U.S. patent application number 10/570837 was filed with the patent office on 2007-03-15 for rotary centrifugal and viscous pumps.
This patent application is currently assigned to UNIVERSITY OF UTAH RESEARCH FOUNDATION. Invention is credited to Danny Blanchard, Bruce Gale, Phil Ligrani.
Application Number | 20070059156 10/570837 |
Document ID | / |
Family ID | 34278693 |
Filed Date | 2007-03-15 |
United States Patent
Application |
20070059156 |
Kind Code |
A1 |
Blanchard; Danny ; et
al. |
March 15, 2007 |
Rotary centrifugal and viscous pumps
Abstract
A pump device (10a, 10b, 10c) includes means for both
transferring rotational momentum to the fluid by viscous forces,
and imparting centrifugal forces to the fluid. The pump (10a, 10b)
can include a wiper (44) extending partially across at least one
rotatable disc surface (48, 48b, 48c) of at least one rotatable
disc (52, 52b, 52c). The pump (10c) can include a rotatable shaft
(150) with a hollow cavity (154) extending from one end to at least
one slot (158) extending radially from the hollow cavity.
Inventors: |
Blanchard; Danny;
(Bountiful, UT) ; Ligrani; Phil; (Sandy, UT)
; Gale; Bruce; (Taylorsville, UT) |
Correspondence
Address: |
THORPE NORTH & WESTERN, LLP.
8180 SOUTH 700 EAST, SUITE 200
SANDY
UT
84070
US
|
Assignee: |
UNIVERSITY OF UTAH RESEARCH
FOUNDATION
615 Arapeen Drive, Suite 310
Salt Lake City
UT
84108
|
Family ID: |
34278693 |
Appl. No.: |
10/570837 |
Filed: |
September 3, 2004 |
PCT Filed: |
September 3, 2004 |
PCT NO: |
PCT/US04/28890 |
371 Date: |
March 6, 2006 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
|
|
60500041 |
Sep 4, 2003 |
|
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|
60500208 |
Sep 4, 2003 |
|
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Current U.S.
Class: |
415/90 |
Current CPC
Class: |
F04D 29/22 20130101;
F04D 29/426 20130101; F04D 5/001 20130101; F04D 1/02 20130101 |
Class at
Publication: |
415/090 |
International
Class: |
F01D 1/36 20060101
F01D001/36 |
Claims
1. A pump device, comprising: a) a pump housing with an inlet, an
outlet, and a fluid passage through which a fluid can pass; and b)
means for both transferring rotational momentum to the fluid by
viscous forces and imparting centrifugal forces to the fluid,
including a mechanism selected from the group consisting of: 1) a
wiper extending partially across at least one rotatable disc
surface of at least one rotatable disc; and 2) a rotatable shaft
with a hollow cavity extending from one end to at least one slot
extending radially from the hollow cavity.
2. A device in accordance with claim 1, wherein the disc surface
includes at least one feature selected from the group consisting
of: at least one channel, extending into the disc surface, and
oriented radially with respect to an axis of rotation of the
rotatable disc; at least one ridge, extending from the disc
surface, and oriented radially with respect to an axis of rotation
of the rotatable disc; a plurality of dimples extending into the
disc surface; a plurality of dimples, extending into the disc
surface, and positioned in a linear array oriented radially with
respect to an axis of rotation of the rotatable disc; at least one
arcuate blade, extending from the disc surface, and oriented in a
spiral about an axis of rotation of the disc; at least one arcuate
channel, extending into the disc surface, and oriented in a spiral
about an axis of rotation of the disc; a cone shape with a
longitudinal axis collinear with an axis of rotation of the disc; a
curved shape with a longitudinal axis collinear with an axis of
rotation of the disc; a random surface roughness; and a patterned
surface roughness.
3. A device in accordance with claim 1, wherein the wiper includes
at least one feature selected from the group consisting of: at
least one channel or indentation, extending into a leading or
trailing edge of the wiper; at least one ridge or protrusion,
extending from a leading or trailing edge of the wiper; at least
one ridge or protrusion, extending from the wiper in a direction
away from the rotatable disc surface; at least one channel or
indentation, extending into the wiper opposite the rotatable disc
surface; a leading or trailing edge extending across the disc a
distance greater than a radius of the rotatable disc surface; a
leading or trailing edge extending across the disc a distance less
than a radius of the rotatable disc surface; a leading or trailing
edge with a curvature in a plane parallel with the rotatable disc
surface or orthogonal to an axis of rotation of the rotatable disc
surface; leading and trailing edges extending orthogonal to one
another; leading and trailing edges extending at an acute angle to
one another; leading and trailing edges with a convex curvature
therebetween; leading and trailing edges with a concave curvature
therebetween; a position extending across an axis of rotation of
the disc; a position extending aside from an axis of rotation of
the disc; a leading or trailing edge perpendicular to the rotatable
disc surface; and a leading or trailing edge at an inclined angle
with respect to the rotatable disc surface.
4. A device in accordance with claim 1, further comprising: a) a
pair of spaced-apart rotatable discs, rotatably disposed in the
pump housing, with opposing rotatable disc surfaces; and b) the
wiper being disposed between the spaced-apart rotatable discs.
5. A device in accordance with claim 4, wherein the pair of
spaced-apart rotatable discs include at least one feature selected
from the group consisting of: the opposing rotatable disc surfaces
having a same surface roughness; the opposing rotatable disc
surfaces having different surface roughnesses; the opposing
rotatable disc surfaces being parallel; the opposing rotatable disc
surfaces being non-parallel; at least one of the rotatable disc
surfaces being planar; at least one of the rotatable disc surfaces
being non-planar; the opposing rotatable disc surfaces being
planar; the opposing rotatable disc surfaces being non-planar; a
common shaft interconnecting the rotatable discs; interconnected to
rotate together at the same speed; rotatable at different speeds;
and different diameters.
6. A device in accordance with claim 1, further comprising an inlet
passage disposed between the inlet of the housing and the disc
surface, and an outlet passage disposed between the disc surface
and the outlet of the housing; the inlet and outlet passages having
an orientation selected from the group consisting of: parallel with
the disc surface; perpendicular to the disc surface; and inclined
with respect to the disc surface.
7. A device in accordance with claim 1, further comprising: a) a
motor, operatively coupled to the at least one rotatable disc; b)
an opposing wall, opposing the wiper, with the wiper, the opposing
wall and the rotatable disc together defining at least a portion of
the fluid passage.
8. A device in accordance with claim 1, wherein the hollow cavity
of the shaft has an inner surface with at least one feature
selected from the group consisting of: a straight, constant
diameter bore oriented concentric with an axis of rotation of the
shaft; a tapered bore with a straight wall in cross-section along
an axis of rotation of the shaft; a tapered bore with a curved wall
in cross-section along an axis of rotation of the shaft; at least
one ridge, extending from the inner surface, and oriented parallel
with an axis of rotation of the shaft; at least one channel,
extending into the inner surface, and oriented parallel with an
axis of rotation of the shaft; a plurality of spiral blades,
extending from the inner surface; a random surface roughness; and a
patterned surface roughness.
9. A device in accordance with claim 1, wherein the at least one
slot includes at least one feature selected from the group
consisting of: a plurality of slots laterally adjacent one another
and disposed circumferentially around the shaft; and a plurality of
slots longitudinally adjacent one another along a length of the
shaft.
10. A device in accordance with claim 1, further comprising: a
portion of the shaft laterally adjacent to the slot defining at
least one impeller blade formed within a circumference of the
shaft.
