases with peristaltic pumps.
Conventional peristaltic pumps exhibit a disadvantageous
retardation or even interruption of the flow at the exit each time
one roller rolls off the tube and the next roller takes over the
pumping action. Peristaltic pumps having several pushers which
compress the tube in a caterpillar-like motion have the same
shortcoming of pulsations. This is caused by the necessity of
filling the reexpanding tube when the pumping component loses
contact with the hitherto compressed tube.
According to the invention this drawback of the prior art is
overcome by introducing a simple device, preferably a cam-operated
pusher, which exerts an external pressure on the tube downstream
from the pump proper, so that an appropriate compensatory pumping
motion can be superimposed on the fluctuating forward motion of the
pumped fluid. In the course of an operating cycle this device does
not really pump but merely regulates, thus preventing undesired
pulsations.
In the accompanying drawing:
FIG. 1 shows a peristaltic pump equipped with a cam-actuated pusher
according to the invention;
FIGS. 2a to 2d show diagrammatically the movements of the essential
components of the pump;
FIGS. 3a 3c help to explain the cooperation of the rollers and the
pusher by showing the different pumping speeds as a function of the
angular position of the rollers and of the position of the plunger;
and
FIG. 4 shows schematically another embodiment of my invention.
As shown in FIG. 1, a pump embodying my invention comprises a case
7 with a groove for a flexible tube 4. On a shaft 10 there are
mounted a cam 11 and a rotating arm 12 bearing two rollers 1 and 2
which roll along the tube 4 along a semicircular section of the
groove. A little roller 8 transmits its motion, governed by the
contour of the cam 11, to a pusher 3 by means of a lever 9 which is
pivoted on a pin 13. A removable cover which is not shown and which
is put on the front of the case 7 serves for keeping the tube 4 in
its position in the groove.
If the pump is driven in the rotary direction indicated by the
arrows in FIG. 1 and in FIGS. 2a to 2d, the i.e. counterclockwise,
the fluid to be pumped is sucked in at an inlet 5. Then it is
propelled over the semicircular section of the tube 4 toward the
spot where the pusher 3 partially compresses the tube 4. After
passing this spot the medium leaves the pump via an exit 6.
The respective motions of the essential components, i.e. of the
rollers 1 and 2 and of the pusher 3, during an operating cycle are
shown in FIGS. 2a to 3d.
If the pusher 3 does not operate the roller 1 produces a pumping
speed or delivery rate W(.phi.) as a function of its angular
position .phi. as shown in FIG. 3a. The dip indicates the
retardation of the flow at the exit 6 of the pump. This retardation
is caused by the necessity of filling the reexpanding section of
the tube 4 when the roller 1 moves off as it turns from position
.phi..sub.b via .phi..sub.c to .phi..sub.d. After the roller 1 has
lost contact with the tube 4, i.e. after passing through position
.phi..sub.d, the pumping speed rate W(.phi.) is again at its normal
level produced by the rollers 1 and 2 when rolling along the
semicircular section of the tube 4.
The pusher 3 has to compensate the retardations of the flow. This
is effected by forming the contour of the cam 11 in such a way that
a supplemental pumping rate I(.phi.) results, which is shown in
FIG. 3b and which is measured at the exit 6 if the rollers 1 or 2
do not operate.
From FIG. 3b it will be seen that the pumping rate I(.phi.) assumes
both negative and positive values. The volume of fluid admitted to
the reexpanding constriction of the tube 4, following the downward
motion of the pusher 3, is exactly equal to the positively
displaced volume due to the upward motion of the pusher 3
coinciding with the angular motion of the roller 1 from .phi..sub.b
via .phi..sub.c to .phi..sub.d. In the course of a cycle the pusher
3 in fact, does not pump but merely regulates. This cooperation of
the rollers 1 and 2 with the pusher 3 may be compared with the
behavior of a pressure accumulator: the pusher 3 holds back some of
the fluid while the rollers 1 and 2 are working with full pumping
speed, and restores it to the mainstream when the roller-pumped
supply is reduced to its minimum volume.
More particularly, the shape of the cam 11 illustrated in FIG. 1 is
such that, as shown, its radius has a minimum value at the two
points engaged by the follower 8 at the instants when the rollers 1
and 2 restart the operating cycle every 180.degree. of rotation by
initiating a new pressure wave at a location remote from outlet 6,
i.e. at the point of contact between tube 4 and roller 2 in the
depicted position. With the cam rotating counterclockwise, follower
8 rides up one of its two diametrically opposite humps to a point
of maximum radius; its radius then decreases progressively for
almost half a circle, thereby generating the negative pressure
which gives rise to the negative velocity component shown in FIG.
3b. Thus, the tube outlet 6 is partially blocked by the pusher 3,
located downstream of the zone of engagement of the tube wall with
driving elements 1, 2, at the very instant when roller 2 goes into
action to generate additional pressure in the direction of flow;
gradually, thereafter, this outlet is unblocked so that the excess
fluid stored at the moment of blocking in the downstream tube
portion can flow out at a controlled rate.
As will be seen from FIG. 3c, the superposition of the pumping
speed W(.phi.) of the rollers 1 and 2 and the compensatory pumping
rate I(.phi.) of the pusher 3 establishes a pulsation-free pumping
rate L which does not the angle .phi. but merely on the rotary
velocity d.phi./dt of the pump.
The exact mathematical formulation of these relationships is as
follows: to the time-dependent pumping speed W(.phi.) of the pump
another pumping speed I(.phi.) is added which conforms, at every
instant t during the time interval from t.sub.1 to t.sub.2 of an
operating cycle, to the equations ##SPC1##
This enables everybody skilled in the art to find out the contour
of the cam 11 by measuring the curve W(t) or W(.phi.), then
determining I(.phi.) preferably graphically, and reproducing step
by step the position of the pusher 3 and the position of the
cam-follower roller 8 which governs in this experiment the contour
of the cam to be determined.
A peristaltic pump of another type is shown in FIG. 4. The flexible
tube 4' is compressed in a caterpillar-like motion by several
plungers 1',2',3', ...; plunger 1' for instance is actuated via a
bar 12' by a cam 12", the latter being mounted on a shaft 10'
together with the cams of the other plungers. The shaft 10' also
drives the cam 11' which effects the compensatory motion of the
pusher 3'. Thus a steady pumping speed is attained, according to
the invention, at the exit 6'.
Peristaltic pumps according to the invention may also be used as
constant-rate suction pumps within the given limitations of the
deformability of flexible tubes by suction. If steady pumping in
either direction is desired, another pusher working on the other
side of the pump proper has to be provided.
In all fields of medical, chemical and biochemical research or
industries where constant-rate delivery and of sensitive or active
fluids is desired, the aforedescribed peristaltic pump as shown in
FIG. 1 is advantageous because of its simple structure as well as
of the easy way the tube can be fitted into the pump or the pump
can be installed in or removed from a closed-flow system without
disconnecting any tube involved. This is very important for
instance where sterile conditions are to be maintained.
* * * * *