EP2920470B1

EP2920470B1 - Pump

Info

Publication number: EP2920470B1
Application number: EP13799343.2A
Authority: EP
Inventors: Justin Rorke Buckland; Richard Wilhelm Janse Van Rensburg; Alex William WILBER
Original assignee: Technology Partnership PLC
Current assignee: Technology Partnership PLC
Priority date: 2012-11-14
Filing date: 2013-11-13
Publication date: 2019-09-25
Anticipated expiration: 2033-11-13
Also published as: GB201220471D0; EP2920470A1; WO2014076474A1; US20150285270A1

Description

This invention relates to a pump in which fluid is propelled by the oscillating motion of a flap. The flap is contained within a flow channel with side walls substantially parallel to the flap. In use, the flap motion generates a series of counter-rotating vortices which interact with the side walls, with the flap and with each other to generate a fluid flow. The vortices also have a mixing function and the pump can be used to exchange heat between the fluid being pumped and the side walls. The pump can also be used as a mixer to combine two inlet fluid flows to form a well-mixed outlet fluid flow.
We use the term fluid to refer to both gases and liquids. We use the term pump to refer to a device to create a flow of a fluid from an inlet to an outlet where the outlet pressure is higher than the inlet pressure, including liquid pumps, air pumps and air fans.
Rotating fans and pumps are well known for pumping gases and liquids. However the efficiency of these pumps tends to decrease as their size becomes small (typical dimensions of less than 5cm), due to motor losses, bearing friction, viscous drag and blade tip leakage. The use of a rotating mechanism requires a bearing which may need lubrication, have a limited lifetime, or be vulnerable to dust.
Rotating fans and pumps are not well suited to generating in-plane fluid flow in thin devices, as axial flow fans and pumps generate flow perpendicular to their plane of rotation, and centrifugal fans and pumps require an axial inlet flow and tangential outlet flow. Therefore it is difficult to package rotating fans in a thin format suitable for laptop computers, portable electronic devices, and heat exchangers for semiconductor devices.
Rotating fans and pumps are often used to provide a fluid flow through a heat exchanger containing a set of heated or cooled fins. Use of separate fluid moving and heat exchange parts requires additional space and leads to reduced heat exchange performance by not making use of rotational fluid flows generated by the pump or fan to enhance thermal mixing and heat exchange performance.
Rotating fans and pumps usually have rotation speeds and blade passing frequencies in the audible range (100Hz to 20kHz), generating periodic noise. Rotating fans and pumps may also require high blade tip velocities (often greater than 10m/s), generating noise with a broad frequency spectrum. These noise sources can be undesirable in many situations.
Oscillating flap fans and pumps are known, in particular piezoelectric fans which often operate at frequencies of 50Hz or 60Hz. The low frequency requires a large amplitude of motion to achieve flap velocities of >1m/s which are typically required to generate significant flow. The large amplitude of motion limits use in thin devices. Currently known piezoelectric fans may be combined with a heat exchanger but are not optimised in choice of flow channel geometry surrounding the flap, oscillation frequency and amplitude, and use of aerodynamic flap profiles. This combination of factors results in currently known piezoelectric fans generating relatively weak fluid flows, in particular with low stall pressure.
The aim of the present invention is to overcome the disadvantages of the fans and pumps described above.
This invention relates to a fluid pump in which a substantially planar flap is positioned within a flow channel having an inlet and an outlet and bounded by two side walls. The side walls extend from the inlet to the outlet and are substantially planar and parallel to the flap. The height of the flow channel, h, is defined by the separation of the side walls.
The flow channel may also be bounded by a second pair of walls perpendicular to the side walls and parallel to the flow direction. We use the term edge walls to refer to this second pair of walls. The edge walls extend along the length of the flow channel from the inlet to the outlet. Preferably the flap extends across the entire width of the flow channel, save for a small gap to avoid contact between the flap and the edge walls.
The flap and flow channel may have several forms: rectangular, sector annular where the sector angle is less than 360°, or full (360°) annular. In the sector annular and full annular cases, the direction of fluid flow is in a radial direction and the lengths of the flap, side walls, edge walls and flow channel mean their respective dimensions in a radial direction and the widths of the flap, side walls and flow channel mean their dimensions in a circumferential direction.
The flow channel has height h and is bounded by side walls with length l_w and width w_w and separation h, where l_w > h and w_w > h.
The flap has length l_f in the direction parallel to the fluid flow and width w_f in the direction perpendicular to the fluid flow such that w_f > h and preferably l_f > 2h and w_f > 2h. In the case of a flap having a sector annular or full annular form, the width of the flap w_f is taken to be the length of the edge of the flap nearest the outlet, taken along a circumferential path.
The pump may exploit a geometric flow velocity amplification effect in which the ratio of fluid flow velocity to flap velocity increases in proportion to l_f /h, so it is preferable to increase the ratio l_f /h in order to increase pump performance.
It is also preferable to minimise fluid flows in directions perpendicular to the flow direction as these are wasteful and may reduce the pump performance and efficiency. These perpendicular flows may occur between the sides of the flap and the edge walls of the flow channel, and their negative impact on pump performance and efficiency can be reduced by increasing the ratio of the flap width w_f to the flow channel height h such that w_f > 2h. It follows that the flow channel width which is wider than the flap it encloses is also substantially greater than the flow channel height.
In order to generate a strong flow and pressure rise, it is important that the side walls extend downstream of the flap by a distance l_d where l_d > l_f /2 and preferably l_d > 2h. Within the length l_d downstream of the flap the side walls are continuous and the flow channel between the side walls is substantially free from additional structures. The substantially unobstructed flow channel downstream of the flap is required to allow space for interactions of vortices with each other and with the side walls. These interactions generate a pressure rise downstream of the flap and increase the pump performance.
Individually some of these features are known in the prior art:

