WO2014096494A1 - Pompe à engrenages, compacte et étanche - Google Patents

Pompe à engrenages, compacte et étanche Download PDF

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Publication number
WO2014096494A1
WO2014096494A1 PCT/ES2013/070891 ES2013070891W WO2014096494A1 WO 2014096494 A1 WO2014096494 A1 WO 2014096494A1 ES 2013070891 W ES2013070891 W ES 2013070891W WO 2014096494 A1 WO2014096494 A1 WO 2014096494A1
Authority
WO
WIPO (PCT)
Prior art keywords
compact
sealed
rotation
gear pump
pump according
Prior art date
Application number
PCT/ES2013/070891
Other languages
English (en)
Spanish (es)
Inventor
Pedro Javier Gamez Montero
Esteve CODINA MACIA
Original Assignee
Universitat Politècnica De Catalunya
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 Universitat Politècnica De Catalunya filed Critical Universitat Politècnica De Catalunya
Publication of WO2014096494A1 publication Critical patent/WO2014096494A1/fr

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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
    • 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
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
    • F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C15/0069—Magnetic couplings
    • 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
    • F04C2240/00—Components
    • F04C2240/40—Electric motor
    • F04C2240/402—Plurality of electronically synchronised motors

Definitions

  • the present invention concerns a gear pump for fluids provided with a dobie electro-magnetic assembly that allows a compact and tight design, without transmission shafts externally coupled to the pump, and where said double electro-magnetic assembly provides a torque independent motor for each gear, resulting in a gear with a minimum contact voltage, or with a controlled contact voltage, in order to minimize the wear of the gears.
  • Gear pumps have application in numerous industrial sectors, among which are the automotive sector and the aeronautics sector.
  • a conventional gear pump consists of a pair of cogwheels: a pinion with external teeth called an internal cogwheel and a crown with internal teeth called an external cogwheel, housed in a cavity of a housing generally formed by a body of pump and a cover connected to each other.
  • the mentioned cavity is in fluid communication with a suction area (fluid inlet) and a discharge area (fluid outlet).
  • the two sprockets rotate around respective parallel axes and are conjugated so that each tooth of the inner sprocket is in permanent sliding contact with the outer sprocket forming what are known as "contact points".
  • the outer sprocket has a Z number of teeth, while the inner sprocket has a Z-1 number of teeth. In this way, between the inner sprocket and the outer sprocket there are permanently Z points of contact between the corresponding sealed chambers Z defined by surfaces of the teeth of both sprockets and by surfaces of the housing.
  • the pumping action is produced by a variation in the volume of said watertight chambers as a result of the complete rotation of the inner and outer sprockets, creating the circulation of successive watertight chambers with increasing fluid volume from said suction area to said suction area impulsion.
  • the Rotational movement is generally imparted by a drive shaft driven by an external motor that rotates the inner gearwheel and the inner gearwheel transmits the rotation motion to the outer gearwheel, although alternative drive means are known.
  • patent application US 20060039815 A1 discloses a gear pump comprising a concentric magnetic ring with the axis of rotation of the outer sprocket and fixed to an outer periphery of the outer sprocket, and a ring with windings concentric with the axis of rotation of the outer sprocket and fixed to the housing so that this ring with windings is radially adjacent around said magnetic ring.
  • US Patent 7500837 B2 describes a gear pump that includes an internal electromagnetic assembly arranged to drive the rotation of the inner gearwheel, and this transmits the rotational movement to the outer gearwheel by the force exerted by the outer teeth of the wheel. internal toothed on the inner teeth of the outer gearwheel at the contact points.
  • US 8182235 B2 discloses a gear pump that includes a drive shaft driven by a first external mechanical actuator and operatively connected through a first clutch to drive the rotation of the inner gearwheel, a driven drive gearwheel. by a second external mechanical actuator and operatively connected through a second clutch to drive the rotation of the outer gearwheel, and an additional internal electromagnetic assembly arranged to drive the rotation of the outer gearwheel.