11. A device in accordance with claim 10, wherein the at least one
impeller blade includes at least one feature selected from the
group consisting of: a plurality of impeller blades laterally
adjacent one another and disposed circumferentially around the
shaft; a plurality of impeller blades longitudinally adjacent one
another along a length of the shaft; a leading or trailing edge
that is flat and oriented parallel with an axis of rotation of the
shaft; a leading or trailing edge with a concave curvature; a
leading or trailing edge with a convex curvature; a plurality of
impeller blades with leading or trailing edges having a same
surface roughness; a plurality of curvilinear impeller blades with
a curvature in a plane perpendicular to the axis of rotation of the
shaft; a plurality of impeller blades with leading or trailing
edges of different surface roughness; and an impeller blade
extending into the hollow interior.
12. A device in accordance with claim 1, further comprising: an end
surface of the hollow cavity proximate the at least one slot having
a protrusion to guide flow to the at least one slot.
13. A device in accordance with claim 1, further comprising: a
volute, disposed around the shaft at the at least one slot.
14. A device in accordance with claim 1, further comprising: a) a
motor, operatively coupled to the shaft; b) a pair of bearings,
carrying the shaft and disposed on opposite sides of the at least
one slot; and c) an intermediate member, disposed between the pair
of bearings, defining a volute around the shaft at the at least one
slot.
15. A pump device, comprising: a) a pump housing with an inlet, an
outlet, and a fluid passage through which a fluid can pass; b) at
least one disc, rotatably disposed in the pump housing, having a
rotatable disc surface; c) a wiper, extending across a portion of
the rotatable disc surface; d) an opposing wall, opposing the
wiper, with the wiper, the opposing wall and the disc together
defining at least a portion of the fluid passage; and e) a motor,
operatively coupled to the disc.
16. A pump device, comprising: a) a pump housing; b) a rotatable
shaft, rotatably disposed in the housing; c) a hollow cavity,
formed in the shaft; d) an aperture formed in an end of the shaft
defining an inlet to the hollow cavity; e) a plurality of slots,
formed in the shaft and extending from an outer surface of the
shaft to the hollow cavity and defining a fluid passage and an
outlet from the hollow cavity, and defining a plurality of impeller
blades between the plurality of slots and within a circumference of
the shaft; and f) at least one bearing, carrying the shaft and
disposed between the housing and the shaft.
17. A device in accordance with claim 16, further comprising: a) a
pair of bearings disposed on opposite sides of the plurality of
slots; b) an intermediate member, disposed between the pair of
bearings and around the plurality of slots, having a cavity
defining a volute that extends uninterrupted to an outlet; and c) a
motor, operatively coupled to the shaft.
Description
FIELD OF INVENTION
[0001] The present invention relates generally to micro-scale
pumps, millimeter-scale pumps, and macro-scale pumps.
BACKGROUND
[0002] The area of microfluidics is developing with many new
sensors, separation devices, drug delivery systems, and other
small-scale and micro-scale fluidic devices. For many of these
devices there is a need to circulate or move fluid through
macro-scale and micro-scale channels. A variety of micropumps are
available to meet this need, and generally to fulfill specific
applications. For example, such micropumps include membrane pumps,
electrohydrodynamic (EHD) pumps, electrokinetic (EK) pumps, rotary
pumps, peristaltic pumps, bubble based pumps, etc. Non-mechanical
pumps, like the electrohydrodynamic and electrokinetic pumps, do
not have moving parts, which increases reliability. Such devices,
however, are generally limited by low flow rate and pressure rise
capabilities, the applications of the pump, the working fluids that
can be pumped, and high supply voltage requirements. Mechanical
pumps, like rotary pumps, peristaltic pumps, and membrane pumps,
have a wide variety of possible working fluids and applications.
Such mechanical micro-pumps (like rotary micropumps), however, are
believed to be feasible only when they are greater than a certain
size.
[0003] Miniature rotary pumps have been proposed. For example, see
Hainan, C., Ahaoying, Z., Yong, L., Xiongying, Y., and Yihua, Y.,
1997, "A novel centrifugal miniature pump and its medical
application," Proceedings of the 1997 International Symposium On
Micromechatronics and Human Science, IEEE, pp. 115-117. Such rotary
pumps have an impeller to produce pumping. The behavior and
performance of macro-scale rotary pumps are well established and
well known. The dynamics, performance, and efficiency of rotary
pumps, however, change as the size of the pump is altered. For
example, secondary flows, and the losses associated with them,
become more important as macro-scale impeller passage size
decreases. As size decreases further, surface (viscous) forces
become more significant, and can dominate the performance of the
pump.
[0004] One important dimension of many rotary pumps is the gap
distance between the top of the blades, and the pump housing. As
the gap increases, there is more leakage across the blades, and the
overall hydraulic efficiency of the pump decreases. If the gap is
too small or zero, the blades can be damaged by contacting the pump
housing. On a macro-scale this "gap problem" is generally
insignificant, but on a micro-scale, or a millimeter-scale, the gap
between the top of the blades and the pump housing can be about the
same as the height of the impeller blades. Thus, in a miniature
rotary pump, the blades should be close to the pump housing to
minimize cross-blade leakage and losses between the blades and the
housing, but such closeness risks damage or friction losses due to
contact.
[0005] The Hainan pump is reported to have a maximum flow rate of
100 m/min and a maximum pressure rise of 10 kPa.
[0006] Another rotary micropump has an integrated magnetic motor
with a stator that also acts as the impeller. See Ahn C. H. and
Allen, M. G., 1995, "Fluid micropumps based on rotary magnetic
actuators," Proceedings of IEEE Micro Electro Mechanical Systems
1995, IEEE, ASME, pp. 408-418. The pump has radial inflow and
radial outflow. Such a pump, however, is believed to have lower
performance, i.e. lower flow rate and lower pressure rise. For
example, the Ahn pump is reported to have a maximum flow rate of 24
.mu.l/min, and a maximum theoretical pressure rise of 100 Pa.
[0007] Another type of pump has been proposed that includes one
spinning disk spinning adjacent a spiral channel concentric with
and spiraling around the rotational axis. An inlet is formed
perpendicular to the disk at the inside of the spiral near a center
of the disk. An outlet is formed perpendicular to the disk at an
outside of the spiral near an outer edge of the disk. See Kilani,
M., Galambos, P., Haik, Y., and Chen, C. J., 2003, "Design and
Analysis of a Surface Micromachined Spiral-Channel Viscous Pump,"
ASME Journal of Fluids Engineering, 125 (2), pp. 339-344. It is
believed that the Kilani pump may be difficult to manufacture.
[0008] Another type of pump has been proposed that includes a shaft
with eccentric rotation nearer one side of a tube than another. See
Sen, M., Wajerski, D., and Gad-El-Hak, M., 1996, "A Novel Pump for
MEMS Applications," ASME Journal of Fluids Engineering, 118, (3),
pp. 624-627. The Sen pump utilizes the outer surface of the shaft.
The Sen pump has limited flow rates and pressure rise
capabilities.
[0009] Another type of pump has been proposed that utilizes a stack
of spinning disks.
SUMMARY
[0010] It has been recognized that it would be advantageous to
develop a millimeter-scale or micro-scale pump which imposes fluid
motion and pressure rise by means of viscous and inertial
forces.
[0011] Briefly, and in general terms, the invention is directed to
a pump device with means for both 1) transferring rotational
momentum to the fluid by viscous forces, and 2) imparting
centrifugal forces to the fluid.
[0012] In one embodiment of the invention set forth above, the pump
can include a wiper extending partially across at least one
rotatable disc surface of at least one rotatable disc.
