WO2008030228A1 - Ensemble pompe de mélange - Google Patents

Ensemble pompe de mélange Download PDF

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Publication number
WO2008030228A1
WO2008030228A1 PCT/US2006/034520 US2006034520W WO2008030228A1 WO 2008030228 A1 WO2008030228 A1 WO 2008030228A1 US 2006034520 W US2006034520 W US 2006034520W WO 2008030228 A1 WO2008030228 A1 WO 2008030228A1
Authority
WO
WIPO (PCT)
Prior art keywords
fluid
pump
motor
motive element
fluid pump
Prior art date
Application number
PCT/US2006/034520
Other languages
English (en)
Inventor
Mitchell A. Friedman
Original Assignee
International Dispensing Corporation
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by International Dispensing Corporation filed Critical International Dispensing Corporation
Priority to PCT/US2006/034520 priority Critical patent/WO2008030228A1/fr
Publication of WO2008030228A1 publication Critical patent/WO2008030228A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • F04C11/005—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of dissimilar working principle
    • F04C11/006—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of dissimilar working principle having complementary function
    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
    • G05D11/00—Control of flow ratio
    • G05D11/008—Control of flow ratio involving a fluid operating a pump motor
    • A—HUMAN NECESSITIES
    • A01—AGRICULTURE; FORESTRY; ANIMAL HUSBANDRY; HUNTING; TRAPPING; FISHING
    • A01C—PLANTING; SOWING; FERTILISING
    • A01C23/00—Distributing devices specially adapted for liquid manure or other fertilising liquid, including ammonia, e.g. transport tanks or sprinkling wagons
    • A01C23/04—Distributing under pressure; Distributing mud; Adaptation of watering systems for fertilising-liquids
    • A01C23/042—Adding fertiliser to watering systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C2/18—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2220/00—Application
    • F04C2220/24—Application for metering throughflow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C5/00—Rotary-piston machines or pumps with the working-chamber walls at least partly resiliently deformable