  • the three drives are alternative and are not intended to act simultaneously to drive the rotation of both inner and outer sprockets, whereby the rotational movement to the inner sprocket is transmitted to the outer sprocket by the force exerted by the teeth external of the internal gearwheel on the internal teeth of the external gearwheel at the contact points or alternatively the rotation movement to the external gearwheel is transmitted to the internal gearwheel by the force exerted by the internal teeth of the outer sprocket on the outer teeth of the inner sprocket at the contact points.
  • Gear pumps have a significant number of advantages, such as a low noise level and a small number of components, which is why they apply in a wide range of industrial sectors, including the automotive sector and the automotive sector. aeronautics. However, some of the advantages of its design have disadvantages in some aspects of its behavior.
  • this gap between the teeth allows a fluid flow from one of the sealed chambers to others, favored by a pressure gradient between the sealed chambers and by a relative movement of the sprockets. Consequently, pump performance is negatively influenced. Since gear pumps produce a fluctuation of flow that overlaps the average flow, this fluctuation of flow is negatively influenced, producing pressure pulsations, which are the major source of vibration and fatigue failures in gear pumps.
  • a major disadvantage of gear pumps is the absence of parts that can be adjusted to compensate for the clearance caused by wear on the profile of the teeth of the sprockets, which results in a progressive reduction in the efficiency of the pump gears, which can be remarkable. Consequently, when the loss of performance due to this wear on the gear profiles exceeds a preset threshold, the only possible alternative is the replacement of both sprockets, with a significant associated economic cost.
  • an objective of the present invention is to eliminate the need for transmission of the torque from one of the cogwheels to the other by a force exerted on the contact points. of the gear of the sprockets, and consequently eliminate or drastically reduce the mechanical tension known as contact tension in the material of the sprockets.
  • a compact and sealed gear pump comprising a sealed housing that includes a pump body and a cover connected to each other defining between them a cavity in fluid communication with a suction area and a driving area, an inner sprocket, provided with a number Z-1 of external teeth, housed in said cavity capable of rotating around a first axis of rotation, an outer cogwheel, provided with a number Z of internal teeth, housed in the cavity with the ability to rotate about a second axis of rotation parallel to said first axis of rotation and engaged with said inner gear wheel, and drive means configured and arranged to rotate at least one of said inner gear wheels and Exterior.
  • the gear pump of the present invention is characterized in that said drive means comprise a first internal electro-magnetic assembly that drives the rotation of the inner gearwheel and a second internal electromagnetic assembly that drives the rotation of the outer gearwheel, where said first and second internal electro-magnetic assemblies are independently controllable by control means.
  • both inner and outer sprockets are independently driven, which allows controlling the torque ratio between the two, including the possibility of minimizing torque transmission between the inner and outer sprockets. Since there is no transmission of torque between the inner and outer wheels by forces exerted by the teeth at the contact points, there are also no contact voltages on the gearwheel material and consequently the wear of the wheels is canceled or drastically reduced. same. Alternatively, the independent drive of the inner and outer gearwheels allows the contact voltage to be controlled at a desired value.
  • said first internal electro-magnetic assembly comprises a first winding ring, coaxial with said first axis of rotation, fixed to said pump body and a first magnetic ring, also coaxial with said first axis of rotation, arranged radially adjacent to said first winding ring and fixed to the inner gearwheel, so that when windings of the first winding ring are excited by means of electric current supply, a magnetic field is generated in the first magnetic ring that transmits a first motor torque and a first rotation speed to the inner sprocket.
  • said second internal electro-magnetic assembly comprises a second coaxial magnetic ring with said second axis of rotation and fixed to the outer toothed wheel and a second ring with coaxial winding with said second axis of rotation, arranged around said second magnetic and fixed ring with respect to said pump body to transmit a second motor torque and a second rotation speed to the outer sprocket.