[0013] In another embodiment of the invention set forth above, the
pump can include a rotatable shaft with a hollow cavity extending
from one end to at least one slot extending radially from the
hollow cavity.
BRIEF DESCRIPTION OF THE DRAWINGS
[0014] Additional features and advantages of the invention will be
apparent from the detailed description which follows, taken in
conjunction with the accompanying drawings, which together
illustrate, by way of example, features of the invention; and,
wherein:
[0015] FIG. 1a is a schematic, partial cross-sectional side view of
a pump in accordance with an embodiment of the present
invention;
[0016] FIG. 1b is a schematic, partial cross-sectional side view of
another pump in accordance with another embodiment of the present
invention;
[0017] FIG. 1c is an exploded perspective view of the pump of FIG.
1b;
[0018] FIG. 1d is a graph of flow rates versus rotational speed for
the pumps of FIGS. 1a and 1b, with a disc diameter of 2.38 mm and a
gap height of 103 .mu.m;
[0019] FIG. 2a is a partial, internal top view of the pump of FIG.
1a;
[0020] FIG. 2b is a partial, internal top view of another pump in
accordance with another embodiment of the present invention;
[0021] FIG. 2c is a partial, internal top view of another pump in
accordance with another embodiment of the present invention;
[0022] FIG. 2d is a partial, internal top view of another pump in
accordance with another embodiment of the present invention;
[0023] FIG. 2e is a partial, internal top view of the pump of FIG.
1b;
[0024] FIGS. 3a-3f are perspective views of discs of the pumps of
FIGS. 1a and 1b in accordance with embodiments of the present
invention;
[0025] FIGS. 3g-3i are partial perspective internal views of wipers
of the pumps of FIGS. 1a and 1b in accordance with embodiments of
the present invention;
[0026] FIG. 4a is a schematic, partial cross-sectional side view of
another pump in accordance with another embodiment of the present
invention;
[0027] FIG. 4b is a partial, cross-sectional perspective view of
the pump of FIG. 4a;
[0028] FIG. 4c is a cross-sectional side view of the pump of FIG.
4a;
[0029] FIG. 4d is a graph of pressure head versus volumetric flow
rate for various experimental pumps with a constant impeller
rotational rate of 9,240 rpm, and with the data points from left to
right for each impeller configuration obtained with outlet tubing
diameters of 0.254 mm, 0.508 mm, and 1.397 mm, respectively;
[0030] FIG. 5a is a partial, cross-sectional perspective view of a
shaft or impeller of the pump of FIG. 4a;
[0031] FIGS. 1b-5f are partial, cross-sectional perspective views
of shafts or impellers for the pump of FIG. 4a in accordance with
embodiments of the present invention;
[0032] FIG. 5g is a partial top view of a shaft or impeller for the
pump of FIG. 4a in accordance with an embodiment of the present
invention;
[0033] FIG. 6a is a schematic, internal top view of the pump of
FIG. 4a showing a volute configuration; and
[0034] FIGS. 6b-6d are schematic, internal top views of volute
configurations for the pump of FIG. 4a in accordance with
embodiments of the present invention.
DETAILED DESCRIPTION OF EXAMPLE EMBODIMENT(S)
[0035] As illustrated in the Figures, various pumps are shown as
exemplary implementations in accordance with the invention. The
size of the pumps can be scaled up to have dimensions on the order
of millimeters, inches, or feet, or can be scaled down to have the
dimensions on the order of micro-meters. The pumps utilize both
viscous and centrifugal forces to provide pumping action. The pumps
have a rotational or spinning element that transfers rotational
momentum to the fluid by viscous forces, and imparts centrifugal
forces to the fluid. At very small scales and for some operating
conditions and embodiments, the centrifugal forces may be
insignificant compared to the viscous forces. Fields that can
benefit from the use of such micro-scale and millimeter-scale pumps
include electronics cooling, implantable medical devices, .mu.-TAS
(micro Total Analysis Systems), micro-fluid dispensing systems,
transport of biomedical fluids, drug delivery, chemical analysis
systems, etc. Fields that can benefit from the use of such
millimeter-scale and macro-scale pumps include blood pumping,
ventricle assist devices, etc.
[0036] The pumps described herein can be described as two types.
The first type is a spinning disc type pump, indicated generally at
10a and 10b, and shown in FIGS. 1a-3h, that utilizes a spinning
disc as the rotational element with a wiper extending partially
across the rotatable disc surface. The second type is a rotary
shaft type pump, indicated generally at 10c and shown in FIGS.
4a-6d, that utilizes a rotatable shaft as the rotational element
with a hollow cavity extending from one end to slots extending
radially from the hollow cavity.
[0037] As illustrated in FIGS. 1a-3h, a spinning disc type pump 10a
is shown in an example implementation in accordance with the
invention. The pump can have a pump housing 14 with an inlet 18, an
outlet 22, and a fluid passage 26 through which a fluid can pass.
The pump housing can be formed by, or can include, various
components of the pump. Similarly, the fluid passage can be formed
by, or can include, various components of the pump. In addition,
the pumps can include an inlet channel 30 between the inlet 18 and
the spinning disc, and an outlet channel 34 disposed between the
spinning disc and the outlet 22.
[0038] As described above, the pump 10a includes a wiper 44
extending partially across a rotatable disc surface 48 of a
rotatable disc 52. The disc surface can be the end of a shaft while
the disc can be the shaft. The disc surface 48 contacts the fluid
in the fluid passage 26, and transfers momentum to the fluid
through viscous forces, which move the fluid through the pump or
fluid passage. In addition, centrifugal forces are present in the
pump due to the rotation of the fluid through the pump, which aids
in pumping by forcing the fluid outward toward the outlet channel
34. Thus, the fluid can pass through the inlet channel 30 to the
spinning or rotatable disc surface 48, which transfers momentum to
the fluid through viscous forces, which moves the fluid through the
outlet channel 34.
[0039] The wiper 44 is disposed adjacent, or on, the disc surface
48, and extends across a portion of the disc surface 48. The wiper
44 "wipes" the fluid from the disc surface 48 and/or directs the
fluid from the disc surface 48 towards the outlet channel 34. The
wiper 44 can include a leading edge 56 which guides the fluid, and
an opposite trailing edge 60. The leading edge 56 of the wiper 44
can help define or form a portion of the fluid passage 26 and the
outlet channel 34. Similarly, the trailing edge 60 of the wiper 44
can help define or form a portion of the fluid passage 26 and the
inlet channel 30.
[0040] The pump 10a can include an opposing wall 64 that opposes
the wiper 44 or the leading and trailing edges 56 and 60. The
opposing wall 64 can be spaced-apart from the wiper 44, and can
include a portion positioned along a perimeter or outer
circumference of the disc surface 48 to maximize the surface area
of the disc surface in contact with the fluid. The wiper 44 (or
leading and trailing edges 56 and 60), the opposing wall 64 and the
disc 52 (or disc surface 48) together define at least a portion of
the fluid passage 26 (and the inlet and outlet channels 30 and
34).
[0041] The disc surface 48, inlet channel 30, outlet channel 34,
and fluid passage 26 can be aligned, or oriented parallel to one
another, to reduce interference in the flow of the fluid, reduce
pressure and flow losses, and increase efficiency. Alternatively,
the inlet and outlet channels can have different configurations or
orientations.
[0042] The wiper 44 can extend to an axis of rotation 68 of the
disc 52, thus extending across half the disc surface 48, as shown
in FIG. 2a. The leading and trailing edges 56 and 60 of the wiper
44 can be oriented orthogonal to one another, again as shown in
FIG. 2a. Similarly, the opposing wall 64 can have orthogonal
portions, or can form a right angle. Thus, the pump 10a can be
configured with the inlet and outlet 18 and 22, or the inlet and
outlet channels 30 and 34, orthogonal to one another.
