Abstrict This invention relates to a positive displacement flow meter or
pump comprising a plurality of spherical balls orbitably entrained
in a toroidal cavity. The first segment of the toroidal cavity tangentially
connecting a fluid inlet to a fluid outlet comprises the flow passage
for the fluid being measured or pumped and the second segment provides
the return pass for the spherical balls. A rotating magnetic field
about the line of axisymmetry of the toroidal cavity generates the
orbiting movement of the spherical balls for measuring the flow
rate or for pumping.
Claims We claim:
1. A ball bearing pump-flow meter comprising in combination:
(a) a closed loop cavity having a circular cross section;
(b) a first port merging into said closed loop cavity;
(c) a second port merging into said closed loop cavity wherein
said first and second ports merging into said closed loop cavity
divides said closed loop cavity into a flow passage segment and
a return-pass segment;
(d) a plurality of spherical balls having a diameter slightly smaller
than the diameter of said circular cross section of said closed
loop cavity, said plurality of spherical balls orbitably entrained
in said closed loop cavity;
(e) a rotating magnetic field rotating about an axis substantially
perpendicular to a plane including said closed loop cavity, wherein
said rotating magnetic field produces a force on said plurality
of spherical balls substantially tangential to said closed loop
cavity in a direction from said first port to said second port in
said flow passage segment of said closed loop cavity and in a direction
from said second port to said first port in said return pass segment
of said closed loop cavity, said force generating an orbiting movement
of said plurality of spherical balls in a direction from said first
port to said second port in said flow passage segment of said closed
loop cavity and in a direction from said second port to said first
port in said return-pass segment of said closed loop cavity;
(f) a stationary braking magnetic field included in said return-pass
segment of said closed loop cavity adjacent to said second port,
wherein said stationary braking magnetic field provides a force
acting in a general direction from said first port to said second
port in said return-pass segment of said closed loop cavity and
provides a braking on said orbiting movement of said plurality of
spherical balls moving from said second port to said first port
in said return-pass segment of said closed loop cavity;
wherein said plurality of spherical balls under an acceleration
in a vicinity of said first port draw the fluid from said first
port into said flow passage segment of said closed loop cavity and
said plurality of spherical balls under a deceleration in a vicinity
of said second port force out the fluid from said flow passage segment
of said closed loop cavity into said second port.
2. The combination as set forth in claim 1 wherein means for measuring
the frequency of said plurality of spherical balls orbiting in said
closed loop cavity is included; whereby, information from said means
is calibrated to a rate of flow.
3. The combination as set forth in claim 1 wherein means for varying
the rate of rotation of said rotating magnetic field is included;
whereby, the rate of flow through said ball bearing pump-flow meter
is controllable by said means for varying the rate of rotation of
said rotating magnetic field.
4. The combination as set forth in claim 2 wherein means for varying
the rate of rotation of said rotating magnetic field is included;
whereby, the rate of flow through said ball bearing pump-flow meter
is controllable by said means for varying the rate of rotation of
said rotating magnetic field.
5. A ball bearing flow meter-flow controller comprising in combination:
(a) a closed loop cavity having a circular cross section;
(b) a first port merging into said closed loop cavity;
(c) a second port merging into said closed loop cavity wherein
said first and second ports merging into said closed loop cavity
divides said closed loop cavity into a flow passage segment and
a return-pass segment;
(d) a plurality of spherical balls having a diameter slightly smaller
than the diameter of said circular cross section of said closed
loop cavity, said plurality of spherical balls orbitably entrained
in said closed loop cavity;
(e) a rotating magnetic field rotating about an axis substantially
perpendicular to a plane including said closed loop cavity, wherein
said rotating magnetic field produces a force on said plurality
of spherical balls substantially tangential to said closed loop
cavity in a direction from said first port to said second port in
said flow passage segment of said closed loop cavity and in a direction
from said second port to said first port in said return pass segment
of said closed loop cavity, said force generating an orbiting movement
of said plurality of spherical balls in a direction from said first
port to said second port in said flow passage segment of said closed
loop cavity and in a direction from said second port to said first
port in said return-pass segment of said closed loop cavity;
whereby, said plurality of spherical balls under an acceleration
in a vicinity of said first port draw the fluid from said first
port into said flow passage segment of said closed loop cavity and
said plurality of spherical balls under a deceleration in a vicinity
of said second port force out the fluid from said flow passage segment
of said closed loop cavity into said second port.
