US20040096345A1 - Fluid pumps with increased pumping efficiency - Google Patents

Fluid pumps with increased pumping efficiency Download PDF

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Publication number
US20040096345A1
US20040096345A1 US10/293,315 US29331502A US2004096345A1 US 20040096345 A1 US20040096345 A1 US 20040096345A1 US 29331502 A US29331502 A US 29331502A US 2004096345 A1 US2004096345 A1 US 2004096345A1
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Prior art keywords
fluid
pumping
piston
strokes
during
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Abandoned
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US10/293,315
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English (en)
Inventor
Nachum Zabar
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MNDE TECHNOLOGIES LLC
MNDE Tech LLC
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MNDE Tech LLC
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Priority to US10/293,315 priority Critical patent/US20040096345A1/en
Assigned to MNDE TECHNOLOGIES L.L.C. reassignment MNDE TECHNOLOGIES L.L.C. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ZABAR, NACHUM
Priority to AU2003276664A priority patent/AU2003276664A1/en
Priority to PCT/IL2003/000929 priority patent/WO2004044421A2/fr
Publication of US20040096345A1 publication Critical patent/US20040096345A1/en
Abandoned legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
    • F04B35/045—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric using solenoids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • F04B17/04—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids
    • F04B17/046—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids the fluid flowing through the moving part of the motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B25/00—Multi-stage pumps
    • F04B25/005—Multi-stage pumps with two cylinders

Definitions

  • the present application relates to fluid pumps.
  • the invention is particularly useful in fluid pumps for pumping air or other gases, and is therefore described below with respect to this application, but it will be appreciated that the invention could also be used for pumping water or other liquids.
  • Fluid pumps are widely used for many applications, including moving fluids from one location to another (translation pumps), compressing the fluid within a container (compression pumps) and reducing the pressure of a fluid within a container (vacuum pumps). Efforts are continually being made to increase the pumping efficiency of such pumps for reducing the power requirements, to make the pumps more compact for reducing the space requirements, and/or to simplify the structure of the pumps for reducing the manufacturing and maintenance costs.
  • An object of the present invention is to provide a fluid pump having advantages in one or more of the above respects, as will be described more particularly below.
  • a fluid pump comprising: a housing having an inlet, an outlet, a passageway connecting the inlet and outlet, and a compartment in the passageway; a piston disposed within a compartment and defining therewith a fluid-charging chamber on one side of the piston and a fluid-pumping chamber on the opposite side of the piston; the piston being reciprocatable in the compartment through forward-pumping strokes and return strokes; the piston being formed with an opening therethrough establishing communication between the chambers and including a one-way valve effective to close the opening through the piston during the forward-pumping strokes and to open the opening during the return strokes; and further valve means effective: to open the inlet with respect to the fluid-charging chamber during the forward-pumping strokes, to close the inlet with respect to the fluid-charging chamber during the return strokes, to open the outlet with respect to the fluid-pumping chamber during the forward-pumping strokes, and to close the outlet with respect to
  • a fluid pump constructed in accordance with the foregoing features is to be distinguished from other types of fluid pumps also including one-way valves through their pistons, such as described in Hammond U.S. Pat. No. 883,457.
  • the fluid-charging chamber at one side of the piston is expanded during the forward-pumping strokes, and is contracted during the return strokes to pressurize the fluid within that chamber and thereby, by the opening of the piston valve, to supercharge the fluid-pumping chamber before the start of the forward-pumping strokes.
  • the fluid charging chamber ( 8 ) is not expanded during the forward-pumping strokes, but rather is contracted during the forward-pumping strokes, and is expanded during the return strokes.
  • the inlet one-way valve ( 6 ) is normally closed during the forward-pumping strokes, rather than during the return strokes, unless that valve is held open by presetting a cam ( 17 ).
  • the volume of the fluid-pumping chamber is greater than that of the fluid-charging chamber.