[0043] The disc surface 48 can be configured to accommodate desired
flow characteristics, and/or to optimize efficiency. For example,
the disc surface 48 can be configured to enhance momentum transfer
from the disc surface to the fluid. Referring to FIG. 3a, the disc
surface 48b can include one or more channels or elongated
indentations 72 extending into the disc surface 48b and oriented
radially. For example, the disc surface 48b can include four
channels or indentations 72 extending from a center of the disc to
a perimeter of the disc, and oriented at equal angles (right or
ninety-degree angles) with respect to one another. The channels or
indentations 72 can be linear or straight, as shown. In addition,
the channels or indentations 72 can have rectilinear side walls, or
rectilinear cross-sections, as shown. It is of course understood
that more or fewer channels can be used; that the channels can be
arcuate or curved; and that the walls or cross-sections of the
channels can be curved or angled. More channels might increase
momentum transfer and increase turbulence or mixing. Curved
channels might be used to impart desired flow characteristics.
Curved or angled walls of the channels might be used to facilitate
laminar or turbulent flow.
[0044] Referring to FIG. 3b, the disc surface 48c can include one
or more ridges or elongated protrusions 76 extending from the disc
surface 48c and oriented radially. For example, the disc surface
48c can include four ridges or protrusions 76 extending from a
center of the disc to a perimeter of the disc, and oriented at
equal angles (right or ninety-degree angles) with respect to one
another. The ridges or protrusions 76 can be linear or straight, as
shown. In addition; the ridges or protrusions 76 can have
rectilinear side walls, or rectilinear cross-sections, as shown. It
is of course understood that more or fewer ridges can be used; that
the ridges can be arcuate or curved; and that the walls or
cross-sections of the ridges can be curved or angled. More ridges
might increase momentum transfer and increase turbulence or mixing.
Curved ridges might be used to impart desired flow characterizes.
Curved or angled walls of the ridges might be used to facilitate
laminar or turbulent flow, or mixing.
[0045] Referring to FIG. 3c, a plurality of dimples 80 can extend
into the disc surface 48d. The plurality of dimples 80 can be
positioned in a linear array that can be oriented radially.
Furthermore, the disc surface 48d can include a plurality of linear
arrays extending radially from near a center of the disc to a
perimeter of the disc, and oriented at equal angles with respect to
one another. The dimples 80 can be of uniform diameter and/or
depth, and can have curvilinear walls or cross-sections. As stated
above, the dimples can enhance momentum transfer. It is of course
understood that the dimples can have non-uniform sizes (i.e.
different diameters and/or depths); can have rectilinear or angled
walls or cross-sections; or oriented in curvilinear arrays.
Non-uniform dimples or curvilinear arrays might impart desired flow
characteristics. Rectilinear or angled walls or cross-sections can
be used to facilitate laminar or turbulent flow or mixing.
[0046] Referring to FIG. 3d, the disc surface 48e can include one
or more arcuate blades 84 extending from the disc surface, and
oriented in a spiral about the axis of rotation 68 of the disc. The
blades 84 can have a proximal end near the center of the disc or
near the axis of rotation, and spiral (i.e. extend radially and
circumferentially) to an outer circumference or perimeter of the
disc. The arcuate blades can help push the fluid towards the outlet
channel 34. The blades 84 define corresponding arcuate channels 86
therebetween. It is of course understood that the disc surface 48e
can be described as having one or more arcuate channels 86
extending into the surface and oriented in a spiral.
[0047] The above described features can enhance momentum transfer
from the disc surface to the fluid. Fluid velocity variations will
occur as the fluid moves past the above described features,
resulting in eddies and local turbulence, which will increase the
diffusion of momentum normal to the disc surface. This will
increase pump efficiency and performance. In addition, the features
may help push the fluid toward the outlet channel.
[0048] The disc surface 48 also can include patterned or random
surface roughness to enhance momentum transfer. For example,
increased surface roughness can be used to enhance momentum
transfer, turbulent flow and/or mixing, while decreased surface
roughness can be used to enhance more laminar flow. The surface
roughness may be patterned to obtain specific flow characteristics
at various radial positions on the disc surface.
[0049] Referring to FIGS. 3e and 3f, the disc can have a non-planar
disc surface. The disc surface 48f can have a cone or conical shape
with a longitudinal axis collinear with the axis of rotation 68 of
the disc, as shown in FIG. 3e. Similarly, the disc surface 48g can
have a curved or dome shape with a longitudinal axis collinear with
the axis of rotation 68 of the disc, as shown in FIG. 3f. The cone
or domed shape of the disc surface 48f or 48g creates a greater
thickness or width of the fluid passage near the perimeter or
circumference of the disc, and less thickness or narrower width of
the fluid passage near the axis of rotation. The area between the
disc and top of the housing is referred to as the gap. The
non-planar shape of the disc surface alters a gap height with
respect to radial position. This change in gap height can be used
to eliminate backflow in the pump, which can increase pump
efficiency and performance. The wiper 44 can be configured to match
the inclined or curved surface of the disc.
[0050] The wiper 44 can also be configured to accommodate desired
flow characteristics, and/or to optimize efficiency. Referring to
FIG. 3g, the wiper 44b can include one or more ridges or
protrusions 90 extending from the leading and/or trailing edge 56
and/or 60. In addition, the wiper 44b can include one or more
channels or indentations 94 extending into the leading and/or
trailing edge 56 and/or 60. The ridges or channels 90 or 94 in the
edges 56 and 60 of the wiper can increase mixing of the fluid.
Fluid can become trapped, and can circulate in and out of the
channels, thus enhancing mixing. The ridges or channels can be
rectilinear, as shown. It is of course understood that the ridge or
channel can be curvilinear or angled to facilitate a more laminar
flow. The ridges or channels can extend through or across a
thickness of the wiper, or through the gap, as shown.
[0051] In addition, the wiper 44 can be configured to reduce
friction with the disc 52. Referring to FIG. 3h, the wiper 44c can
include one or more ridges or protrusions 98 extending from the
wiper 44 in a direction away from, or towards, the disc 52 or disc
surface 48. The ridges or protrusions 98 can extend along the
leading and trailing edges 56 and 60. Similarly, the wiper 44c can
include one or more channels or indentations 102 extending into the
wiper. The channels or indentations can extend into the wiper
opposite the disc surface. The ridges 98 and channels 102 can
reduce friction between the disc surface 48 and the wiper 44c, such
as by reducing the area of the wiper 44c in contact with the disc
52 or disc surface 48. Reducing friction can reduce the power
requirements to rotate the disc. (The ridges 98 and channels 102
shown in FIG. 3h are configured to face a second disc, described
below, but the wiper can be flipped-over to face the first disc 52,
the configuration shown in FIG. 3h being for clarity.) The wiper 44
can be configured to facilitate mixing, and increase performance of
the wiping action. Referring to FIG. 2b, the wiper 44d, or the
leading and trailing edges 56d and 60d, can extend across the disc
52 or disc surface 48 a distance greater than a radius of the disc
surface, or can extend across more than half the diameter of the
disc. Such a configuration can decrease the recirculation near the
center of the disc surface. Alternatively, referring to FIG. 2c,
the wiper 44e, or the leading and trailing edges 56e and 60e, can
extend across the disc or disc surface a distance less than a
radius of the disc surface, or can extend across less than half of
the diameter of the disc. Such a configuration can increase the
recirculation near the center of the disc surface.
