EP3228866A1 - Heizölpumpe mit zahnradgetriebe - Google Patents

Heizölpumpe mit zahnradgetriebe Download PDF

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Publication number
EP3228866A1
EP3228866A1 EP17158191.1A EP17158191A EP3228866A1 EP 3228866 A1 EP3228866 A1 EP 3228866A1 EP 17158191 A EP17158191 A EP 17158191A EP 3228866 A1 EP3228866 A1 EP 3228866A1
Authority
EP
European Patent Office
Prior art keywords
pinion
teeth
pump
separator
ring gear
Prior art date
Legal status (The legal status 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 status listed.)
Granted
Application number
EP17158191.1A
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English (en)
French (fr)
Other versions
EP3228866B1 (de
Inventor
Dominique EMAILLE
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Suntec Industries France SA
Original Assignee
Suntec Industries France SA
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Filing date
Publication date
Application filed by Suntec Industries France SA filed Critical Suntec Industries France SA
Publication of EP3228866A1 publication Critical patent/EP3228866A1/de
Application granted granted Critical
Publication of EP3228866B1 publication Critical patent/EP3228866B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F04C2/101—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 with a crescent-shaped filler element, located between the inner and outer intermeshing members
    • 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
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0007—Radial sealings for working fluid
    • 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
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/084—Toothed wheels