6. The combination as set forth in claim 5 wherein means for measuring
the frequency of said plurality of spherical balls orbiting in said
closed loop cavity is included; whereby, information from said means
is calibrated to a rate of flow.
7. The combination as set forth in claim 5 wherein means for varying
the rate of rotation of said rotating magnetic field is included;
whereby, the rate of flow through said ball bearing flow meter-flow
controller is controllable by said means for varying the rate of
rotation of said rotating magnetic field.
8. The combination as set forth in claim 6 wherein means for varying
the rate of rotation of said rotating magnetic field is included;
;whereby, the rate of flow through said ball bearing flow meter-flow
controller is controllable by said means for varying the rate of
rotation of said rotating magnetic field.
Description BACKGROUND OF THE INVENTION
As the present-day chemical and pharaceutical industries become
ever-increasingly automated, there is a great demand of means for
acccurately measuring the flow rate or the total amount of flow
over a given time period. The most desirable type of flow meter
is the positive displacement flow meter, which provides a means
for measuring a flow with high accuracy and reliability. Few positive
displacement flow meters are commercially available today and positive
displacement flow meter technology is virtually nonexistent at the
present time.
The primary object of the present invention is to provide a positive
displacement flow meter comprising a train of spherical balls orbitably
entrained in a toroidal cavity wherein a magnetic field rotating
about the axis of axisymmetry of the toroidal cavity and the fluid
flow jointly generates the orbiting movement of the spherical balls.
Another object is to provide a positive displacement pump including
a train of spherical balls orbitably entrained in a toroidal cavity
wherein a rotating magnetic field generates the orbiting movement
of the spherical balls in the first segment of the toroidal cavity
comprising the flow passage and a stationary magnetic field produces
a braking on the orbiting movement of the spherical balls in the
second segment of the toroidal cavity.
A further object is to provide a positive displacement flow meter
or a positive displacement pump including the guides across the
inlet and outlet openings into the toroidal cavity that enhances
a continuous and smooth orbiting movement of the spherical balls.
Yet another object is to provide a positive displacement flow meter
that functions as a flow meter as well as a flow controlling device.
Yet a further object of the present invention is to provide a positive
displacement pump which requires no seals.
Still another object is to provide a positive displacement flow
meter or a positive displacement pump with a simple and a compact
construction.
Still a further object is to provide a positive displacement flow
meter or a positive displacement pump which is inexpensive.
These and other objects of the present invention will become clear
as the description thereof proceeds.
BRIEF DESCRIPTION OF FIGURES
The present invention may be described with great clarity and specificity
by referring to the following Figures:
FIG. 1 illustrates a cross section of a ball bearing pump constructed
in accordance with the principles of the present invention.
FIG. 2 illustrates another cross section of the ball bearing pump
of FIG. 1 taken along a plane 2--2 as shown in FIG. 1.
FIG. 3 illustrates a further cross section of the ball bearing
pump of FIG. 1 taken along a plane 3--3 as shown in FIG. 1.
FIG. 4 illustrates a cross section of another embodiment of the
ball bearing pump.
FIG. 5 illustrates another cross section of the ball bearing pump
of FIG. 4 taken along a plane 5--5 as shown in FIG. 4.
FIG. 6 illustrates a cross section of a further embodiment of the
ball bearing pump.
FIG. 7 illustrates another cross section of the ball bearing pump
of FIG. 6 employing the rotating magnets in creating a rotating
magnetic field, which cross section is taken along a plane 7--7
as shown in FIG. 6.
FIG. 8 illustrates a cross section of the ball bearing pump of
FIG. 6 employing the stationary magnets in creating a rotating magnetic
field, which cross section is taken along the same plane as that
of FIG. 7.
FIG. 9 illustrates an end view of a magnetic core usable in conjunction
with the arrangement shown in FIG. 7 or in FIG. 8.
FIG. 10 illustrates an end view of another magnetic core usable
in conjunction with the arrangement shown in FIG. 7 or in FIG. 8.
FIG. 11 illustrates a cross section of a ball bearing flow meter
constructed in accordance with the principles of the present invention.