[0052] Referring to FIG. 2d, the wiper 44f can have leading and/or
trailing edges 56f and 60f with a curvature in a plane parallel
with the rotatable disc surface 48 or orthogonal to an axis of
rotation 68 of the rotatable disc surface. The curvature can
increase the efficiency of the wiper 44f in "wiping" the fluid from
the disc surface 48. In addition, the leading and trailing edges
56f and 60f can extend at an acute angle with respect to one
another. Decreasing the angle between the edges 56f and 60f can
increase the exposed disc surface 48, thus increasing pump
performance. Alternatively, the edges can be oriented at an obtuse
angle depending on the application of the pump.
[0053] Referring again to FIG. 2b, the leading and trailing edges
56d and 60d can have an intersection or tip 106 with a convex
curvature therebetween. The convex curvature can reduce
recirculation and mixing, but can increase pumping performance.
Alternatively, referring to FIG. 2c, the leading and trailing edges
56e and 60e can have an intersection 110 with a concave curvature.
The concave curvature can increase recirculation and mixing.
[0054] The wiper 44 can also be configured to affect the flow rate,
pressure rise and/or mixing characteristics. Referring to FIGS. 2b
and 2d, the wiper 44d and 44f can be positioned to extend across
the axis of rotation 68 of the disc 52, and across over half of the
disc. Referring to FIG. 2c, the wiper 44e can be positioned to
extend aside from, or away from, the axis of rotation 68 of the
disc 52, and across less than half of the disc.
[0055] In addition, the leading and trailing edge of the wiper can
be angled to change the efficiency of the wiper to "wipe" the fluid
from the disc surface. The edge 56 or 60 of the wiper 44 can be
orthogonal or perpendicular to the disc surface 48, as shown in
FIG. 3h. Alternatively, the edge 56d or 60d of the wiper 44d can
have an acute or obtuse angle with respect to the disc surface, as
shown in FIG. 3i. In addition, the edge of the wiper can be curved
in a plane orthogonal to the disc surface.
[0056] As shown and described above, the wiper can be positioned
and oriented symmetrically with respect to the disc surface.
Alternatively, the wiper and disc surface can have an asymmetrical
configuration.
[0057] In addition, the inlet and outlet channels, or the inlet and
outlet, of the pump can be configured to optimize performance or to
accommodate particular applications. For example, the inlet and
outlet channels 30 and 34 can be oriented parallel with the disc
surface 48 and orthogonal to one another, as shown in FIG. 1a. As
another example, the inlet and outlet channels 30b and 34b can be
oriented at an obtuse angle with respect to one another to maximize
the disc surface 48, as shown in FIG. 2d. Alternatively, the inlet
and outlet channels can be oriented perpendicularly or inclined
with respect to the disc surface to suit particular
applications.
[0058] Referring to FIG. 1b, another pump 10b is shown that is
similar in many respects to the pump 10a of FIG. 1a, and described
above. The pump 10b can include the wiper 44 disposed between a
pair of spaced-apart discs 52b and 52c rotatably disposed in the
pump housing. The discs 52b and 52c include opposing disc surfaces
48h and 48i. The wiper 44 can be disposed between the discs 52b and
52c and can wipe or direct the fluid from both disc surfaces 48h
and 48i. The discs 52b and 52c can be interconnected by a common
shaft 120 so that they rotate together at the same speed, and can
be turned by the same motor. Alternatively, the discs 52b and 52c
can be rotated separately, or at different speeds, to enhance
mixing of the fluid. The discs 52b and 52c, or the disc surfaces
48h and 48i, can be similar to facilitate manufacturing, facilitate
laminar flow and minimize recirculation. For example, the discs or
disc surfaces can have the same diameter and the same surface
roughness, can be planar, and can be parallel to one another.
Alternatively, the discs or disc surfaces can have different
diameters, different surface roughness, can be non-planar, and/or
can be non-parallel to increase recirculation or mixing, as
discussed above.
[0059] During testing of the spinning disc type pumps 10a and 10b,
three discrete regions of a pumping area, fluid passage or disc
surface were observed, as shown in FIG. 2e. In a first region
(region 1), near a leading edge of the disc and the trailing edge
60 of the wiper 44, the spinning disc 52 draws fluid away from the
trailing edge of the wiper, creating a low pressure region. The
pressure forces, due to the pressure gradient, force fluid from the
inlet channel 30 into the pumping area, and along the trailing edge
of the wiper. The fluid then is forced tangentially through a
second region (region 2) due to the viscous forces applied to the
fluid by the spinning disc and the diffusion of momentum. The fluid
tangential velocity decreases as the fluid approaches the leading
edge 56 of the wiper 44 near the outlet in a third region (region
3), which results in a high pressure region at the trailing edge of
the wiper. The high pressure will force the fluid radially outward
toward the outlet channel 34. Due to the variation of tangential
velocity with radial position, the region of highest pressure may
be located at a radial position between an outer disc radius and a
coupling shaft radius, resulting in a fluid flow from the region of
highest pressure toward the coupling shaft. This movement of fluid
results in a backflow at smaller radii of the pumping area.
Centrifugal force also forces the fluid from the pumping area to
the outlet channel. The fluid flow through these regions was
visualized in the double-disc pump 10b using a dye.
[0060] The height or thickness of the fluid passage through the
pump (also height of the wiper) is referred to as the gap height of
the pump. The volume of fluid between the two discs or between the
single disc and upper pump housing is referred to as the pumping
area. Experimental pumps have been created with a disc diameter of
2.381 mm, and a gap height of 103 .mu.m. The maximum flow rates
obtained were 0.74 ml/min and 2.1 ml/min for the single-disc and
double-disc pumps, respectively, for a rotational speed of 5000
rpm.
[0061] The advantages of the above-described micro-scale pumps
compared to other micropumps include a wide range of possible flow
rates, simplicity, constant flow, planar structure, well controlled
flow rate, and possible mixing characteristics.
[0062] The discs 52-52c described above can be formed by the end of
a shaft. Referring to FIG. 1c, the shafts can be captured in
bearings 116b and 116c, which also form a seal along the shafts to
reduce leakage.
[0063] An exploded view of an experimental double-disc pump can be
seen in FIG. 1c. There are five main fabricated components of the
experimental pump: 1) the disc(s) 52b and 52c, 2) top housing 122,
3) bottom housing 124, 4) bearings 116b and 116c, and 5)
wiper/channel insert 128. Fabrication of the disc(s) 52b and 52c
can be realized using precision machining techniques. A lathe can
be used to obtain the desired outside diameter of the disc shaft,
and to create the disc surface. The diameter of the experimental
disc(s) for flow rate testing was 2.381 mm, and the diameter of the
experimental discs for flow visualization was 6.35 mm. For the
double-disc pump, a hole can be bored into one of the disc
surfaces, in which the coupling shaft 120 (FIG. 1b) can be
press-fit. The other disc can be machined on the lathe to the
desired outside diameter and then the coupling shaft can be
machined on the end, such that the step between the disc shaft
diameter and coupling shaft diameter forms the other disc surface.
The coupling shaft can be press-fit into the bored hole in one disc
until the desired gap height is obtained. The disc of the
single-disc pump can be made from type 304 stainless steel. The
discs for the double-disc pump used for flow rate testing were made
from brass. The bottom and upper discs for the double-disc pump
used for flow visualization were made from aluminum and acrylic
respectively. The acrylic disc was clear and allowed the flow to be
visualized through the disc. The above-described parts can be
integrated together to produce the same features with fewer parts.