US 4498851 describes oscillating flaps to generate a fluid flow.
US 4923000 shows walls parallel to flaps but not extending downstream of the flap.
US 5861703 shows walls parallel to flap but not extending significantly downstream of the flap.
US 7321184 shows walls perpendicular rather than parallel to the flap.
US 4834619 shows walls downstream of the flap and parallel to the flap but not forming a flow channel surrounding the flap.
FR2528500A1 shows an oscillating flap in a flow channel, but the flow channel does not have an unobstructed region downstream of the flap.
JP2002339900A shows an oscillating flap in a flow channel, but the downstream region of the flow channel contains additional structures and which form smaller channels not satisfying the condition that channel width is substantially greater than channel height. US20110064594A1 also cites the design described in JP2002339900A as an example of prior art.
JPH0312493U shows an oscillating fan in a channel with square cross-section, while the current invention requires a flow channel and flap with width greater than the height. Additionally, JPH0312493U shows inlets beside the flap while the current invention requires side walls in this region.
US5941694A shows multiple flaps in a flow channel but these flaps to not have an unobstructed region of flow channel extending downstream by more than twice the side wall separation.

A flow channel with an unobstructed region immediately downstream of the flap is required to provide a space for interaction of vortices with each other and with the side walls to provide a pressure rise downstream of the flap and thereby to improve the pump performance. In this invention we describe a combination of geometry of flow channel and geometry and motion of oscillating flap that is required for high pump performance, and this combination is not known in the prior art.
A further benefit of the unobstructed region of flow channel downstream of the flap is to provide space for the vortices to mix the fluid, which is useful in the case where the pump acts as a mixer or heat exchanger.
The pump is equipped with an actuator which provides an oscillating force or torque to drive oscillatory motion of the flap.
In use, the direction of flap motion is substantially perpendicular to the side walls and the motion of the flap has larger amplitude near the outlet than near the inlet, causing the flap to create and shed vortices in the fluid being pumped, with interaction of the vortices with each other, with the flap and with the side walls creating a fluid flow and pressure rise downstream of the flap. The side walls contain the vortex street generated by the flap oscillation and increase the fluid flow and pressure, compared to a piezoelectric fan not provided with side walls of the geometry shown in Figure 1.
The mechanism of generating fluid movement for propulsion by oscillating motion of flaps or aerofoils is well known in nature and is used by fish and birds for swimming and flying. This mechanism has also been investigated for ship propulsion and for micro-aerial vehicles. In the present invention, the flapping propulsion mechanism is enhanced by providing static side walls that extend downstream of the oscillating flap.
A qualitative explanation of the flow generation mechanism is given below, in terms of vortices generated by the flap and their interactions with the side walls. The side walls can be conceptually replaced by image line and sheet vortices. The image line vortices have the opposite sense of rotation to the real vortices in the flow channel, such that the wall-perpendicular velocity components of a real and image vortex pair sum to zero. The image sheet vortices at the wall locations provide zero slip at the walls. These vortex sheets occur in pairs separated by stagnation points at the wall. The sheet vortices exert shear forces on the fluid in the flow channel and diffuse into the flow channel at a rate depending on the fluid viscosity. The net effect of the sheet vortices is to exert a downstream force on the fluid, causing fluid in the flow channel to move from the inlet to the outlet.
The cross-section of the flap and flow channel perpendicular to the width direction may be substantially uniform across the width of the pump, so that different designs with increased or decreased width and flow rate can be created easily and can share common manufacturing processes.
The flap may have an aerodynamic or aerofoil shape or a thin trailing edge to enhance vortex formation and shedding and to reduce drag.
There may be a piezoelectric or magnetostrictive bending actuator incorporated into or mounted on the flap.
The flap may be driven by a remote actuator using a mechanical connection or a hydraulic or pneumatic drive.
The flap may be driven by electrostatic or magnetic forces.
The flow channel inlet may be divided into two regions to combine two fluid inlet streams, such that in use, the motion of the flap generates vortices and causes the two inlet fluid streams to be pumped and mixed downstream of the flap.
There may be a temperature difference applied between one or both side walls and inlet fluid stream, such that in use, the motion of the flap generates vortices causing the inlet fluid stream to be pumped and to exchange heat with one or both side walls, with the circulating flow of the vortices enhancing heat transfer. The motion of the flap may be driven at ultrasonic frequencies (>20kHz) to provide operation inaudible to humans.
The motion of the flap may be driven at low frequencies (<400Hz), below the frequency of peak sensitivity of the human ear, to provide quiet operation
The flap may have maximum peak-to-peak displacement, A, between 10% and 70% of the side wall separation. In any case, it is preferable that the flap does not impact the side walls during operation.
The flap oscillation frequency, f, may be chosen to give a Strouhal number, St = f A / U between 0.1 and 0.5, where U is the average fluid flow speed in the flow channel. A Strouhal number in this range is found to provide efficient propulsion for a wide range of swimming and flying animals.
The amplitude of flap motion may be amplified by mechanical resonance of the flap.
The flap may be clamped at the edge near the inlet. Alternatively the flap may oscillate with fixed centre of mass and be supported by two pivot supports at nodal locations, or the flap may be supported by a flexible vibration isolating support.
An electromechanical actuator mounted on the flap may be provided with electrical connections using flexible support wires, or by a flexible circuit acting as a vibration isolating support.
The flap may have a flexible construction such that fluid loading causes non-sinusoidal motion of the flap.
The pump may contain two or more flaps, where the flaps move with out of phase motion to avoid noise and vibration.
The flap may be fabricated from a folded sheet metal structure with a laser-welded seam.
The pump may consist of an array of oscillating flaps contained within flow channels. A single actuator may drive multiple flaps.
The pump may contain an array of multiple flaps fabricated from a single sheet.
The pump may contain an array of flaps supported by a common support frame.