FIG. 12 illustrates another cross section of the ball bearing flow
meter of FIG. 11 taken along a plane 12--12 as shown in FIG. 11.
FIG. 13 illustrates a cross section of another embodiment of the
ball bearing flow meter taken along the same plane as that of FIG.
12.
FIG. 14 illustrates a cross section of a further embodiment of
the ball bearing flow meter.
FIG. 15 illustrates another cross section of the ball bearing flow
meter of FIG. 14 taken along a plane 15--15 as shown in FIG. 14.
FIG. 16 illustrates an end view of a stationary magnet with toroidal
core employed to create a rotating magnetic field.
FIG. 17 illustrates a cross section of a pair of magnets with the
toroidal core sandwiching the toroidal cavity of a ball flow meter
in mirror image to one another.
FIG. 18 illustrates an end view of a coaxial arrangement of a stationary
magnet with an annular core and a central core providing an annular
gap to receive the toroidal cavity of a ball bearing flow meter.
FIG. 19 illustrates a cross section of a ball bearing flow meter
wherein the axis of rotation of the rotating magnets is off-set
from the axis of axisymmetry of the toroidal cavity of the flow
meter.
FIG. 20 illustrates a cross section of another ball bearing flow
meter wherein the axis of rotation of the rotating magnets is off-set
from the axis of axisymmetry of the toroidal cavity of the flow
meter.
SPECIFICATION
In FIG. 1 there is shown a cross section of a ball bearing pump
taken along a plane including the center line of the toroidal cavity
or the closed loop cavity. A plurality of the spherical balls 1
are orbitably entrained in series within a toroidal cavity or a
closed loop cavity 2. The cross section of the toroidal cavity 2
is a circle with a diameter slightly larger than the diameter of
the spherical balls 1; whereby, only little amounts of fluid can
leak across each of the spherical balls 1 while each of the spherical
balls 1 is allowed to orbit following the toroidal cavity 2. The
toroidal cavity 2 is divided into two segments; the first segment
3 connecting the first port 4 and the second port 5 tangentially
providing a fluid passage from one port to the other port, and the
second segment 6 providing a return pass for the spherical balls
1. A sensor 7 sensing each of the spherical balls passing by is
installed adjacent to the outer wall of the toroidal cavity 2 on
the first segment side. A stationary magnet 8 providing braking
on the orbiting spherical balls 1 is installed on the second segment
side.
In FIG. 2 there is shown another cross section of the ball bearing
pump of FIG. 1 taken along a plane 2--2 as shown in FIG. 1. The
opening 9 of the port 4 into the toroidal cavity 2 is provided with
a guide 10 having a guiding edge commensurate with the outer perimeter
of the toroidal cavity, that enhances the orbiting movement of the
spherical balls. The opening of the port 5 into the toroidal cavity
also includes such a guide.
In FIG. 3 there is shown a further cross section of the ball bearing
pump of FIG. 1 taken along a plane 3--3 as shown in FIG. 1. The
toroidal cavity 2 is coaxially disposed adjacent to rotating magnets
11 12 etc., which creates a rotating magnetic field wherein the
flux lines of the rotating magnetic field traverse across the toroidal
cavity. The rotating magnetic field creates the orbiting movement
of the spherical balls by induction, reluctance or hysteresis. The
spherical balls may be made of solid or hollow stainless steel or
carbon steel, copper, aluminum with plastic lining depending on
the type of magnetic orbiting. The spherical balls may be stainless
steel or plastic balls with a permanent magnetic bar or carbon steel
bar embeded inside of the spherical balls. The stationary magnetic
field across the toroidal cavity created by the stationary magnet
8 disposed at the second segment of the toroidal cavity, puts a
braking effect on the orbiting motion of the spherical balls driven
by the rotating magnetic field created by the rotating magnets 11
12 etc.