  • the gear pump of the present invention provides an innovative, more compact and watertight design, since it does not have any primary transmission shaft that goes out through the pump body or cover, no axis being seen from the outside of the sealed housing of the pump.
  • one or both inner and outer gearwheels include on the surfaces of mutual contact a coating of a thermoplastic material, such as for example polyoxymethylene or polyacetal, an elastomeric, polymer, plastic or synthetic coating, which aids in the The tightness of the sealed chambers although the contact voltage is very low. In this way a benefit is obtained in the volumetric yield.
  • a thermoplastic material such as for example polyoxymethylene or polyacetal, an elastomeric, polymer, plastic or synthetic coating
  • the compact and sealed gear pump of the present invention allows the contact voltages of the contact points between the inner and outer sprockets to be controlled by means of the two internal electro-magnetic assemblies independent that drive the rotation of the inner sprocket and the rotation of the outer sprocket, respectively.
  • the magnitude of the contact tension can be controlled if torque transmission by gear between the inner gear wheel and the outer gear wheel is desired. , the torque of each wheel being controllable independently.
  • it can be controlled whether the inner sprocket is the one that transmits torque to the outer sprocket, or if the outer sprocket is the one that transmits torque to the inner sprocket, or if both sprockets and transmit torque between they at different magnitudes, as well as if there is no torque transmission by gear between both sprockets.
  • the compact and sealed gear pump of the present invention makes it possible to control the wear of the surfaces of the tooth profiles of the inner gear wheel and the outer gear wheel, said wear being zero or minimum, which consequently improves the Volumetric efficiency and performance of the gear pump.
  • Fig. 4 shows a comparative graph of the volumetric characteristics and the maximum contact voltage as a function of the number of teeth in a gear pump according to the design of the present invention, where:
  • - Z is the number of teeth.
  • Fig. 5 shows a comparative graph of the maximum contact voltage for different angular positions of the gear in a gear pump according to a conventional design and the range of variation of the maximum contact voltage as a function of the angular position of the gear in a gear pump according to the design of the present invention.
  • the compact and sealed gear pump of the present invention minimizes internal fluid leaks, from one another of the sealed chambers thanks to the absence of wear, and prevents external leaks, from inside to outside the housing waterproof thanks to the absence of shafts that cross the walls of the waterproof housing.
  • the compact and sealed gear pump of the present invention allows to control the synchronization and the relative speed of both gearwheels independently, allowing rotation in both directions of rotation to produce a pumping action of lower flow rate pulsation, reducing pressure pulsations , which are the major source of vibrations and fatigue failure.
  • the compact and sealed gear pump of the present invention improves the environmental relationship of this type of fluid pumps thanks to its tightness in relation to the surrounding environment.
  • Fig. 1 is a sectioned plan view of a compact gear pump and waterproof according to an embodiment of the present invention
  • Fig. 2 is a cross-sectional view taken by the piano l l-ll of Fig. 1
  • Fig. 3 is a sectional elevational view of a compact and sealed gear pump according to another embodiment of the present invention
  • Fig. 4 is a comparative graph of the volumetric characteristics and the maximum contact voltage as a function of the number of teeth in a gear pump according to the present invention.
  • Fig. 5 is a comparative graph of the maximum contact voltage in a gear pump according to a conventional design and the maximum contact voltage in a gear pump according to the present invention as a function of the angular position of the gear.
  • a compact and sealed gear pump according to an embodiment of the present invention, which comprises a sealed housing 100 formed by a pump body 126 and a cover 156 fixed to each other by means of screws or any other fastening element 162. Between said pump body 126 and said cover 156 a cavity is defined in fluid communication with a suction area 140 and a discharge area 152.