  • the piston stem is located in the fluid-charging chamber and occupies a part of the volume of that chamber.
  • volume of the fluid-pumping chamber is less than that of the fluid-charging chamber. This can be done by providing the piston with a cylindrical section of smaller diameter than the piston and located in the fluid-pumping chamber such that the effective volume of the fluid-pumping chamber is less than that of the fluid-charging chamber.
  • the housing of the fluid pump includes a linear drive for reciprocating the piston through the forward and return strokes.
  • the drive is the linear electromagnetic drive described in my International Application No. PCT/IL02/00313, filed 18 Apr., 2002, Published ______, as International Publication No. ______.
  • the embodiments of the invention described below therefore include such a drive.
  • fluid pumps constructed in accordance with the foregoing features are capable of operating at relatively high efficiency, thereby reducing the power requirements. They are also capable of being implemented in compact constructions, thereby reducing the space requirements. Further, they are capable of being constructed of a relatively few simple parts which can be produced in volume and at relatively low cost, thereby reducing the manufacturing and maintenance costs.
  • FIG. 1 is a longitudinal sectional view illustrating one form of fluid pump constructed in accordance with the present invention
  • FIGS. 2 a, 2 b and 2 c illustrate the reciprocatory movements of the armature of the linear electromagnetic drive in the fluid pump of FIG. 1;
  • FIG. 3 is a diagram illustrating how an increase in efficiency is obtainable in a fluid pump constructed in accordance with the present invention as compared to a typical prior art construction
  • FIG. 4 is a longitudinal view illustrating a two-stage fluid pump constructed in accordance with the present invention.
  • FIG. 5 is a longitudinal sectional view illustrating a third fluid pump constructed in accordance with the present invention.
  • FIG. 6 is a longitudinal sectional view illustrating a still further fluid pump constructed in accordance with the present invention.
  • FIG. 1 illustrates one form of fluid pump constructed in accordance with the present invention.
  • a fluid pump includes a linear electromagnetic drive of the construction described in my above-cited International Patent Application No. PCT/IL02/00313, and therefore such a drive is included in the fluid pump illustrated in FIG. 1.
  • the operation of such a drive will be better understood by reference to FIGS. 2 a - 2 c described below.
  • the advantages obtainable by such a fluid pump will be better understood by reference to the diagrams of FIG. 3, also described below.
  • the fluid pump illustrated in FIG. 1 includes a housing, generally designated 2 , constituted of a section 2 a for housing a linear electromagnetic drive, and a section 2 b for housing the pump valving elements driven by the electromagnetic drive.
  • the linear electromagnetic device section 2 a includes: a core 3 of magnetically permeable material; a coil 4 wound on a bobbin 5 fixed within the core 3 ; and an armature 6 of magnetically permeable material mounted for bi-directional reciprocatory movement towards and away from one end face of the core 3 .
  • the bi-directional movements of the armature 6 are transmitted as linear movements by a shaft 7 passing through the core 3 to a piston 8 at the opposite side of the device.
  • Piston 8 is movable within a cylindrical compartment defined by two transverse walls 9 , 10 of the fluid valving section 2 b, such that the reciprocations of the piston 8 produce an air pumping action as will be described more particularly below.
  • Armature 6 and its shaft 7 are supported for bi-directional linear movement by a pair of a flat elastic springs 13 , 14 , of disc configuration at the opposite sides of core 3 and connected to the core by a pair of side plates 15 , 16 secured together by axially extending tie rods or long screws 17 .
  • each flat spring is made of elastic sheet material of a circular disc shape and formed with a plurality of coaxial circular arrays of closed, elongated curved slots to impart axial flexibility while providing transverse (radial) stiffness.
  • Piston 8 is secured to one end of shaft 7 by a fastener 18 which passes through the piston and the respective flat spring 13 at that side of the core.
  • the opposite end of shaft 7 is secured to flat spring 14 by another fastener 19 passing through it and an outer collar 19 a.