Definitions

  • the invention disclosed herein relates generally to a proportioning pump assembly, and more particularly to a pumping apparatus that maintains the ratio of two pumped fluids, which ratio is unaffected by alterations in the pressure and velocity of the flowing fluids.
  • beverage dispensing valves that provide for the mixing of carbonated water and syrup to produce a dispensed beverage are well known in the art.
  • Other applications such as adding medication to drinking water with such additives as chlorine or iodine and adding fertilizer concentrate to irrigation water are similarly well known.
  • U.S. Patent No. Re. 35, 780 to Hassell et al. discloses a beverage dispensing valve having two sets of oval gears in which the ratio of two liquid beverage constituents is maintained by the interaction of the oval gear pairs, which are sized so that the desired ratio is maintained. Flow is regulated through use of solenoid operated pallet valves for each liquid component.
  • U.S. Patent No. 3,821,963 to Olsen et al. discloses a liquid proportioning apparatus for injecting a liquid into the flow of a driving liquid.
  • the apparatus uses an eccentric paddle wheel as the fluid motor to drive a separate pump for a second liquid to be injected into the driving flow.
  • U.S. Patent No. 6,357,466 to Walton et al. discloses an apparatus for generating a mixture of a first fluid and a measured quantity of a second fluid in a fluid stream.
  • the gears of a flow meter rotate when a first fluid is passed through the flow meter.
  • a shaft connected coaxially with a gear of the flow meter is connected with a gear of a cavity pump for a second fluid so that the second fluid is pumped through the cavity pump when the first fluid is directed through the flow meter.
  • the blending pump assembly of the instant invention comprises a fluid motor, the motor having an inlet fluidly connected to a source of a first fluid and an outlet, a pump having an inlet fluidly connected to a source of a second fluid and an outlet, such fluid motor being operatively engaged with such pump through a drive which transfers torque from the fluid motor to the fluid pump, the fluid motor and pump being interconnected in such a way that a predetermined ratio between such first fluid and such second fluid is consistently maintained, irrespective of the pressure and velocity of the driving liquid.
  • the blending pump assembly may be provided an internal recirculation channel controlled by a valve to enable adjustment of the fluid proportions.
  • the blending pump assembly may be provided with modular quick-connect fluid pump blocks which provide varying flow rates for a given angular velocity of the driving gear of the fluid motor.
  • the blending pump assembly may simultaneously provide both a recirculation channel and a modular quick-connect fluid pump block to enable both fine and gross adjustment of the ratio between dispensed diluent and concentrate.
  • the blending pump assembly described thus provides proportioning of two fluids in a tightly controlled manner, and may provide adjustment of such proportion for fine and gross control of the ratio of such two fluids.
  • the compound motor/pump structure allows torque produced from the shaft in a fluid motor assembly to be used to drive a pump assembly connected thereto in such a way that the output from the pump maintains a desired proportion to the output of the fluid motor, irrespective of the flows there through.
  • the first fluid motor assembly is preferably driven by fluid pressure from a first fluid directed through an inlet port, which flow in turn drives the shaft in the fluid motor assembly. The torque generated is translated from the shaft to a gear in the connected pump.
  • a fluid motor body includes an inlet for a first fluid and a corresponding outlet, while the pump body includes an inlet for a second fluid and a corresponding outlet.
  • the first fluid inlet and outlet on the fluid motor body are in fluid communication with a chamber within the main motor body.
  • the second fluid inlet and outlet on the pump body are in fluid flow communication with a chamber within the pump body.
  • the first fluid inlet and outlet on the fluid motor body are in fluid communication with one pair of circular gears positioned within the chamber in the motor
  • the second fluid inlet and outlet on the pump body are in fluid communication with a second pair of circular gears positioned within the chamber in the pump.
  • the first pair of circular gears comprises a gear motor
  • the second pair of circular gears comprises a gear pump.
  • gear pairs may be replaced with a single gear element in either or both of the pump and motor assemblies, such as an eccentrically mounted impeller.
  • Each gear or gear pair as the case may be, preferably rotates in its own housing, fluidly separate from the other gear pair.
  • a recirculation channel is provided in the gear pump assembly that enables fine adjustment of the compound motor/pump output.
  • a "tee" connector may be positioned in the flow line of the pump, downstream of the pump outlet, which allows fluid communication between the pump flow line downstream of the pump and the pump flow line upstream of the pump.
  • a needle valve or similarly constructed flow control device may be positioned in the flow branch interconnecting the downstream line with the upstream line.
  • minute adjustment of such flow control device may bleed off a portion of the fluid output from the pump assembly, directing such fluid back to the pump input, and in turn enable fine adjustment of the amount of fluid dispensed from the pump flow line for a given amount of first fluid passing through the fluid motor.
  • gross adjustment of the proportional flow of a first fluid to a second fluid may be provided in a simple adjustment step.