  • an inner gearwheel 102 provided with a number Z-1 of external teeth and an external gearwheel 104 provided with a number Z of internal teeth.
  • Said inner sprocket 102 is rotatable about a first axis of rotation Ei and said outer sprocket 104 is rotatable about a second axis of rotation Ee parallel to said first axis of rotation Ei and is engaged with the inner sprocket 102.
  • External teeth of the inner gearwheel 102 have Z contact points 172 with the outer gearwheel 104, and between these Z contact points are defined Z sealed chambers of variable volume 110 delimited by surfaces of the outer teeth of the inner gearwheel 102 , surfaces of the internal teeth of the outer gearwheel 104, and surfaces of the chamber body 126 and the cover 156.
  • the pump body cavity is cylindrical and coaxial with said second axis of rotation Ee.
  • the gear pump comprises drive means that include a first internal electro-magnetic assembly that drives the rotation of the inner gearwheel 102 and a second internal electro-magnetic assembly that drives the rotation of the outer gearwheel 104, with the particularity that said first and second internal electro-magnetic assemblies are independently controllable by control means.
  • said first internal electro-magnetic assembly comprises a first ring with winding 1 14 fixed to said pump body 126 and a first magnetic ring 1 18 arranged around said first ring with winding 1 12 and fixed to the inner toothed wheel 102, to transmit a first torque and a first rotation speed to the inner gearwheel 102.
  • Both said first ring with winding 114 and said first magnetic ring 118 are coaxial with said first axis of rotation Ei.
  • said second internal electro-magnetic assembly comprises a second magnetic ring 120 fixed to the outer gearwheel 104 and a second winding ring 122 disposed around said second ring magnetic 120 and fixed to said pump body 126 to transmit a second motor torque and a second rotation speed to the outer gearwheel 104.
  • Both said second magnetic ring 120 and said second winding ring 122 are coaxial with said second axis of rotation USA
  • the pump body 126 has an outer surface 154 and an inner surface 148 and the cover 156 has an outer surface 158 and an inner surface 160, so that when the cover 156 is attached to the pump body 126, the inner surface 148 of the pump body 126 and the inner surface 160 of the covers are located directly adjacent to the sealed chambers of variable volume 10 cooperating with the surfaces of the teeth of the inner and outer sprockets 102, 104 in the definition of the variable volumes of the waterproof cameras of variable volume 110.
  • the inner surface 148 of the pump body 126 has machining that forms non-variable empty volumes that act as a suction port 106 and a discharge port 108 of opposite semicircular elongated shapes (Fig. 1).
  • the pump body 126 also has a suction duct 142 of optimum fluid-dynamic geometry that connects the suction area 140 with said suction port 108 and consequently with those of the sealed chambers of variable volume 1 10 which are coincident with the suction port 108, and a discharge conduit 150 of optimum fluid-dynamic geometry connecting the discharge port 106, and consequently those of the sealed chambers of variable volume 110 which are coincident with the discharge port 106, with the drive area 152.
  • the gear pump sucks a fluid that is conducted from a corresponding reservoir or fluid source (not shown) to the suction area 140, and through the suction conduit 142, suction port 108, sealed chambers of variable volume 110, discharge port 106 and discharge conduit 150 to the discharge area 152 to be driven to a corresponding component or system (not shown).
  • the cover 156 can also have machining that defines non-variable empty volumes that act as a suction port 168 and a discharge port 170 of opposite semicircular elongated shapes (Fig. 2).
  • the suction port 168 of the cover 156 is opposite and aligned with the suction port 106 of the pump body 126 and is exposed to those of the sealed chambers of variable volume 1 10 which are coincident with the suction port 168, while the discharge port 170 of the cover 156 is opposite and aligned with the discharge port 108 of the pump body 126 and is exposed to those of the sealed chambers of variable volume 1 0 which are coincident with the discharge port 170.
  • the inner gearwheel 102 and the outer gearwheel 104 are conjugated so that each tooth of the inner gearwheel 102 is in permanent non-sliding contact with the outer gearwheel 104 forming those known as contact points 172.
  • the outer gearwheel 104 Z has teeth (Z being an integer), one more than the internal gearwheel 102. In this way, Z contact points 172 are formed.