  • the core 3 of magnetically permeable material has a longitudinal axis LA, an outer section 3 a of cylindrical configuration coaxial with axis LA; a central section 3 b coaxial with axis LA, spaced from the outer section 3 a, and also of cylindrical configuration; and a side section 3 c, perpendicular to axis LA, bridging the other cylindrical section 3 a and the central cylindrical section 3 b at one side of the core (left side, FIG. 1).
  • the opposite side (right side, FIG. 1) of the core is not bridged, but rather is left open.
  • the right side of the core 3 is extended past the coil 4 and bobbin 5 , as shown at 3 d.
  • Coil 4 and bobbin 5 are both spaced inwardly of the open side of the core so as to be completely recessed within the core and to define an annular recess, shown as 20 .
  • the movable armature 6 faces and is aligned with extension 3 d defining the annular recess 20 within core 3 .
  • Armature 6 is movable towards and away from the coil 4 and its bobbin 5 inwardly and outwardly of the annular recess 20 .
  • the outer diameter of armature 6 is slightly less than the inner diameter of the outer core section 3 a at the annular recess 20 .
  • the armature is formed with a central recess 6 a of slightly larger diameter than the outer diameter of the central core section 3 b to define an outer annular section 6 b of the armature receivable within the annular recess 20 of the core 3 during the reciprocatory movement of the armature.
  • Coil 4 is energized by a source of alternating current 30 having a half-wave rectifier 31 effective to energize the coil in half-cycles to drive the armature 6 in one direction, and to de-energize the coil in the remaining half-cycles to permit the pair of flat springs 13 , 14 to drive the armature in the opposite direction.
  • FIGS. 2 a - 2 c illustrating three positions of the armature 6 with respect to the core 3 , as the armature is driven in one direction by the coil during one-half of each cycle, and in the opposite direction by the flat springs 13 , 14 , during the other half of each cycle.
  • Such reciprocatory movements are straight-line movements parallel to the longitudinal axis LA of the core 3 .
  • FIG. 2 a illustrates the initial or normal position (i.e., at the working point) of the armature, also shown in FIG. 1, when coil 4 is deenergized.
  • the outer annular section 6 b of the armature is aligned with the annular recess 20 defined by the outer core section 3 a, the central core section 3 b, the recessed coil 4 and its bobbin 5 .
  • FIG. 2 a illustrates this initial position of the armature as being substantially flush with the outer face of the central core section 3 b. However, this depends on the working point of the electromagnetic device. In some applications the initial position of the armature may be slightly inwardly, and in other applications slightly outwardly, of the outer face of central core section 3 b.
  • FIG. 2 b illustrates the maximum inner position of the armature with respect to the core
  • FIG. 2 c illustrates the maximum outer position of the armature with respect to the core.
  • the outer surface of the armature annular section 6 b which, as described earlier, is of only slightly smaller diameter than the inner diameter of the core outer section 3 a, defines a first working gap WG 1 with the inner surface of the outer section 3 a of the core.
  • Both gaps WG 1 , WG 2 are working gaps, in the sense that they change in dimension during the bi-directional, reciprocatory movements, of the armature 6 , and thereby contribute to the attractive force produced by the magnetic flux flowing through the core 3 .
  • both working gaps WG 1 , WG 2 are of annular configuration.
  • each loop includes the two gaps WG 1 , WG 2 . Both gaps change in length during the movement of the armature 6 as shown in FIGS. 2 a and 2 c, and therefore serve as working gaps contributing an attractive force with respect to the armature. The provision of two working gaps in each circulating loop of magnetic flux maximizes the mechanical force produced by the device for the electrical power consumed.
  • the reciprocatory movements of the armature 6 , and thereby of the shaft 7 and the piston 8 are linear straight-line movements parallel to the longitudinal axis LA of the core 3 .