With the arrangement as shown in FIGS. 1 and 2 the spherical balls
experience acceleration in the vicinity of one of two port openings
into the toroidal cavity and experiences deceleration in the vicinity
of the other of two port openings depending on the direction of
the orbiting motion of the spherical balls. When the spherical balls
are accelerated in the vicinity of the first port 4 the distance
between two adjacent spherical balls increases and, consequently,
the fluid is drawn into the first segment 3 of the toroidal cavity
2 from the port 4. When the spherical balls are decelerated in the
vicinity of the second port 5 the distance between two adjacent
spherical balls decreases and, consquently, the fluid is forced
out from the first segment 3 of the toroidal cavity 2 into the second
port 5. Since there is only a little amount of fluid leaking across
each of the spherical balls, the fluid has to move with the orbiting
spherical balls and, consequently the ball bearing pump shown in
FIGS. 1 and 2 functions as a positive displacement pump. The pumping
rate can be obtained by counting the frequency of the spherical
balls passing by the sensor 7 and calibrating such information into
an actual volume flow rate or mass flow rate.
In FIG. 4 there is illustrated a cross section of another embodiment
of the ball bearing pump comprising a plurality of spherical balls
13 a toroidal cavity 14 a pair of ports 15 and 16 and a ball
counter 17 arranged in the same manner as that of the combination
shown in FIG. 1. The stationary braking magnet 18 is disposed at
the return-pass side of the toroidal cavity adjacent to the outer
wall of the toroidal cavity on a plane including the center line
of the toroidal cavity, which arrangement allows a sandwiching of
the toroidal cavity 14 with a pair of rotating magnet as shown in
FIG. 5.
In FIG. 5 there is shown another cross section of the ball bearing
pump of FIG. 4 taken along a plane 5--5 as shown in FIG. 4. A pair
of rotating magnets with multiple poles 19 and 20 sandwiches the
toroidal cavity 14 in a coaxial relationship, which arrangement
generates a strong rotating magnetic field with fluxes traversing
across the toroidal cavity 14.
In FIG. 6 there is illustrated a cross section of a further embodiment
of the ball bearing flow meter including the spherical balls 21
a toroidal cavity 22 and a pair of ports 23 and 24. The ports 23
and 24 are connected to the toroidal cavity 22 in a 45 degree angle
with respect to the plane including the center line of the toroidal
cavity.
In FIG. 7 there is shown another cross section of the ball bearing
pump of FIG. 6 taken along a plane 7--7 as shown in FIG. 6. The
rotating magnet 25 with multiple poles are rotatably disposed adjacent
to the toroidal cavity 22. The poles 26 27 etc., of the rotating
magnet 25 are disposed in the first quadrant of the cross section
of the toroidal cavity. The central core 28 with a centrally located
circular hole 29 has its rim extending towards to the toroidal cavity
22 in the third quadrant of the cross section of the toroidal cavity.
The poles of the braking magnet 30 installed on the return-pass
side of the toroidal cavity occupies the second and fourth quadrant
of the cross section of the toroidal cavity wherein the C-shaped
core of the braking magnet extends through the hole 29 centrally
disposed through the central core 28. The port 23 and 24 extends
out from the toroidal cavity 22 in the second quadrant of the cross
section of the toroidal cavity. The central core 28 may be arranged
to rotate with the rotating magnet 25 or to be stationary.
In FIG. 8 there is illustrated a cross section of yet another
embodiment of the ball bearing pump similar to that shown in FIG.
6 which cross section is taken along the same plane as that of
FIG. 7. In this arrangement, the rotating magnetic filed is created
by a series of electric coils 31 32 33 etc., wound around a stationary
annular core 34 placed adjacent to the toroidal cavity in a coaxial
relationship. A plurality of the poles 36 37 38 39 etc., extending
from the annular core 34 disposed in the same manner as the multiple
poles of the rotating magnet 25 of FIG. 7 generate rotating magnetic
flux traversing across the toroidal cavity and connecting into the
central core 40 with a centrally located hole 41. The braking magnet
42 installed on the return-pass side of the toroidal cavity 35 is
disposed in the same manner as the braking magnet 30 of FIG. 7.
The central core 40 may be arranged to be rotated with the rotating
magnetic field or to be stationary. The rotating magnetic field
is generated by the stationary annular magnet 34 in the same manner
as the rotating magnetic field created by the plurality of stationary
electric coils in an alternating current electric motor. The magnetic
poles included in the rotating magnet or stationary magnet generating
a rotating field may be non-shaded poles or shaded poles.
In FIG. 9 there is illustrated an end view of a central core such
as the item 28 of FIG. 7 or item 40 of FIG. 8. The central core
43 may be a solid cylinder of carbon steel with a central hole or
a stack of a plurality of annular wafers of carbon steel.