Description of the figures

Figure 1 shows a fluid pump 1 comprising a flow channel 10 with an inlet 2 and outlet 3. The flow channel is bounded by side walls 4 and edge walls 6. The flow channel contains a flap 8 with actuator 9 attached to the flap. The flap has length l_f and width w_f where preferably w_f > 2h. The side walls and flow channel extend downstream of the flap by a distance l_d , where l_d ≥ l_f /2 and preferably l_d > 2h. It is preferable for the flap length l_f to satisfy the condition l_f > 2h. The side walls have length l_w and width ww and satisfy the relationships l_w > h and w_w > h.
Figure 2 shows a plan view of the pump and flow channel, showing inlet 2, outlet 3, edge walls 6, flap 8 and actuator 9 attached to the flap.
Figure 3A shows a side view of the pump and flow channel, showing inlet 2, outlet 3, side walls 4, and flap 8. The flap oscillates towards the side walls and the extreme positions of the flap are shown by dashed lines. The motion of the flap is larger at the end nearer the outlet 3 and this motion generates a series of counter-rotating vortices 5 forming a reverse von Kárman vortex street. In an inviscid approximation, the side walls can be replaced by image vortices 12 with opposite sense of rotation to the real vortices 5. Figure 3B shows the variation of pressure with position along the flow channel. There is a pressure rise from inlet to outlet, indicating fluid pumping function. A substantial part of the pressure rise Occurs downstream of the flap due to the interaction of the vortices with the side walls and due to the interactions of alternating vortex pairs which form jet flows oriented downstream.
Figure 4 shows three forms of the pump in plan and section views, with the fluid flow directions indicated by arrows. Figure 4A show a rectangular form pump. Figure 4B shows a sector annular form pump, with the same topology as the rectangular for pump but formed into a curved shape. Figure 4C shows a full annular form pump in which the air flows radially outwards. It is also possible to create an annular pump in which the inlet and outlet locations are reversed with respect to those shown in Figures 4B and 4C, and the flap is arranged so as to generate a radial flow travelling inwards towards the inner edge of the pump.
Figure 5A shows a con Karman street created by flow past a cylinder. The bluff body generates a drag wake composed of staggered counter-rotating vortices with interspersed jet flow oriented upstream. Figure 5B shows a streamlined foil which generates a reverse von Karman street. This actively generated wake produces jet flow between alternating vortex pairs that is orientated downstream (as described in INTED. AND COMP. BIOL., 42:243-257 (2002)).
Figures 6A and 6B illustrate the fluid flow in the flow channel at two points in time. Fluid velocity is indicated by arrows and contours of magnitude of vorticity are indicated by solid lines. The flap is also shown. Figure 6B illustrates the fluid flow and flap position at time approximately one quarter period of flap oscillation later than Figure 6A. Each vortex generates a vortex sheet at the wall to counter slip velocity induced by an image vortex of the type described in Figure 3. Generation of a new vortex pulls the previous vortex over to same ide, so the resulting vortex pair generates a pair of wall sheet vortices of opposing senses separated by a stagnation point. The pair of sheet vortices exert shear forces on the fluid with opposite directions, but the downstream shear forces dominate creating a net downstream force on the fluid and generating a fluid flow.