  • the pump housing may be pivotally attached to the motor housing, and an intermediate drive mechanism, such as a gear train, may be provided between the two such that torque from the fluid motor drive shaft is transferred to the drive shaft of the driven member of the pump through such gear train.
  • the gears between the two housings may be selected to provide the desired proportional speeds of the motor and pump.
  • the pump housing is pivotally mounted to the motor housing, the pump housing may be pivoted to allow access to and replacement of the gears of the gear train, and thereafter pivoted and locked back into a position in which the gears of the gear train engage one another, thus enabling gross changes in proportioned flow rates to be achieved in a quick and easy manner.
  • the gear train may remain fixed, and the driven gear or gears within the pump may vary from pump block to pump block, such that switching out one pump block for another may provide changes in proportioned flow rates.
  • a pressurized first fluid is provided to the fluid motor fluid channel inlet and is delivered to the operative gear member(s) therein for providing rotation thereof. The first fluid then flows out of the fluid channel outlet.
  • the pressurized first fluid provides for the driving force for the gear pump for the second fluid.
  • the gear members are dimensioned such that, for each revolution of the gear members, a predetermined ratio of such first and second fluid is delivered. Moreover, such ratio is maintained regardless of the rotation rate of the gear members.
  • the gear pump output may be finely adjusted by permitting a portion of the output to recirculate back to the pump inlet thereby reducing the quantity of such second fluid injected into the first driving fluid stream, and may be grossly adjusted by replacing drive gears between the fluid motor and fluid pump.
  • the member(s) of the fluid pump serve as a pump, it is not necessary to pressurize the second fluid source for the delivery thereof to the blending pump assembly.
  • the gear members within the fluid motor housing may be configured to minimize clearance between the gear teeth and the sidewalls of the chamber, and between the top and bottom surfaces of the gear member(s) and the top and bottom walls of the chamber.
  • one or more parallel tooth gears are provided in a tapered configuration (i.e., having a cone-shaped perimeter), and the motor housing is similarly tapered so that the gear(s) can be individually placed in the tapered housing to a depth that would ensure a close fit regardless of manufacturing tolerances.
  • the clearance at one or both faces of the gear member(s) may then be filled by one or more upper and lower flat shims, thus resulting in close clearances between both the outside diameter of the gear member(s) and the housing, and between the gear face(s) and the housing.
  • connection between the fluid motor and pump is one of a direct drive engagement, such that a desired proportional flow may be maintained at all times, irrespective of the pressure or velocity at which the driving fluid flows through the fluid motor.
  • the mechanisms provided herein for both fine and gross adjustment require few parts, such that the compound motor/pump assembly of the instant invention requires less maintenance, and may likewise be provided at lower cost, than prior known blending apparatuses.
  • the features of fine and gross adjustment of proportional flow rates set forth herein enables much finer proportioning control than previously known blending apparatuses, and thus may be used in applications requiring very large proportioning ratios.
  • the tapered gear construction feature enables operation of the fluid motor (and optionally the fluid pump) at greater efficiency and with less leakage than prior known systems without requiring expensive manufacturing processes to reduce clearances between motor members.
  • Fig. 1 is an exploded perspective view of a blending pump assembly according to one embodiment of the instant invention.
  • Figs. 2a and 2b are cross section views of the blending pump assembly of Figure 1.
  • Fig. 3 is a cross section view of the pump portion of the blending pump assembly of Figure 1.
  • Fig. 4a is a cross section view of a vane pump or motor assembly according to an alternate embodiment of the instant invention.
  • Figs. 4b and 4c are exploded and sectional views of a screw pump assembly according to another embodiment of the instant invention.
  • Figs. 5a-5c are exploded and sectional views of a blending pump assembly according to another embodiment of the instant invention.
  • Fig. 6 is a sectional view of an alternate embodiment of the fluid motor assembly.
  • Fig. 7 is a schematic drawing of a first and second embodiment of the present invention.
  • a first preferred embodiment of the compound motor/pump assembly of the instant invention is shown in Figure 1.
  • a blending pump assembly generally designated as 10, includes a lower gear motor assembly 12 and an upper gear pump assembly 15.
  • Lower gear motor assembly 12 comprises gear motor body 17 and cover 18, the motor body 17 having an inlet fluid channel 21 and an outlet fluid channel 24 (best seen in Figure 2).
  • Inlet fluid channel 21 may be in fluid communication with a pressurized source of a first fluid as shown in Figure 7.
  • Motor body 17 further includes a cavity 27 wherein a first pair of gears 30, 31 is nested.
  • Gears 30, 31 may be circular gears having a plurality of teeth about their periphery, such that the teeth of gear 30 intermesh with the teeth of gear 31.
  • shaft 34 is rotatively secured to motor body 17 and fixedly secured to gear 30, and extends from gear 30 upward through aperture 36 in cover 18 to provide a drive axle 39 for upper gear pump assembly 15.
  • Gear 31 freely rotates on shaft 35, rotatively secured between motor body 17 and cover 18.
  • a vane pump a flexible rotor pump, or similarly configured pump assemblies capable of being driven by a motive fluid and transferring torque to a drive shaft 39 may be used for motor assembly 12.