  • Such straight line reciprocatory movements produce a more efficient pumping action than angular movements resulting from a pivotally-mounted armature, thereby further maximizing the mechanical force produced by the device for the electrical power consumed.
  • the illustrated construction eliminates the energy loss associated with driving flux through a non-working gap, thereby minimizing power consumption as well as heat generation. Further, the absence of an air space (a non-working gap) between the coil and the core produces better heat dissipation of the heat generated in the coil.
  • a further advantage is that, since no fixed (non-working) gap is required between the coil of the core and the armature, the coil may be of smaller diameter for the same number of turns, thereby decreasing the overall length of the coil wire; alternatively the wire diameter may be slightly increased for the same overall diameter of the core. Either case enables the resistance of the coil wire to be reduced, thereby further contributing to the reduction in the power consumed and the heat generated.
  • non-working gaps are generally provided in existing electromagnetic devices in order to accommodate manufacturing tolerances with respect to relatively movable surfaces during the operation of the armature. Such non-working gaps tend to produce undesirable side forces according to the degree of eccentricity with respect to the relatively movable surfaces. Since non-working gaps are not needed in the above-described construction illustrated in FIGS. 1 and 2 a - 2 c, such side forces may be substantially eliminated, so that the electromagnetic device operates more efficiently and with less wear of the parts thereby, contributing to longer life.
  • valve elements producing the fluid-pumping action are located within the valving section 2 b defined by the two transverse plates 9 , 10 which define a cylindrical compartment within which piston 8 reciprocates.
  • Piston 8 is disposed within this compartment, or cylinder, so as to define therewith a fluid-charging chamber C C on one side (right side, FIG. 1), and a fluid-pumping chamber C P on the opposite side.
  • Piston 8 is reciprocated by shaft 7 through forward-pumping strokes (leftwardly, FIG. 1) and return strokes to produce the fluid-pumping action, as will be described more particularly below.
  • Piston 8 is formed with at least one opening 40 therethrough, preferably a plurality of openings as shown in FIG. 1, establishing communication between the two chambers C C and C P on opposite side of the piston.
  • Each of the piston openings 40 includes a one-way valve V P effective to be closed during the forward-pumping strokes and to be opened during the return strokes.
  • Transverse plate 9 defining the opposite side of the fluid-charging chamber C C is also formed with at least one opening 41 therethrough, preferably a plurality of such openings, each controlled by a one-way valve so as to control the inletting of fluid into the fluid-charging chamber C C ; such one-way valves act as inlet valves and are therefore designated V I .
  • transverse plate 10 defining the opposite side of the fluid-pumping chamber C P is also formed with at least one opening therethrough 42 , preferably a plurality of such openings, each controlled by a one-way valve to control the outletting of fluid from the fluid-pumping chamber C P ; such one-way valves act as outlet valves and are therefore designated V O .
  • the cylinder defined by the two transverse walls 9 , 10 , in which piston 8 is reciprocateable, is in a connecting passageway between a fluid inlet to the housing, and a fluid outlet from the housing.
  • the housing fluid inlet designated 43
  • the connecting fluid passageway from inlet 43 to the fluid-charging chamber C C includes openings 44 through the armature 6 , and an annular passageway 45 between shaft 7 and core 3 .
  • Passageway 45 communicates with inlet openings 41 via the elongated curved slots in flat spring 13 at that (left) side of the electromagnetic drive section 2 a of housing 2 .
  • the fluid outlet from housing 2 is defined by an opening 46 through an outer transverse plate 47 attached to transverse wall 10 .
  • Plate 47 defines with wall 10 a further chamber C D , serving to dampen the pressure pulsations and sounds of the fluid flowing from the pumping chamber C P through openings 42 and outlet 46 during the forward-pumping (leftward) strokes of the piston 8 .
  • the three groups of one-way valves, V P , V I and V O are oriented to operate as follows:
  • the piston one-way valves V P close the piston openings 40 during the forward-pumping (leftward) strokes of the piston, and open openings 40 during the return (rightward) strokes.