For example, the wiper/channel insert can be integrated into the
top housing. As another example, the bearing material can be the
same material as the top housing, such that the top housing and top
bearing are the same piece.
[0064] For experimentation, the top housing 122 was made from
acrylic to allow the flow passing into and through the pump to be
visualized. The top housing can have an inlet and outlet passage
that connects the inlet and outlet tubing to the inlet and outlet
channels of the pumps. The top housing 122 for the double-disc pump
contains the upper bearing 116c. The bottom housing 124 for the
pumps can be made from aluminum, and contains the lower bearing
116b.
[0065] The bearings 116b and 116c can be made from Torlon, a strong
self-lubricating plastic. The upper and lower bearings can
press-fit into the top and bottom housing respectively. Torlon is
used because it has a low coefficient of friction, and can be
easily machined. The outer diameter of the bearings was 12.7 mm,
and the inner diameter was the diameter of the disc shaft. A recess
that is 1 mm deep was cut into the bottom bearing under the inlet
and outlet channel. The larger hydraulic diameter of the inlet and
outlet channels due to this recess reduces the speed and pressure
losses of the fluid as it travels through the inlet and outlet
channels, and minimizes losses as the fluid turns from the inlet
tubing to the inlet channel, and from the outlet channel to the
outlet tubing.
[0066] The wiper/channel insert 128 can be machined from brass shim
stock using a CNC milling machine. The brass shim stock used for
the flow rate testing and flow visualization testing was 103 .mu.m
tall and 78 .mu.m tall respectively. The width of the inlet and
outlet channels machined into the brass shim stock was half the
disc diameter (channel widths of 1.191 mm, and 3.175 mm). The
wiper/channel insert 128 can be captured between the top and bottom
housings 122 and 124 and a seal is created by tightening bolts that
clamp the top and bottom housing together.
[0067] The pump can be assembled by connecting the disc pump shaft
to the motor coupling shaft on the motor. The disc surface can be
adjusted so that the disc surface is flush with the top surface of
the bottom housing. The wiper/channel insert can then be positioned
and secured in place. Then for the double-disc pump, the coupling
shaft with the upper disc can be press-fit into the lower disc
until the upper disc surface contacts the upper wiper surface. The
top housing can then be secured, and tightened to minimize leakage.
The inlet and outlet tubes can then be connected to the top
housing. The air can be bled from the pump.
[0068] As discussed above, the pumps can be powered, and the discs
can be rotated, by a motor. The motor can be selected based on size
and power requirements of the desired application. For
experimentation, the disc pumps were powered by an externally
mounted Maxon EC32 number 118891, brushless DC motor that is 32 mm
in diameter, with an 80 Watt power rating. The maximum speed is
25,000 rpm, with a stall torque of 0.35 N-m. The brushless motor
was controlled by an Advanced Motion Controls power amplifier
(Model #BE12A6). The power amplifier has a DC supply voltage of
40V, a peak current of 12 Amps, and continuous current rating of 6
Amps. A negative feedback controller was employed to maintain
constant speed for any variation in torque. The speed was
controlled by adjusting a 15-turn potentiometer. The speed range
was 100-13,200 rpm. The motor controller determines the rotational
speed from the signal from an optical encoder attached to the motor
shaft. This apparatus produced a voltage signal that is
proportional to speed. The voltage was measured using a Keithley
131 Digital Multimeter.
[0069] Referring to FIG. 1d, experimental flow rates for the
experimental single-disc and double-disc pumps 10a and 10b are
shown for rotational speeds ranging from 1000 rpm to 5000 rpm, disc
diameter of 2.381 mm, and gap height of 103 .mu.m. The experimental
results show that the flow rate increases nearly linearly with
rotational speed for the single-disc and double-disc pumps. The
maximum flow rates for the single-disc pump and double-disc pump
are 0.74 ml/min and 2.1 ml/min respectively for a rotational speed
of 5000 rpm. Note that the flow rate will increase with greater
rotational speed, and larger disc diameter. The flow rate will
decrease with lower rotational speeds, smaller disc diameters, and
smaller gap heights. The flow direction can also be reversed by
changing the rotational direction of the disc(s).
[0070] The advantages of these micro-scale pumps compared to other
micropumps include a wide range of possible flow rates, simplicity,
constant flow, planar structure, well-controlled flow rate, and
possible mixing characteristics. The experimental flow rate shows a
nearly linear relationship between flow rate and rotational speed.
The fluid pumping direction can be reversed by changing the
rotational direction of the disc(s). The design of the disc pumps
is simple, and can potentially be fabricated using microfabrication
technology due to the planar structure of the pump. The disc pumps
are actuated with an external motor, but a microfabricated disc
pump can potentially be actuated with a micro-electrostatic comb
drive. The movement of the dye through the pumping area indicates
the presence of a recirculating flow near the coupling shaft, and
the movement of dye due to pressure gradients, viscous forces, and
centrifugal forces. The movement of the dye also indicates a
significant increase in the surface area of the dye volume, which
will increase mixing through the pump area and outlet channel.
[0071] As illustrated in FIGS. 4a-6d, a rotatable shaft type pump
10c is shown in an example implementation in accordance with the
invention. As described above, the pump 10c includes a rotatable
shaft 150 with a hollow cavity 154 extending from one end to one or
more slots 158 extending radially from the hollow cavity. The
hollow cavity 154 can be a bore extending axially into one end of
the shaft so that a longitudinal axis of the hollow cavity 154 is
concentric with a longitudinal axis of the shaft 150, or an axis of
rotation 162 of the shaft. The hollow cavity 154 can have an inner
surface 166 that contacts the fluid and helps define a fluid
passage 26c. The slots 158 can extend from an outer surface of the
shaft 150 to the inner surface 166 of the hollow cavity 154, and
can be positioned intermediate the ends of the shaft. The slots 158
can define impellers or impeller blades 170 that are contained
within the circumference or perimeter of the shaft.
[0072] The rotatable shaft 150 or inner surface 166 transfers
momentum to the fluid through viscous forces, and provides a
"pre-swirl" to the fluid that aids in overall pumping by reducing
sudden acceleration of the fluid at the impellers. In addition,
centrifugal forces act on the fluid between the impeller blades
170, or in the slots 158, forcing the fluid outward, and thus
creating a pumping effect. Thus, the fluid can pass into the hollow
cavity 154 to the inner surface 166, which transfers momentum to
the fluid through viscous forces, and through the slots 158, which
apply centrifugal forces to the fluid.
[0073] A pair of bearings 174 and 178 can carrying the shaft 150,
and can be disposed on opposite sides of the slots 158 and impeller
blades 170. An intermediate member 182 can be disposed between the
pair of bearings 174 and 178, and can define a volute 186 around
the shaft 150 at the slots 158.
[0074] The bearings 174 and 178 and intermediate member 182 can be
contained in, or can help form, a housing 14c. As described above,
the housing 14c or pump 10c can include an inlet 18c and an outlet
22c, and an inlet channel 30c extending from the inlet to the shaft
and an outlet channel 34c extending from the shaft, slots or volute
to the outlet. The hollow cavity 154 can form part of the inlet
channel 30c. The inlet and outlet channels 30c and 34c can be
oriented parallel with the shaft 150 or axis of rotation 162. In
addition, the housing or pump can include an exit plenum 190
disposed proximate the volute 186 so that the fluid passes through
the volute and into the exit plenum. Alternatively, the volute 186
can open to an outlet.