  • gear pump assembly 15 comprises a gear pump body 42, to which a cover 43 is attached ( Figure 1).
  • a second pair of gears 46, 47 is nested in pump body 42.
  • Gears 46, 47 may be circular gears having a plurality of teeth about their periphery, such that the teeth of gear 46 intermesh with the teeth of gear 47.
  • Gear 46 is securely attached to drive axle 39 such that rotation of gear 30 causes simultaneous rotation of gear 46.
  • a seal 48 in aperture 36 may be provided for preventing fluid communication along shaft 34 between cavity 27 and gear pump body 42.
  • Gear 47 freely rotates on shaft 49, rotatively secured between pump body 42 and cover 43.
  • Pump body 42 has an inlet port 51 and an outlet port 52 creating a flow channel 55 through gear pump assembly 15.
  • Inlet port 51 is in fluid communication with a source of a second fluid as shown in Figure 7. Such second fluid source need not be pressurized.
  • a recirculation channel 58 is provided in pump body 42 having an adjustable valve 60 to adjust flow through recirculation channel 58.
  • Valve 60 may, for example, comprise a valve stem 62 extending through gear pump cover 43 (best seen in Figure 1) and a valve handle 65 to permit adjustment of flow through valve 60.
  • Valve 60 may be any appropriate type of valve having throttling characteristics and is preferably a needle valve enabling fine control of flow through recirculation channel 58.
  • Flow through recirculation channel 58 is in the direction indicated by arrow 69 in Figure 3.
  • the fluid motor, the pump, or both may be other than gear assemblies, in which the fluid motor and pump have a common rotating shaft.
  • a vane pump assembly as illustrated in Figure 4a can be used as the fluid motor, the pump, or both.
  • Such a vane pump assembly 70 may comprise body 71 having an inlet fluid channel 72 and an outlet fluid channel 74.
  • a slotted impeller 76 having a plurality of vanes 78 is eccentrically supported on shaft 80.
  • Shaft 80 is rotatively secured to body 71.
  • a seal 81 may be provided to prevent fluid leakage along shaft 80.
  • the impeller 76 is located close to body 71 so a crescent- shaped cavity 83 is formed. Vanes 78 fit within slots of the impeller 76 and are configured to extend into such cavity 83 to form a slideable seal against body 71.
  • inlet fluid channel 72 may be placed in fluid communication with a pressurized source of a first fluid (not shown).
  • the pressurized fluid enters the inlet fluid channel 72 and impinges on a first of such plurality of vanes 78 causing impeller 76 to rotate in the direction shown by arrow 85.
  • Such motion of impeller 76 also causes shaft 80 to rotate.
  • Shaft 80 extends outward from body 71 to provide a drive shaft for a connected pump.
  • the pressurized fluid passes through cavity 83 to outlet fluid channel 74.
  • vane pump assembly 70 When vane pump assembly 70 is utilized as a pump, shaft 80 causes impeller 76 to rotate. As the impeller 76 rotates and a second, unpressurized fluid enters the pump, the vanes 78 are pushed to the wall of body 71 forming a tight seal. As impeller 76 rotates, the vanes force such second fluid into the crescent-shaped cavity, and sweep the fluid toward the fluid outlet channel 74.
  • Other combinations of fluid motors and pumps having a common rotating shaft shared between the motor and pump can be used, such as a gear motor, as described with reference to Figures 1 and 2, and a vane pump, as described above. In such a case, the shaft of one of the gears in the gear motor drives the impeller of the vane pump.
  • a vane pump assembly can be used as a fluid motor with its shaft connected to drive one of the gears of a gear pump.
  • motor assemblies and/or pump assemblies of generally similar construction may likewise be utilized, such as a flexible vane pump,
  • gear pump body 42 is pivotally mounted to cover 18 of fluid motor assembly 12 via a pivot screw 90.
  • screw 90 locks the position of gear pump body 42, but when loose, screw 90 allows gear pump body 42 to pivot freely about screw 90.
  • shaft 34 extends upward from first gear 30 in fluid motor assembly 12, and a motor drive axel 39 extends through cover 18.
  • a first drive train gear 91 mounted on the exposed end of motor drive axel 39.
  • fluid motor assembly 12 comprises gears 30, 31, as explained above, alternate fluid motor configurations could likewise be utilized without departing from the spirit and scope of the invention, including a vane pump, flexible rotor pump, gear pumps having gears of other geometries, and any other pump assembly which may be driven via application of a pressurized fluid to the flow channel passing there through.
  • gear pump body 42 may be constructed to provide an opening between the bottom of gear pump body 42 and cover 18 of fluid motor assembly 12, such opening being of sufficient size to accommodate first gear 91 and a second gear 92.
  • gear pump body 42 is depicted as optionally utilizing a flexible vane pump assembly 70 having a flexible rotor 76 mounted within gear pump body 42, with a fluid inlet and outlet (not shown) directing fluid through gear pump body 42 and the cavity thereon holding flexible rotor 76.
  • flexible rotor 76 would preferably be mounted on pump drive axel 93, which in turn is mounted to second gear 92, such that rotation of second gear 92 causes rotation of flexible rotor 76 to in turn pump fluid through the pump assembly.
  • alternate gear elements such as one or more parallel tooth gears may be used for the pump assembly without departing from the spirit and scope of the invention.
  • gear pump body 42 is pivotally mounted to cover 18, access may be had to both first gear 91 and second gear 92 by pivoting gear pump body 42.