  • the inlet one-way valve V I open the path from the inlet 43 to the fluid-charging chamber C C , via armature openings 44 , annular passageway 45 and openings 41 , during the forward-pumping strokes of the piston, and close this path during the return strokes.
  • the outlet one-way valves V O open the path from the fluid-pumping chamber C P to the housing outlet 46 , during the forward-pumping strokes of the piston, and close this path during the return strokes of the piston.
  • such an arrangement enables pressurized fluid to flow from the charging chamber C C into the pumping chamber C P during the return strokes, to thereby supercharge the fluid-pumping chamber C P to a higher pressure before the start of the forward-pumping strokes.
  • FIG. 1 schematically illustrates the one-way valve V P , V I , V O as being simple flapper valves, it will be appreciated that they could be any type of one-way valve, such as an umbrella valve, inertia valve, ball valve, etc.
  • the electromagnetic drive section 2 a of the illustrated fluid pump reciprocates piston 8 through forward-pumping strokes (leftwardly, FIG. 1) and return strokes (rightwardly) with respect to the fluid-charging chamber C C and the fluid-pumping chamber C P .
  • piston 8 moves leftwardly to close one-way valve V P and to open one-way valves V O and V I .
  • the piston pumps the fluid from chamber C P through valves V O and the housing outlet 46 , while at the same time it draws fluid via opening 41 into the fluid-charging chamber C C .
  • piston 8 moves in the opposite direction, i.e., rightwardly, FIG. 1.
  • fluid-pumping chamber C P is immediately expanded, thus causing valve V O to immediately close; in addition, the fluid-charging chamber C C is immediately contracted, thereby causing valve V I to immediately close.
  • valve V P With respect to valve V P , this valve, is in a closed condition at the beginning of the return stroke, but opens during the return stroke according to the pressure on its opposite faces and the biasing pressure, if any, biasing it closed. As soon as valve V P opens during the return stroke, pressurized fluid within the fluid-charging chamber C C passes into the fluid-pumping chamber C P thereby boosting the pressure within the fluid-pumping chamber C P before the start of the next forward-pumping stroke.
  • FIG. 3 is a diagram illustrating the pressure-volume relationship with respect to a fluid pump constructed in accordance with the present invention (curve A) as compared to that of a conventional fluid pump (curve B) not having a supercharged pumping chamber.
  • the displacements illustrated in FIG. 3 are adjusted to produce 3.4 cfm at 3600 cycles per minute.
  • the fluid pump constructed in accordance with the present invention (curve A) supercharges the fluid-pumping chamber C P at about two psig (16.5 psia, assuming no leakage) when the fluid pump is at 20 psig back pressure.
  • a pump constructed in accordance with the foregoing features provides a number of important advantages.
  • a linear reciprocatory drive is generally not as advantageous in a pump as a constant-displacement drive because of the need for more “dead volume” in a linear drive in order to avoid the danger of impact of the piston against the valve plate.
  • the use of a linear reciprocatory drive is particularly advantageous since here the “dead volume” effectively increases the super-charging effect.
  • leakage is not significant at the piston stem, thereby avoiding the need of a seal at the piston stem and the friction produced by such a seal.
  • valves particularly the suction valves, are disposed within the housing, thereby reducing noise.
  • opening of the piston valves during the return strokes not only supercharges the fluid-pumping chamber before the start of the fluid-pumping stroke as described above, but also reduces the load during the return stroke.
  • the fluid being pumped is passed through the interior of the reciprocatory drive, thereby cooling that drive.
  • a fluid pump constructed in accordance with the features illustrated in FIG. 1 is capable of attaining higher efficiency, and therefore of reducing the power requirements.
  • a fluid pump may be constructed very compactly, thereby reducing the space requirements.
  • a fluid pump can be constructed of relatively few simple parts producible in volume and at relatively low cost, thereby reducing the manufacturing costs.