Figure 7A shows fluid motion generated by an oscillating flap 8. Time-averaged fluid flow is from left to right and vortices 5 generated by the oscillating flap are shown downstream of the flap. Figure 7B shows temperature contours 31 in the fluid flow generated by an oscillating flap in the case where there is a temperature difference between heated or cooled side walls 29 nd the fluid at the inlet 2. Upstream of the flap a boundary layer 30 grows in thickness, slowing heat transfer. Downstream of the flap, vortices disrupt the boundary layer and speed up heat transfer.
Figure 8A shows the cross-sectional shape of an aerodynamically shaped flap 8. Figure 8B shows a similarly shaped flap containing a bending actuator containing a piezoelectric or magnetostrictive layer 13 and an elastic layer 14. The aerodynamic shape can be created by folding a sheet of material 16 and joining the sheet to itself at a line 15 located between the bending actuator and the downstream end of the flap.
Figure 9 shows two oscillating flaps 8 driven by a single actuated rod 17 connected to each flap by a pivot support 18. Clamps 19 prevent movement at one end of the flaps, while the couple generated by the combination of clamping force and driving force causes motion at the other end of the flaps.
Figure 10 shows a pump with two inlets 20, 21 and one outlet 3. Flow is driven from the inlets to the outlet by an oscillating flap 8 which also causes the inlet fluid flows to become mixed by the vortex-rich flow generated by the oscillating fan.
Figure 11A shows an oscillating flap 8 supported by a clamp 19 at one end and oscillating in a fundamental bending mode at the other end. Figure 11B shows an oscillating flap 8 vibrating about its centre of mass, supported by two pivot supports 23 which do not constrain the angle of the flap, and with a mass 22 attached to one end of the flap such that the amplitude of motion at the other end of the flap is larger.
Figure 12 shows a heat exchanger with inlet fluid flow 25 driven by oscillating fans 8 between static walls 4. The static walls are in thermal contact with pipes 24. The pipes may contain a pumped circulating flow of heat-carrying fluid, or they may be heat pipes containing liquid and vapour transported by evaporation and condensation processes and capillary forces, or they may be solid conductors. Figure 12A shows a side view and Figure 12B shows a plan view.
Figure 13 shows a heat exchanger 28 with integrated array of fans 8 and static walls 4 which also serve as heat sink fins, conducting heat to or from the base of the heat exchanger 27. A fluid flows from the inlet 2 to the outlet 3. When used as a heat sink, heat flows from the fins to the fluid. When used as a device to cool a fluid, heat flows from the fluid to the fins. The motion of the fins 8 is indicated by dotted lines and is substantially perpendicular to the static walls.
Figure 14 shows load curves for an oscillating fan device driven at voltages from 40Vpp to 140Vpp using a piezoelectric bimorph bending actuator oscillating at approximately 250Hz. In this case fluid being pumped is air and the approximate dimensions of the device are:

side wall separation, h: 9mm

flap width, w_f : 63mm

flap length, l_f : 31mm

side wall width, w_w : 64mm

total side wall length, l_w : 80mm

downstream length, l_d : 49mm

Figure 15 compares the heat transfer provided by the oscillating fan with the heat transfer provided by a conventional rotating fan, as a function of air flow rate through a heat exchanger. The oscillating fan provides significantly greater the heat transfer than a rotating fan operating at the same air flow rate.
Figures 16, 17, 18, 19, 20 and 21 show examples of the prior art.

Claims

A fluid pump comprising:
a flow channel (10) containing an fluid inlet (2) and a fluid outlet (3) and bounded by two side walls (4),

a substantially planar flap (8) positioned inside the flow channel (10), and

an actuator (9) capable of transmitting an oscillating force or torque to the flap (8),

the fluid pump being characterised in that the side walls (4) extend from the inlet (2) to the outlet (3) and are substantially planar and parallel to the flap (8) and extend beyond the downstream end of the flap (8) towards the outlet (3) by a distance, l_d, such that l_d ≥ l_f /2, where l_f is the length of the flap, and

where the side wall separation, h, length, l_w, and width, w_w, satisfy the relationships: l_w > h and w_w > h,

whereby in use, the actuator (9) drives oscillatory motion of the flap (8) in a direction substantially perpendicular to the side walls (4) with motion of the flap (8) having larger amplitude near the outlet (3) than near the inlet (2).
A pump according to claim 1, where the region of flow channel (10) between the flap (8) and the outlet (3) is substantially unobstructed.
A pump according to any of the above claims, where the flap length l_f satisfies the condition l_f > 2h.
A pump according to any of the above claims, where the side walls (4) extend beyond the downstream end of the flap (8) towards the outlet (3) by a distance l_d such that l_d > 2_h.
A pump according to any of the above claims, where the where the flap width, w_f , satisfies the condition w_f > 2h.
A pump according to any of the above claims, where the flap (8) and flow channel (10) have sector annular forms, or where the flap (8) and flow channel (10) have full annular forms.
A pump according to any of the above claims, where motion of the flap (8) causes creation and shedding of vortices into the fluid being pumped, with interaction of the shed vortices with the side walls (4), with each other and with the flap (8) creating a pressure rise downstream of the flap (8).
A pump according to any of the above claims, where the flap (8) has an aerodynamic or aerofoil shape or a thin trailing edge, and, preferably, has substantially uniform cross-section perpendicular to the width direction.
A pump according to any of the above claims, where a piezoelectric or magnetostrictive bending actuator (9) is incorporated into or mounted on the flap (8), or where the flap (8) is driven by a remote actuator using a mechanical connection (17) or a hydraulic or pneumatic drive.
A pump according to any of the above claims, where the flow channel inlet (2) is divided into two regions to combine two fluid inlet streams and, in use, the motion of the flap (8) generates vortices causing the two inlet fluid streams to be pumped and mixed downstream of the flap (8).
A pump according to any of the above claims, where a temperature difference is applied between the side walls (4) and inlet fluid stream, such that in use, the motion of the flap (8) generates vortices causing the inlet fluid stream to be pumped and to exchange heat with one or both side walls (4).
A pump according to any of the above claims, where the motion of the flap (8) is driven at ultrasonic frequencies (>20kHz), or where the motion of the flap (8) is driven at low frequencies (<400Hz).
A pump according to any of the above claims, where the oscillation frequency, f, is chosen to give a Strouhal number, St = f A / U between 0.1 and 0.5, where U is the average fluid flow speed in the flow channel (10).
A pump according to any of the above claims, where the flap (8) oscillates with fixed centre of mass and is supported by two pivot supports (23) at nodal locations or is supported by a flexible vibration isolating support.
One or more pumps according to any of the above claims, including a total of two or more flaps (8), where the flaps (8) move with out of phase motion to avoid noise and vibration.