  • first gear 91 is removably attached to drive axel 39, such that first gear 91 may be removed and replaced with a gear having a different gear geometry, thus enabling gross modification of the rotational speeds of gears 30, 31 and of flexible rotor 76, which in turn modifies the proportional flow rates between the fluid motor assembly 12 and the gear pump assembly 15.
  • second gear 92 may likewise be removably attached to flexible rotor 76, such that second gear 92 may be replaced instead of or in addition to first gear 91 to enable gross modification of the proportional flows between fluid motor assembly 12 and gear pump assembly 15. Still further, first and second gears 91 and 92 may be maintained, and gear pump body 42 may be interchangeable, with different rotors 76 or other gear members of varying construction in different gear pump bodies. The single screw connection provided by pivot screw 92 enables quick interchange of such alternate pump body configurations. Likewise, while not particularly shown in Figure 5, gear pump assembly 15 may be provided with recirculation channel 58 and valve 60 as discussed above to also enable fine adjustment of the proportional flows between fluid motor assembly 12 and gear pump assembly 15.
  • gear members 30 and 31 may be provided as round, parallel tooth gears having a tapered perimeter 101.
  • the benefits of using a positive displacement pump as the fluid motor may be maintained without the associated disadvantages of leakage past the motor gears.
  • the positive displacement pump and more particularly a gear pump, allows the fluid that drives the motor to likewise provide the lubrication for the gears and rotating shafts.
  • Gears are quite common and easily manufactured whether
  • the gear members in fluid motor assembly 12 are formed as parallel tooth gears having a tapered or cone-shaped perimeter 101.
  • the chambers in which tapered gears 30 and 31 sit is likewise preferably tapered to that the gears 30 and 31 can be individually placed in the tapered housing to a depth that would ensure a close fit regardless of manufacturing tolerances.
  • manufacturing tolerances may cause a clearance to be produced between the top and bottom walls of the gears and the top and bottom walls of the chamber, respectively.
  • Such clearances are preferably filled with upper and lower flat shims 102 to the required thickness, thus resulting in close clearances between both the outside diameters of the gears as well as between the gear faces and the motor housing.
  • the fluid motor assembly 12 is driven by fluid pressure from a first fluid 105 directed through inlet fluid channel 21.
  • first fluid 105 directed through inlet fluid channel 21.
  • Gears 30, 31 are meshed together and counter-rotate relative to each other when the first fluid 105 is directed through the inlet fluid channel to the outlet fluid channel 24.
  • Shaft 34 from one of the fluid pressure driven gears, gear 30, extends upward through the housing to drive one of the gears, gear 46 of the gear pump assembly 15, which in turn will cause the gears 46, 47 in gear pump assembly 15 to counter rotate relative to each other in order to draw a second fluid 107 through inlet port 51 and pump such second fluid 107 out through outlet port 52.
  • first fluid 105 enables the pumping of such second fluid 107 since one gear of each pair is secured to a common rotating shaft.
  • the first pair of gears and second pair of gears are sized to provide a predetermined proportion of such second fluid 107 based on the flow of such first fluid 105.
  • the proportional flow of the second fluid in relation to the first fluid may be finely adjusted by adjusting the amount of flow through recirculation channel 58 by use of valve 60. Since pump assembly 15 provides a positive displacement gear pump, increased flow through recirculation channel 58 results in decreased flow through outlet port 52.
  • proportional flow may be grossly adjusted by changing the gears in the gear train between fluid motor drive axel 39 and fluid pump drive axel 93 (or by replacing gear pump body 42 with an alternate gear pump body having a distinct gear or rotor configuration) to enable a single pump assembly to be used in a wide variety of mixing applications.
  • Blending pump assemblies may be combined in series, such that the mixture from a first assembly 111 may be continuously diluted by directing the mixture through a second assembly 114, while directing the driving fluid through a second non-driven (or fluid pressure driven) motor with a common rotating shaft.
  • a low power electric motor and more preferably a battery-powered low power electric motor, may also be provided with a rotary drive shaft of such motor engaging the driving gear 30 in the fluid motor assembly to further assist motor start-up when the driving fluid is under low pressure.
  • a gear motor with very close clearances between the moving parts, there may be locations at which contact between the moving parts occurs, causing friction and hesitancy in initiating motor operation (particularly in those cases when low fluid pressures are used to drive the fluid motor).
  • the battery-powered low power electric motor (or optionally line voltage powered electric motor) may thus assist the low-pressure fluid in overcoming such friction, providing an inexpensive remedy.
  • continuous operation can be maintained without requiring continuous operation of the electric motor.
  • continuous operation may be maintained by the pressurized fluid source with little or no continuous power supply to the electric motor, and the electric motor speed is controlled primarily by the fluid pressure applied by the driving fluid and any flow restrictions in the fluid circuit.
  • a fluid motor and fluid pump can be sized and configured so that a predetermined ratio between the two fluids is maintained regardless of changes in pressure and flow rate of the driving fluid.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Automation & Control Theory (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Abstract