  • FIG. 4 illustrates a two-stage fluid pump, generally designated 100 , constructed in accordance with the present invention.
  • the pump illustrated in FIG. 4 includes a housing having an electromagnetic linear drive coupled at one end to a first valving section 2 b 1 , and at the opposite end to a second valving section 2 b 2 .
  • the drive section 2 a is constructed exactly as described above with respect to FIG. 1, and therefore the same reference numerals have been used to identify it and its corresponding parts, with the subscripts “1” and “2” for the two valving sections “b1” and “b2”, respectively.
  • shaft 7 of the reciprocatory drive section 2 a is coupled at one end to a first piston 8 1 in valving section 2 b 1 , and at the opposite end to a second piston 8 2 in valving section 2 b 2 .
  • each of the two valving sections 2 b 1 , 2 b 2 is of the same construction as valve section 2 b in FIG. 1; and therefore to facilitate understanding, the various parts have also been identified with the same reference numerals but with the subscript “1” and “2”, respectively.
  • the one-way valves in valving section 2 b 1 are identified as V I1 , V P1 , V O1
  • the various chambers are identified as C C1 , C P1 , and C D1
  • the corresponding elements in valving section 2 b 2 are identified as V I2 , V O2 , C C2 , C P2 and C D2 .
  • Valving section 2 b 2 operates in the same manner as described above with respect to FIG. 1, except that in this case its fluid-charging chamber C C2 is supercharged by the pressurized fluid within the pumping chamber C P1 of the first valving section 2 b 1 at the start of the leftward-moving pumping stroke of piston 8 2 .
  • valving section 2 b 2 of the pump illustrated in FIG. 4 operates in the same manner as described above with respect to FIG. 1, except that its fluid-charging chamber C C2 is supercharged by the fluid pumped from valving section 2 b 1 .
  • valving section 2 b 1 acts to supercharge the air supplied to valving section 2 b 2 before section 2 b 2 further supercharges the air pumped therefrom in a manner as described above with respect to FIG. 1.
  • FIG. 4 illustrates the cylindrical chambers of the two pistons 8 1 , 8 2 , as being of the same diameter, preferably piston 8 2 of the second stage 2 b 2 is of smaller diameter since that stage acts on fluid at a higher pressure than the fluid in the first stage.
  • Another minor modification illustrated in the fluid pump illustrated in FIG. 4 is that, instead of having a plurality of one-way valves for each of the two sections 2 b 1 , 2 b 2 , there is only one such one-way valve in each of the two sections.
  • the operation of the fluid pump illustrated in FIG. 5, therein generally designated 200 is basically the same as described above with respect to FIG. 1.
  • Its electromagnetic drive section is the same, and therefore corresponding parts have been identified with the same reference numerals.
  • Its fluid-valving section involves the same basic operation as fluid-valving section 2 b in FIG. 1 but of a slightly different construction. To facilitate understanding, therefore, the corresponding parts in the fluid-valving section of the fluid pump 200 illustrated in FIG. 5 are identified by the same reference numerals as in FIG. 1, but in the “200” series.
  • piston 208 in fluid pump 200 illustrated in FIG. 5 is also coupled to shaft 7 of the reciprocatory drive section 2 a for reciprocation within a cylindrical compartment, and also divides the compartment into a fluid-charging chamber C C and fluid-pumping chamber C P .
  • piston 208 includes a cylindrical section 250 of smaller diameter than that of the piston and located within the fluid-pumping chamber C P such that the effective volume of that chamber is less than that of the fluid-charging chamber C C .
  • Pump 200 illustrated in FIG. 5 is otherwise of basically the same construction as in FIG. 1, including one-way valve V P in piston 208 , one-way valve V I in housing wall 209 , and one-way valve V O in housing wall 210 .
  • the fluid inlet is shown at 219
  • the fluid outlet is shown at 246 .