  • the pumping action is produced by the variation of the volume of the variable volume sealed chambers 110 with the complete rotation of the inner gearwheel assembly 102 and the outer gearwheel 104, creating the circulation of successive sealed chambers of variable volume 1 10 with increasing fluid volume from the suction area 140 (inlet) to the area of drive 152 (output).
  • the contact voltages of the contact points 172 are controlled by means of the first and second independent internal electro-magnetic assemblies for the inner gearwheel 102 and the outer gearwheel 104. Accordingly, the magnitude of the tension of the tension of contact if a transmission of torque by gear is desired between the inner sprocket 102 and the outer sprocket 104, the torque of each wheel being independently controlled.
  • the inner sprocket 102 is the one that transmits torque to the outer sprocket 104, or it can be contracted if the outer sprocket 102 is the one that transmits the torque to the inner sprocket 102, or if both Inner and outer wheels 102 and 104 transmit torque between them at different torque magnitudes, or if there is a minimum torque transmission per gear between both inner and outer sprockets 102 and 104.
  • the first magnetic ring 1 18 of the first electromagnetic assembly is located circumferentially and connected to the inner sprocket 102.
  • the first magnetic ring 1 18 is formed by a plurality of permanent magnets located in the radial direction and whose orientation, location and polarity can be exchanged at convenience.
  • the inner gearwheel 02 does not incorporate a magnetic ring formed by a plurality of permanent magnets but is formed and constructed entirely or partially by magnetic material forming the corresponding first magnetic ring.
  • the first magnetic ring 1 18 is operated by said first ring with winding 1 14, which, in the embodiment shown in Figs.
  • first concentric rings connected to each other by first radial ribs in which first windings 1 18 are interconnected by means of wire or appropriate material, and connected to a corresponding power supply (not shown), for example through a central cylindrical conduit 112 and through the cover 158 and / or the pump body 126.
  • a power supply not shown
  • the first windings 1 16 are properly excited by the power supply of the power supply, a magnetic field is generated in the magnets permanent of the magnetic ring 1 18 causing the rotation of the inner gearwheel 102.
  • a programmable automaton or a logic card can be placed to control, between others, the speed of rotation and the torque of the inner sprocket 102 that allow cooperating in the control of the tension of contact and relative speed.
  • two hydrodynamic bearings 144 and 146 are located to position, support and facilitate the rotation of the inner gearwheel 102 by hydrodynamic lubrication, with grooves (not shown).
  • two other hydrodynamic bearings 144 and 146 are located to position, support and facilitate the rotation of the inner gear wheel 102 by hydrodynamic lubrication, with grooves (not shown).
  • the first two concentric rings connected by first radial ribs of the winding ring 14 are fixed and centered with the pump body 126 and with the cover 156 by means of the rings 114 embedded in machined circumferential grooves in the inside the inner surface 148 of the pump body 126 and inside the inner surface 160 of the cover 156.
  • This configuration forms the radial seal towards the center of the pump body 126 through the faces of the inner toothed wheel 102 in contact adjacent to the inner surface 148 of the pump body 126 and the inner surface 160 of the cover 156, and consequently, the tightness of the sealed chambers of variable volume 1 10 in contact adjacent to the inner surface 148 of the pump body 126 and the inner surface 160 of the cover 156.
  • the outer gearwheel 104 carries the second magnetic ring 120, which is located circumferentially and joined to the outer gearwheel 104,
  • the second magnetic ring 120 is formed by a plurality of permanent magnets located in the radial direction and whose orientation, location and Polarity can be exchanged at convenience.
  • the outer gearwheel 104 instead of incorporating a second magnetic ring formed by a plurality of permanent magnets may be formed and constructed entirely or partially by a magnetic material (not shown) forming the second magnetic ring.
  • the second magnetic ring 120 is operated by said second ring with winding 122 concentric to the second magnetic ring 120, which, in the embodiment shown in Figs. 1 and 2, it comprises two second concentric rings connected to each other by a few radial ribs in which are arranged a few second windings 124 interconnected by means of wire or appropriate material, and connected to the corresponding power supply (not shown) through the cover 158 and / or the pump body 126.