L'invention concerne un ensemble pompe de mélange pour maintenir avec exactitude deux composants fluides (12, 15) en proportion adéquate. L'écoulement d'un premier fluide est utilisé pour entraîner un moteur hydraulique, qui à son tour entraîne un mécanisme de pompage à injecter une quantité proportionnelle d'un deuxième fluide dans l'écoulement du premier fluide. Le moteur et la pompe hydrauliques (12, 15) sont dimensionnés de manière à conserver une proportion prédéterminée entre les deux fluides indépendamment des changements de pression et de débit dudit premier fluide.
PCT/US2006/034520 2006-09-06 2006-09-06 Ensemble pompe de mélange WO2008030228A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/US2006/034520 WO2008030228A1 (fr) 2006-09-06 2006-09-06 Ensemble pompe de mélange

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/US2006/034520 WO2008030228A1 (fr) 2006-09-06 2006-09-06 Ensemble pompe de mélange

Publications (1)

Publication Number Publication Date
WO2008030228A1 true WO2008030228A1 (fr) 2008-03-13

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PCT/US2006/034520 WO2008030228A1 (fr) 2006-09-06 2006-09-06 Ensemble pompe de mélange

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8303277B2 (en) 2002-11-21 2012-11-06 International Dispensing Corporation Blending pump assembly
JP2016075221A (ja) * 2014-10-07 2016-05-12 日本電産サンキョー株式会社 ギアポンプ

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3179383A (en) * 1963-03-01 1965-04-20 Norton Knedlik Method for metering and blending together a plurality of fluids
JPS5614889A (en) * 1979-07-13 1981-02-13 Yukio Watanabe Rotary engine by vane pump and vane motor
US5012837A (en) * 1990-10-10 1991-05-07 Xolox Corporation Ratio device for dispensing liquids
US5466131A (en) * 1994-03-22 1995-11-14 Micropump Corporation Multiple-chamber gear pump with hydraulically connected chambers

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3179383A (en) * 1963-03-01 1965-04-20 Norton Knedlik Method for metering and blending together a plurality of fluids
JPS5614889A (en) * 1979-07-13 1981-02-13 Yukio Watanabe Rotary engine by vane pump and vane motor
US5012837A (en) * 1990-10-10 1991-05-07 Xolox Corporation Ratio device for dispensing liquids
US5466131A (en) * 1994-03-22 1995-11-14 Micropump Corporation Multiple-chamber gear pump with hydraulically connected chambers

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8303277B2 (en) 2002-11-21 2012-11-06 International Dispensing Corporation Blending pump assembly
JP2016075221A (ja) * 2014-10-07 2016-05-12 日本電産サンキョー株式会社 ギアポンプ

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