  • fluid pump 200 illustrated in FIG. 5 operates in basically the same manner as described above with respect to FIG. 1 except for the following principle difference: Since the volume of the fluid-pumping chamber C P is reduced by the cylindrical section 250 of the piston 208 during the return strokes of the piston, when pressurized fluid flows from the fluid-charging chamber C C into the fluid-pumping chamber C P via valve V P , the fluid-pumping chamber will be supercharged to a greater extent than in FIG. 1 before the start of the forward-pumping strokes.
  • transverse wall 248 in FIG. 5, formed with the inlet opening 219 defines an inlet chamber C DI communicating with the fluid-charging chamber C C for damping the sounds of the inletted fluid
  • circumferential wall 247 formed with the outlet opening 246 defines an outlet chamber C DO communicating with the fluid-pumping chamber C P for damping the pressure pulsation's and sounds of the outletted fluid.
  • FIG. 6 illustrates a fluid pump, therein generally designated 300 , which is similar to that of FIG. 5, including a cylindrical section, therein designated 350 , carried by the piston 308 coaxially therewith and located within the fluid-pumping compartment C P so as to reduce the volume of that compartment as compared to the volume in the fluid-charging chamber C C .
  • the piston 308 is coupled to shaft 7 of the electromagnetic drive section 2 a at one side of the piston, and carries the coaxial cylindrical section 350 at the opposite side of the piston.
  • Transverse wall 347 formed with the outlet opening 346 defines an annular outlet chamber C D communicating with the fluid-pumping chamber C P for damping the pressure pulsations and sounds of the outletted fluid.
  • This arrangement permits the fluid outlet 346 of the fluid pump to be located in transverse wall 347 of the housing, rather than in circumferential wall 247 of the housing in the FIG. 5 construction.
  • Fluid pump 300 illustrated in FIG. 6 otherwise is constructed and operates substantially the same as described above with respect to FIGS. 1 - 5 .
  • each of the flat springs 13 , 14 could be, and preferably is, a stack of such springs rather than a single spring.
  • the one-way valves illustrated could be of any appropriate construction, inertia valves being particularly preferable in the illustrated fluid pump.
  • the pump could be used for pumping liquids as well as gases.
  • the invention could be implemented in a vacuum pump, e.g., by reversing the inlet and outlet or reversing the locations of the valves.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Electromagnetic Pumps, Or The Like (AREA)
  • Reciprocating Pumps (AREA)
US10/293,315 2002-11-14 2002-11-14 Fluid pumps with increased pumping efficiency Abandoned US20040096345A1 (en)

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US10/293,315 US20040096345A1 (en) 2002-11-14 2002-11-14 Fluid pumps with increased pumping efficiency
AU2003276664A AU2003276664A1 (en) 2002-11-14 2003-11-06 Fluid pumps with increased pumping efficiency
PCT/IL2003/000929 WO2004044421A2 (fr) 2002-11-14 2003-11-06 Pompes a fluide ayant une efficacite de pompage amelioree

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20060034710A1 (en) * 2004-08-13 2006-02-16 Moretti Stephen M Linear pump suspension system
US20080310978A1 (en) * 2007-06-14 2008-12-18 Viasys Sleep Systems, Llc Modular CPAP compressor
US20100037644A1 (en) * 2008-08-15 2010-02-18 Charles Barry Ward Condensate Pump
CN101975150A (zh) * 2010-10-26 2011-02-16 中国民航大学 双作用柱塞式除冰液泵

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US20080310978A1 (en) * 2007-06-14 2008-12-18 Viasys Sleep Systems, Llc Modular CPAP compressor
US8708674B2 (en) * 2007-06-14 2014-04-29 Carefusion 212, Llc Modular CPAP compressor
US9717869B2 (en) 2007-06-14 2017-08-01 Carefusion 212, Llc Modular CPAP compressor
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WO2004044421A3 (fr) 2004-07-01

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