  • the second windings 124 are properly excited by the power supply of the power supply, a magnetic field is generated in the permanent magnets of the magnetic ring 120 causing the wheel to rotate. external toothed 104.
  • a programmable automaton or a logic card (not shown) can be placed that allows to control, among others, the rotation speed and the wheel motor torque external toothed 104 allowing control of the contact voltage and relative speed.
  • two hydrodynamic bearings 164 and 166 are located to position, support and facilitate the rotation of the outer gearwheel 104 by hydrodynamic lubrication, with grooves (not shown).
  • two hydrodynamic bearings 164 and 166 are located to position, support and facilitate the rotation of the outer gearwheel 104 by hydrodynamic lubrication, with grooves (not shown).
  • the two second concentric rings connected by second radial ribs of the winding ring 122 are fixed and centered with the pump body 126 and the cover 156 by means of the rings 122 embedded in a circumferential grooves machined inside of the inner surface 148 of the body of pump 126 and inside the inner surface 160 of the cover 156.
  • This configuration forms the radial seal to the outside of the pump body 126 through the faces of the outer sprocket 104 in contact adjacent to the inner surface 148 of the pump body 126 and the inner surface 160 of the cover 156, and consequently, the tightness of the sealed chambers of variable volume 110 in contact adjacent to the inner surface 148 of the pump body 126 and the intended surface 160 of the cover 156 ,
  • Fig. 3 shows a compact and sealed gear pump according to another alternative embodiment of the present invention, which comprises, in a manner analogous to that described above in relation to Figs. 1 and 2, a sealed housing 200 that includes a pump body 126 and a cover 156 connected to each other defining between them a cavity in fluid communication with a suction area 140 and a driving area 152, an intentional gearwheel 102 provided with a number Z-1 of external teeth housed in said cavity capable of rotating around a first axis of rotation Ei, an external gearwheel 104 provided with a number Z of internal teeth housed in the cavity capable of rotating about a second rotation axis Ee parallel to said first rotation axis Ei and engaged with said inner gearwheel 102, and drive means including a first internal electro-magnetic assembly that drives the rotation of the internal gearwheel 102 and a second electro- internal magnetic that drives the rotation of the outer gearwheel 104, said first and second internal electromagnetic assemblies being independently controllable entirely by means of control.
  • the waterproof housing 200 comprises a first sealed motor housing 206 connected tightly to the pump body 126 and a second sealed motor housing 208 connected tightly to the cover 156.
  • the first Internal electro-magnetic assembly comprises a first magnetic ring 18 fixed to a first concentric shaft 210 with the first axis of rotation Ei housed inside said first sealed motor housing 206 and a first winding ring 1 14 housed within the first housing of sealed engine 206 and fixed thereto surrounding the first magnetic ring 1 18.
  • This first shaft 210 is directly connected to the inner gear wheel 102.
  • the second internal electro-magnetic assembly comprises a second magnetic ring 120 fixed to a second concentric shaft 212 with the second axis of rotation Ee housed within said second sealed motor housing 208 and a second winding ring 122 housed within the second housing motor airtight 208 and fixed thereto surrounding the second magnetic ring 120.
  • This second shaft 212 is connected to a rigid transmission member 204 which is in turn connected to the outer sprocket 104 by means of drive pins 202 or elements Similar.
  • first and second watertight motor housings 208, 208 do not have openings through which the first and second shafts 210, 212 exit to the outside, which ensures perfect sealing of the watertight housing 200.
  • one of the inner and outer sprockets 102, 104 or both inner and outer sprockets 102, 104 have a synthetic material coating in those areas that make mutual contact, that is, in those areas of the teeth of the inner and outer sprockets 102, 104 which include the contact points 172.
  • Said synthetic material may be a thermoplastic, such as for example polyoxymethylene or polyacetal, or an elastomer. This coating helps the tightness of the sealed chambers of variable volume 1 10 without any contact voltage or with a very low contact voltage. In this way a benefit in volumetric yield is obtained.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Abstract