In FIG. 10 there is shown an end view of another central core
45 with a centrally located hole 46. The central core may be a solid
hollow cylinder of carbon steel with a plurality of radial slits
47 or a stack of a plurality of annular wafers of carbon steel with
multiple radial slits.
In FIG. 11 there is illustrated a cross section of a ball bearing
flow meter constructed in accordance with the principles of the
present invention. The ball bearing flow meter comprises a plurality
of the spherical balls 48 orbitably entrained in series within a
toroidal cavity 49 wherein the toroidal cavity 49 has a circular
cross section with a diameter slightly greater than the diameter
of the spherical balls 48. The toroidal cavity 49 is divided into
two segments by the openings 50 and 51 of the ports 52 and 53 merging
into the toroidal cavity; the first segment 54 of the toroidal cavity
49 connects the two ports 52 and 53 to one another in a tangential
arrangement and provides the flow passage from one port 52 to the
other port 53 while the second segment 55 of the toroidal cavity
49 provides the return-pass for the spherical balls. The pot openings
50 and 51 are provided with the guides 56 and 57 respectively.
The construction and purpose of these guides are described in conjunction
with FIG. 2. The sensor 58 sensing each of the spherical balls passing
by provides the information that is calibrated into the volume rate
or mass rate of the flow. It should be understood that there is
little leak of fluid across each of the spherical balls as the gap
between the surface of the spherical balls and the wall of the toroidal
cavity is very small and the pressure difference across each of
the spherical balls is maintained at a low value. Therefore, the
fluid cannot flow through the ball bearing flow meter without orbiting
the spherical balls.
In FIG. 12 there is shown another cross section of the ball bearing
flow meter of FIG. 11 taken along a plane 12--12 as shown in FIG.
11. A rotating magnet 59 with multiple poles 60 61 etc., disposed
adjacent to the toroidal cavity 49 in a coaxial relationship generates
a rotating magnetic field with the magnetic flux traversing across
the toroidal cavity 49. The rotating magnetic field generates an
orbiting motion of the spherical balls following the toroidal cavity.
The construction of the spherical balls 48 are described in conjunction
with the description of the operating principles of the ball bearing
pump.
The direction of the rotating magnetic field must be selected in
such a way that the spherical balls orbit from the inlet port opening
to the outlet port opening in the flow passage segment of the toroidal
cavity and from the outlet port opening to the inlet port opening
in the return-pass segment of the toroidal cavity. The spherical
balls experience an acceleration in the vicinity of the inlet port
opening because the rotating magnetic field and the fluid pressure
gradient collaborates to orbit the spherical balls in the flow passage
segment of the toroidal cavity and, consequently, the distance between
adjacent pairs of the spherical balls increases in the vicinity
of the inlet port opening as the fluid moves into the gap between
the spherical balls in the toroidal cavity through the inlet port.
The spherical balls experience a deceleration in the vicinity of
the outlet port opening because the rotating magnetic field and
the fluid pressure gradient oppose each other in the return-pass
segment of the toroidal cavity and, consequently, the distance between
adjacent pairs of the spherical balls decreases in the vicinity
of the outlet port opening as the fluid occupying the gap between
the spherical balls in the toroidal cavity is emptied into the outlet
port. As a matter of fact, in order to make a ball bearing flow
meter work, it is sufficient to have a magnetic field on the return-pass
half of the toroidal cavity that returns the spherical balls from
the outlet side with a lower fluid pressure to the inlet side with
a higher fluid pressure. It should be understood that, in most industrial
applications, flow meters are used in conjunction with flow control
valves controlling the flow rate. The ball bearing flow meter of
the present invention can provide a dual role as a flow meter and
as a flow control means when a rotating magnetic field with a variable
rpm is employed in generating the orbiting motion of the spherical
balls.
In FIG. 13 there is shown a cross section of another embodiment
of the ball bearing flow meter taken along the same plane as that
of FIG. 12. The toroidal cavity 64 of a ball bearing flow meter
is sandwiched between a pair of rotating magnets with multiple poles
62 and 63 in a coaxial arrangement. This arrangement of a pair of
rotating magnets disposed in a mirror image to one another provides
more and stronger orbiting force on the spherical balls compared
with the single rotating magnet of FIG. 12.