[0075] The hollow cavity 154 or bore can have a straight, constant
diameter and can be oriented concentric with the axis of rotation
162, as shown in FIGS. 4a and 5a. In addition, the shaft 150 can
have a tapered inlet 194 to reduce fluid losses. The hollow cavity
can also be configured to reduce fluid losses. For example, the
hollow cavity can include a tapered bore 150b with a straight wall
in cross-section along the axis of rotation 162 of the shaft, as
shown in FIG. 5e. The bore can be inwardly or outwardly tapered.
Alternatively, the hollow cavity can include a tapered bore with a
curved wall in cross-section along the axis of rotation of the
shaft.
[0076] In addition, the hollow cavity 154 or inner surface 166 can
be configured to increase momentum transfer from the inner surface
to the fluid, and to help direct or push the fluid through the
hollow cavity. For example, the hollow cavity or inner surface can
include one or more ridges 200 extending from the inner surface 166
and oriented parallel with the axis of rotation 162 of the shaft,
as shown in FIG. 5c. Similarly, the hollow cavity or inner surface
can include one or more channels 204 extending into the inner
surface and oriented parallel with the axis of rotation of the
shaft, as shown in FIG. 5c. As another example, the hollow cavity
or inner surface can include one or more spiral blades 208
extending from the inner surface, or one or more spiral channels
210 extending into the inner surface, as shown in FIG. 5d. The
spiral ridges or channels can extend around the inner surface and
along the length of the inner surface. The ridges or channels can
have rectilinear cross-sections, as shown, to increase momentum
transfer. It is of course understood that the ridges or channels
can have curved or inclined cross-sections to reduce turbulence or
mixing. Furthermore, the inner surface can have random or patterned
surface roughness, as described above.
[0077] The slots 158 can be configured to increase pumping
performance. For example, a plurality of slots 158 can be disposed
laterally adjacent one another and disposed circumferentially
around the shaft, as shown in FIG. 5a. As another example, a
plurality of slots 158 can be disposed longitudinally adjacent one
another along a length of the shaft, as shown in FIG. 5b. In
addition, the plurality of slots can be disposed circumferentially
and longitudinally, again as shown in FIG. 5b. More or larger slots
can increase the volume available for fluid flow, can decrease
fluid losses, and can increase pump performance. Similarly, the
plurality of impeller blades 170 can be laterally adjacent one
another and disposed circumferentially around the shaft, as shown
in FIG. 5a, and/or longitudinally adjacent one another along a
length of the shaft, as shown in FIG. 5b.
[0078] The slots 158 or blades 170 can be configured to improve
pump performance. For example, the slots or blades can have a
leading or trailing edge 214 that is flat and oriented parallel
with the axis of rotation of the shaft, as shown in FIG. 5f. As
another example, the leading or trailing edges 218 can have a
concave curvature, as shown in FIG. 5a. Alternatively, the leading
or trailing edge can have a convex curvature.
[0079] The slots or blades 220 can be arcuate, or have a curvature,
in a plane perpendicular to the axis of rotation, as shown in FIG.
5g. The curvature can be oriented to curve forward or backward with
respect to the direction of rotation of the shaft. For example, an
experimental backward curved 4-blade impeller was fabricated with
.beta.1 and .beta.2 angles of 80 and 85 degrees respectively. As
another example, an experimental forward curved 4-blade impeller
was fabricated with .beta.1 and .beta.2 angles of 144 and 114
degrees respectively. In addition, the blades 220 can be narrower
than the slots to increase the area through which the fluid can
pass.
[0080] In addition, the slots 158 or blades 170 can be configured
to enhance heat transport near the surface. For example, the
leading or trailing edges can have a similar or different surface
roughness.
[0081] Furthermore, the impeller blades can be configured to extend
into the hollow interior.
[0082] Referring to FIG. 5f, an end surface 230 of the hollow
cavity 154 proximate the slots 158 can have a protrusion 234 to
guide flow to the at least one slots. The protrusion 234 can have a
concave curvature, as shown. In addition, the walls of the hollow
cavity 154 can have a similar curvature leading into the slots.
[0083] Referring to FIG. 6a, the volute 186 can be configured to
facilitate flow from the shaft or impeller blades. The volute 186
can have a volute wall 240 with a concave curvature surrounding a
portion of the shaft, and extending in an open configuration to
allow the flow to exit the volute into the exit plenum 190, or
outlet. Thus, there is an unobstructed channel between the volute
and the plenum, and the volute wall extends outward from the shaft
without narrowing.
[0084] An experimental pump was built with a rotatable shaft 150
with a 2.38 mm outer diameter and a hollow cavity with a 1.17 mm
inner diameter. The rotatable shaft 150 was mounted using bearings
174 and 178 located above and below the exit plenum 190, which are
mounted in the pump housing 14c. The volute 186 and an outlet
channel are then located in the region between the upper and lower
bearings 174 and 178 and pump housing 14c. There can be a
continuous channel, from the inlet tubing, through the pump housing
and top of the upper bearing to the inlet of the shaft. Inside the
channel through the upper bearing, the fluid flow transitions from
a non-rotating bearing wall to the inside of a rotating shaft. The
bearing forms a seal for the spinning shaft, which reduces the
leakage from the impeller outlet to the shaft inlet. The side walls
of the volute and part of the outlet channel for an experimental
pump were formed by a piece of machined brass shim stock that is
416 .mu.m tall. This volute and outlet channel can be aligned with
the slot ports of the shaft. With this construction, when the shaft
spins, centrifugal forces from the spinning impeller shaft force
fluid flow through the shaft inlet, through the interior of the
shaft, through the slots, out through the slot ports, into the
volute, and then into and through the outlet channel. The volute
design shown in FIG. 6a has been found to minimize the effects of
surface forces, and is referred to as an open volute design. The
open volute design is characterized by a large "open" channel from
the impeller to the exit plenum, or outlet. Alternative volute
designs are shown in FIGS. 6b-6d.
[0085] The volute 186 can efficiently direct fluid toward the
outlet channel. The volute designs employed in macroscale pumps,
where fluid motion is induced by inertial forces, are different
from the design employed here. This design difference is because
flow from the impeller exit and within the volute is significantly
influenced by both inertial forces and surface forces. The present
open volute design increases the width and maximizes the hydraulic
diameter thereby decreasing the average fluid velocity and velocity
gradients, which also reduces viscous losses.
[0086] The pump 10c advantageously includes the impeller integrated
into the body of the shaft, instead of on the top of the shaft.
This design is simple, and allows it to be easily manufactured at
low cost. In addition, the problems of tip blade clearance and flow
leakage around the blade tips are not present. As stated above, an
important dimension of many macro-scale centrifugal pumps is the
gap distance between the top of the blades, and the pump housing.
As the gap increases, there is more leakage across blades, and the
overall hydraulic efficiency of the pump decreases. If the gap is
too small or zero, the blades can be damaged by contacting the pump
housing. On a macro-scale this "gap problem" is generally
insignificant, but on a micro-scale, or a millimeter-scale, the gap
between the top of the blades and the pump housing can be about the
same as the height of the impeller blades.
[0087] The design of the rotary shaft pump (RSP) eliminates this
"gap problem." The shaft or impeller can be constructed by boring a
hole in the end of a shaft, and then cutting slots in the side of
the shaft at the bottom of the bored hole. Thus, the material
between the slots acts as the blades of the impeller, and the slots
form passages between the bored interior and outer shaft surface.
The gap at the top of the blades is zero, because the top of the
blades also connects to the shaft. The hollow interior of the shaft
transfers momentum to the passing fluid through viscous forces.
This "pre-swirl" can be significant on a millimeter-scale or
micrometer-scale, when the ratio of the hollow interior length to
diameter is large, and the circumferential wall velocity is greater
than the average axial fluid velocity. The "pre-swirl" aids in the
overall fluid pumping by reducing the sudden acceleration of the
fluid at the inner blade tip.