La présente invention concerne une pompe à engrenages qui comprend une carcasse étanche (100, 200) incluant un corps de pompe (126) et un couvercle (156) comportant une cavité en communication fluidique avec une région d'aspiration (140) et une région d'impulsion (152), une roue dentée intérieure (102) pourvue d'un nombre Z-1 de dents extérieures qui est placée dans ladite cavité et qui peut tourner autour d'un premier axe de rotation (Ei), une roue dentée extérieure (104) pourvue d'un nombre Z de dents intérieures qui est placée dans la cavité et qui peut tourner autour d'un second axe de rotation (Ee) parallèle au premier axe de rotation (Ei) et engrenée avec ladite roue dentée intérieure (102) et des premier et second ensembles électromagnétiques internes qui actionnent respectivement la rotation des roues dentées intérieure et extérieure (102, 104), lesdits premier et second ensembles électromagnétiques internes pouvant être commandés indépendamment par des moyens de commande.
PCT/ES2013/070891 2012-12-21 2013-12-18 Pompe à engrenages, compacte et étanche WO2014096494A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ESP201232006 2012-12-21
ES201232006A ES2482869B1 (es) 2012-12-21 2012-12-21 Bomba de engranajes compacta y estanca

Publications (1)

Publication Number Publication Date
WO2014096494A1 true WO2014096494A1 (fr) 2014-06-26

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT201800003151A1 (it) * 2018-02-28 2019-08-28 Agilent Tech Inc A Delaware Corporation Sistema di pompaggio per vuoto comprendente una pompa da vuoto ed il suo motore

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0230868A2 (fr) * 1985-11-25 1987-08-05 Institut Cerac S.A. Machine rotative
WO1991018206A1 (fr) * 1990-05-16 1991-11-28 Johnson Pump Aktiebolag Ensemble pompe
EP0821187A2 (fr) * 1996-07-26 1998-01-28 Toyota Jidosha Kabushiki Kaisha Générateur de pression d'huile et appareil pour délivrer de la puissance
US20100130327A1 (en) * 2008-11-25 2010-05-27 Toyota Motor Engineering & Manufacturing North America, Inc. Multi-Drive Fluid Pump

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0230868A2 (fr) * 1985-11-25 1987-08-05 Institut Cerac S.A. Machine rotative
WO1991018206A1 (fr) * 1990-05-16 1991-11-28 Johnson Pump Aktiebolag Ensemble pompe
EP0821187A2 (fr) * 1996-07-26 1998-01-28 Toyota Jidosha Kabushiki Kaisha Générateur de pression d'huile et appareil pour délivrer de la puissance
US20100130327A1 (en) * 2008-11-25 2010-05-27 Toyota Motor Engineering & Manufacturing North America, Inc. Multi-Drive Fluid Pump

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT201800003151A1 (it) * 2018-02-28 2019-08-28 Agilent Tech Inc A Delaware Corporation Sistema di pompaggio per vuoto comprendente una pompa da vuoto ed il suo motore
WO2019166882A1 (fr) * 2018-02-28 2019-09-06 Agilent Technologies, Inc. A Delaware Corporation Système de pompage à vide comportant une pompe à vide et son moteur
CN111788392A (zh) * 2018-02-28 2020-10-16 安捷伦科技有限公司 包括真空泵及其马达的真空泵送系统

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ES2482869A1 (es) 2014-08-04
ES2482869B1 (es) 2015-05-12

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