In FIG. 14 there is illustrated a cross section of another arrangement
of the ball bearing flow meter including a plurality of spherical
balls entrained in a toroidal cavity or closed loop cavity 66. The
pair of ports 67 and 68 are extending out from the toroidal cavity
66 from the side of the toroidal cavity, which arrangement provides
a clear outer circumference of the toroidal cavity.
In FIG. 15 there is illustrated another cross section of the ball
bearing flow meter of FIG. 14 taken along a plane 15--15 as shown
in FIG. 14. The multiple poles 69 70 etc., of the rotating magnet
71 are disposed adjacent to the outer circumference of the toroidal
cavity wall. The central core 72 is rotatably disposed within the
inner circumference of the toroidal cavity wall and rigidly connected
to the rotating magnet 71 by means of a shaft 73 made of magnetically
nonreacting material. The sensor 74 sensing the spherical balls
passing by is installed on the side of the toroidal cavity.
In FIG. 16 there is shown an end view of a stationary annular
magnet that generates a rotating magnetic field when it is connected
to a three phase alternating electric current. This stationary annular
magnet includes an annular core 75 a plurality of the electric
coils 76 wound around the annular core 75 and a plurality of poles
77 extending from one side of the annular core 75.
In FIG. 17 there is illustrated another cross section of the stationary
annular magnet of FIG. 16 taken along a plane 17--17 as shown in
FIG. 16 which is installed adjacent to a toroidal cavity 78 in
conjunction with another stationary annular magnet disposed in a
mirror image to one another wherein the toroidal cavity 78 of a
ball bearing flow meter is sandwiched therebetween.
In FIG. 18 there is illustrated an end view of another stationary
annular magnet that generates a rotating magnetic field when it
is connected to a three phase alternating electric current. This
stationary annular magnet includes an annular core 80 a plurality
of electric coils 81 wound around the annular core 80 and a plurality
of the poles 82 extending inwardly from the annular core 80. A central
core 83 having a solid cylindrical geometry with a plurality of
radial slits is disposed within the stationary annular magnet on
the same plane, which arrangement provides an annular space 84 for
installing the toroidal cavity of a ball bearing flow meter. The
stationary annular magnets shown in FIGS. 16 and 18 generates a
rotating magnetic field on the same principle as a rotating magnetic
field is generated in a three phase alternating current electric
motor.
In FIG. 19 there is shown a cross section of a ball bearing flow
meter including a toroidal cavity 85 sandwiched between a pair of
rotating magnets 86 and 87 disposed in a mirror image to one another
within the loop of the toroidal cavity. The axis of rotation of
the rotating magnets 86 and 87 is off set from the axis of axisymmetry
of the toroidal cavity 85 wherein the rotating magnetic field created
by the pair of rotating magnets 86 and 87 effects the spherical
balls only when they are located in the return-pass segment of the
toroidal cavity 85. It is not difficult to imagine that a pair of
rotating magnets having the same arrangement as that shown in FIG.
19 with a diameter matched to the inside circumference of the toroidal
cavity wall can be installed in a coaxial arrangement.
In FIG. 20 there is shown a cross section of a ball bearing flow
meter including a toroidal cavity sandwiched between a pair of the
rotating magnets 89 and 90 disposed in a mirror image to one another
wherein the toroidal cavity 88 has a diameter smaller than the diameter
of the rotating magnets.
It should be understood that the ball bearing pump can always be
used as a flow meter and, consequently, the ball bearing pump is
a positive displacement pump and a positive displacement flow meter,
while the ball bearing flow meter is only a positive displacement
flow meter. It should be further understood that the different configurations
for the arrangement of the rotating magnets and the stationary magnets
in conjunction with the toroidal cavity of a flow meter or a pump
are interchangeable between the rotating magnets and the stationary
magnets. For example a pair of stationary magnets similar to that
shown in FIG. 16 can be installed in the same configuration as the
pair of rotating magnets shown in FIG. 19.
While the principles of the present invention have now been made
clear by the illustrative embodiments, the utilization of the present
invention shall not be limited to such illustrative embodiments
as it will be immediately obvious to the skilled in the art that
they may make many modifications of the structure, arrangements,
elements, proportions and materials which are particularly adapted
to the specific working environment and operating condition in practicing
the the invention without departing from the principles of the present
invention. |