[0088] An experimental rotary shaft pump was fabricated with five
main parts: 1) the impeller or shaft 150, 2) top housing, 3) bottom
housing, 4) bearings 174 and 178, and 5) volute 186. Fabrication of
the impeller 150 can be realized using precision machining
techniques. A lathe can be used to obtain the desired outside
diameter of the shaft, and to bore the hole in the end of the
shaft. The cone shape at the inlet of the shaft can be made using a
center drill. Slots can then be cut into the side of the shaft
using a milling machine and an indexing tool. The impeller can be
made from 304 stainless steel. Five impeller designs were
constructed for testing: 1) radial 2-blade, 2) radial 4-blade, 3)
radial 6-blade, 4) backward curved 4-blade, and 5) forward curved
4-blade. The blades were evenly spaced around the circumference of
the shaft. The blades on the impellers were evenly spaced, and were
0.38 mm tall (the slots are 0.38 mm tall). The backward curved
4-blade impeller has .beta.1 and .beta.2 angles of 80 and 85
degrees respectively. The forward curved 4-blade impeller has
.beta.1 and .beta.2 angles of 144 and 114 degrees respectively. The
above described parts can be integrated together to produce the
same features with fewer parts. For example, the volute can be
integrated into the top housing. As another example, the bearing
material can be the same material as the top housing, such that the
top housing and top bearing are the same piece.
[0089] The top housing 202 was made from acrylic to allow the flow
passing into and through the pump to be visualized. The top housing
contains the upper bearing 174 and can have an inlet channel and
outlet channel. The ends of clear plastic tubes can be press-fit
into the holes. The bottom housing 206 was made from aluminum, and
contains the lower bearing 178. The bottom housing can also have a
recess that forms the exit plenum 190. The expansion of the fluid
channel as it enters the exit plenum slows the fluid, and minimizes
losses as the fluid turns to the outlet channel.
[0090] The bearings were made from Torlon, a strong
self-lubricating plastic. The upper and lower bearings were
press-fit into the top and bottom housing respectively. Torlon is
used because it has a low coefficient of friction, and can be
easily machined. The outer diameter of the bearings was 6.35 mm,
and the inner diameter was 2.38 mm.
[0091] The volute 186 was machined from brass shim stock using a
CNC milling machine. Each piece of brass shim stock was 104 .mu.m
thick. Thus the height of the volute can be changed by stacking
pieces of brass shim stock. For all of the present tests, a height
of 0.416 mm was used because it is just larger than the height of
the slots located in the shaft.
[0092] The pump can be assembled by connecting the impeller shaft
150 to the coupling shaft on the motor. The volute 186 can then be
positioned and secured in place. The top housing 202 can then be
secured, and tightened to minimize leakage. The inlet and outlet
tubes can then be connected to the top housing. The air can be bled
from the system.
[0093] As described above, the shaft can be operatively coupled to
a motor. The experimental pumps were powered by an externally
mounted Maxon EC32 number 118891, brushless DC motor that is 32 mm
in diameter, with an 80 Watt power rating. The maximum speed is
25,000 rpm, with a stall torque of 0.35 N-m. The maximum testing
speed was limited by the maximum speed of the optical encoder
(14,000 rpm) attached to the motor shaft. The brushless motor was
controlled by an Advanced Motion Controls power amplifier (Model
#BE12A6). The power amplifier has a DC supply voltage of 40V, a
peak current of 12 Amps, and continuous current rating of 6 amps. A
negative feedback controller was employed to maintain constant
speed for any variation in torque. The speed was controlled by
adjusting a 15-turn potentiometer. The speed range is 100-13,200
rpm. The motor controller determines the rotational speed from the
signal from an optical encoder attached to the motor shaft. This
apparatus produces a voltage signal that is proportional to speed.
The voltage was measured using a Keithley 131 Digital
Multimeter.
[0094] Experimental pumps were tested with experimental impeller
designs include radial 2-blade, radial 4-blade, radial 6-blade,
backward-curved 4-blade, and forward curved 4-blade arrangements.
The fluid flow for each impeller design was throttled using outlet
tubing diameters of 0.254 mm, 0.508 mm, and 1.397 mm of the same
length.
[0095] Referring to FIG. 4d, variations of pressure head with
volumetric flow rate are shown for the pumps, all for an impeller
rotational speed of 9,240 rpm. The data was obtained by throttling
the flow in the rotary shaft pump experiments by changing the
inside diameter of the outlet tubing. The data for each pump
arrangement (from left to right) correspond to outlet tubing inner
diameters (D) of 0.254 mm, 0.508 mm, and 1.397 mm, respectively.
For each impeller configuration (operating at constant impeller
rotational speed), FIG. 4d shows that increasing the exit tube
diameter gives a higher volumetric flow rate through the pump,
which, for the impellers tested, gives lower magnitudes of pressure
head. Qualitative trends of FIG. 4d data for each impeller
configuration (at constant impeller rotational speed) are similar
for Q>2 ml/minute. Here, different data sets have similar
slopes, sometimes with different ranges of pump head. At lower
volumetric flow rates, data sets for different impeller
configurations sometimes show completely different slopes, as well
as different quantitative trends. Overall, data trends shown in
FIG. 4d are similar to ones also observed at impeller rotational
speeds of 1,320 rpm and 13,200 rpm. Pressure head magnitudes
produced by the impeller generally decrease as the flow rate is
increased (as outlet tubing diameter increases) for a constant
rotational speed. This is associated with a decrease of hydraulic
efficiency, which is related to overall impeller behavior, and to
increased hydrodynamic losses and increased slip as flow rate
increases. The nearly parallel nature of the pressure rise and flow
rate trends for the different impeller blade designs indicates that
these overall slopes are independent of impeller blade design. The
impeller blade design thus appears to affect the magnitude of the
product of hydraulic efficiency and slip factor, but not overall
slopes of the pressure-flow rate data.
[0096] The above-described experimental pumps produced flow rates
up to 64.9 ml/min. This value is larger than many other micropumps
of similar size, which generally reach flow rates only up to about
16 ml/min.
[0097] The centrifugal pumps described above advantageously have
high efficiency and reduce the possibility of breaking
micro-blades. For example, the centrifugal pumps can have 80%
hydraulic efficiency at 2 ml/min flow rate. Traditional centrifugal
pumps can require impeller blades to be positioned close to the
stationary top of the pumping chamber, but with a gap that lowers
the efficiency. Reducing the gap increases the risk that the blades
impact the top of the pumping chamber, breaking the blades or
causing other damage. The centrifugal pumps described above,
however, essentially have a gap of zero between blades and the top
because the top directly above the blades is also part of the
shaft. In addition, the centrifugal pumps described above can be
easily manufactured.
[0098] A larger-scale experimental pump was tested. The pump
impeller was 25.4 mm in diameter. The volute was machined into the
top housing with a depth of 3.81 mm, such that the volute and top
housing were one piece. The pump was tested with an outlet tubing
inner diameter and length of 9.525 mm and 300 mm respectively. The
rotational speeds tested were 1500-3300 rpm. The maximum flow rate
achieved was 3200 ml/min, with a maximum pressure of 7.6 kPa.
[0099] While the foregoing examples are illustrative of the
principles of the present invention in one or more particular
applications, it will be apparent to those of ordinary skill in the
art that numerous modifications in form, usage and details of
implementation can be made without the exercise of inventive
faculty, and without departing from the principles and concepts of
the invention. Accordingly, it is not intended that the invention
be limited, except as by the claims set forth below.
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