Definitions

  • the present invention relates to the field of pumps for household fuel burners and more particularly to gear pumps.
  • This type of pump conventionally comprises a housing generally containing two sprockets with external right teeth and two lateral orifices, a supply orifice and a discharge orifice arranged strictly opposite.
  • One of the pinions is driven either by keying or machined directly on its shaft and the other is driven by the drive gear and can be free on its axis ringed or bearing.
  • the fluid fills the volume between the teeth and is transported from the supply port to the discharge port by occupying the volume between the teeth.
  • the major disadvantage of this type of pump is related to their balancing.
  • the object of the present invention is therefore to overcome the drawbacks mentioned above and to propose an alternative to known compact internal gear pumps having a low energy consumption while ensuring a sufficient flow rate for fuel burners with a power of less than or equal to at 70 kilowatts.
  • the subject of the present invention is a low-flow fuel pump comprising a casing provided with at least one intake orifice and a discharge orifice, and containing an internal gear comprising an externally toothed gear, a gear crown with internal teeth and a separator keeping the pinion and the crown apart and sealing between said inlet and discharge ports, the separator being crescent-shaped and arranged symmetrically with respect to the axis passing through the respective centers the pinion and the crown, the teeth of the ring having an arcuate profile and the teeth of the pinion having a profile conjugate to that of the teeth of the ring, said pump being remarkable in that the pinion comprises thirteen teeth distributed uniformly along a pitch diameter, in that the ring has eighteen teeth uniformly distributed along a pitch diameter and in that the arcuate profile of the teeth of the ring is defined by a radius and a center positioned, with respect to the center of said ring, with polar coordinates, said radius being between 0.66 and 1 times the the value of the pitch diameter of
  • said pitch diameters of the pinion and the crown are respectively equal to 13 and 18 mm.
  • Interpenetration i is advantageously between 5 and 8% of the value of the pitch diameter of the ring.
  • said radius is between 15 and 16 mm and said polar coordinates are such that the distance is between 19 and 21 mm and the angle is between 45 and 50 °.
  • the separator is delimited, on the pinion side, by an inner cylindrical surface and, on the crown side, by an outer cylindrical surface and the cylindrical surfaces of the teeth belonging to the head circles of the pinion and the crown slide in sealing contact along said surfaces.
  • the internal cylindrical surface of the separator extends on either side of the axis passing through the respective centers of the pinion and the crown along an arc forming an angle less than 180 ° with respect to the center of the pinion, and in that the outer cylindrical surface of the separator extends on either side of said axis, along an arc forming an angle greater than 180 ° relative to the center of the ring.
  • the free ends of the separator shrink advantageously so as to form an edge substantially parallel to the axis of rotation of the pinion.
  • the object of the present invention is, starting from an existing internal gear oil pump, hereinafter referred to as "anterior pump", to define a new configuration of its internal gearing ensuring a sufficient flow rate for fuel oil burners. less than or equal to 70 kilowatts, without modifying the size of the front pump and its overall dimensions as well as the position of its various connections.
  • the low-flow fuel pump 1 is of the internal gear pump type and comprises a casing 2 provided with at least one inlet, not shown, of a fluid to be compressed and a discharge port, not shown, of the compressed fluid.
  • low-flow pump refers to a pump capable of delivering a flow rate of up to 40 l / h (liters per hour), depending on pump outlet pressure conditions and for a typical rotation speed of 2850 rpm.
  • the pump 1 also comprises, arranged inside said casing 2, a pinion 3 leading to external toothing adapted to be set in motion by not shown drive means, a ring 4 with internal teeth and a separator 5 holding the pinion 3 and the ring 4 apart and sealing between the inlet and discharge ports of the pump 1.
  • the pinion 3 is disposed inside the ring 4 so as to drive the latter, when turning in one direction, to create a space that sucks the fluid to move it between the teeth on either side of the separator 5, to the discharge port.
  • the pinion 3 and the ring 4 are respectively defined by their number of teeth, their pitch diameter Dm3, Dm4, head diameter Dt3, Dt4 and foot diameter Dp3, Dp4 and their tooth profile.
  • the pinion 3 - crown 4 assembly is characterized by the eccentricity, hereinafter referred to as "E", that is to say the distance between the respective centers C3, C4 of the pinion 3 and the ring gear 4. .
  • the separator 5 is crescent-shaped disposed symmetrically with respect to the axis passing through the respective centers C3, C4 of the pinion 3 and the ring 4, and fills most of the free space between the head circles pinion 3 and crown 4 opposite the point of the deepest engagement, that is to say the opposite of the place where the teeth of pinion 3 penetrate most between the teeth of the crown 4.
  • the separator 5 is delimited, on the pinion side 3, by an internal cylindrical surface 51 whose Di5 diameter is equal to the head diameter Dt3 thereof and, on the crown side 4, by an outer cylindrical surface 52 whose diameter De5 is equal to the head diameter Dt4 thereof.
  • the cylindrical surfaces of the teeth belonging to the head circles of the pinion 3 and the ring gear 4 slide in sealing contact along the inner cylindrical 51 and outer 52 surfaces of the separator 5.
  • cylindrical surfaces of the teeth belonging to the head circles of the pinion 3 and the ring gear 4 are the cylindrical surfaces determined by the respective head circles of the pinion 3 and the wheel 4, in other words cylindrical surfaces containing the circles respective head of the pinion 3 and the wheel 4 and whose height corresponds respectively.
  • the pump 1 comprises a pinion 3 with thirteen teeth and a ring 4 with eighteen teeth.
  • This torque 13/18 allows to have a number of teeth, on the one hand, high enough to limit the path of the contact between teeth to reduce friction and, on the other hand, small enough to be physically feasible considering pump housing 2 dimensions 1. By elsewhere, this torque 13/18 reduces the galling value.
  • the tooth section is based on the pinion 3: this is the difference between the tooth-tooth surface and the tooth-tooth surface, more precisely the active diameter Da3 of the pinion 3.
  • the latter is equal to the root diameter Dp3 of pinion 3, which is added twice the value of the game for to escape the connecting radii of the tooth of the pinion 3 to the root diameter Dp3, said clearance being conventionally of the order of 0.2 mm and Da3 being therefore equal to 12.2 mm.
  • a flow rate Q equal to 40 l / h is chosen in a first approach, this flow rate being very small compared to the previous pump, but sufficient to firstly create a vacuum at the suction port of the pump.
  • the pump 1 compensate for internal leakage of the gear and a possible pressure regulator on the other hand, and finally feed a burner of 70 kilowatts.
  • a value of the interpenetration i equal to 1.1 is then deduced.
  • the formulas hereinafter known to the skilled person make it possible to determine the main characteristics of the pinion 3 - crown 4 assembly.
  • the pitch diameter Dm3 of the pinion 3 is then given by the formula: " Da3 + i "and is therefore substantially equal to 13.3 mm.
  • the head diameter Dt3 of the pinion 3 is given by the formula: "Da3 + 2i” and is therefore substantially equal to 14.4 mm.
  • the head diameter Dt4 of the ring 4 is given by the formula: "Da3 + 2 ⁇ (E)" and is therefore substantially equal to at least 17.2 mm.
  • the pitch diameter Dm4 of the ring 4 is then given by the formula: "Dt4 + i" and is therefore substantially equal to at least 18.3 mm.
  • the maximum width G5 of the separator 5 (Cf. figure 6 ) is given by the formula: "Dt4 + i - Dt3" and is therefore substantially equal to 3.9 mm.
  • interpenetration i does not allow at this stage to define the toothing, on the other hand it directs towards the abandonment of the toothing in involute. Indeed, it is not possible to determine a set of involute teeth with such a fine tooth or the number of teeth must be considerably increased, which then causes manufacturing difficulties.
  • each tooth of the ring 4 has an arcuate profile defined by its radius R4 and its center Cp4, the latter being positioned relative to the center C4 of the ring 4 and to the x-x ', yy' axes of symmetry of the latter (Cf. figure 4 ) with the following polar coordinates: distance L4, angle A4.
  • each tooth of said pinion 3 has a profile conjugate to that of the teeth of the ring gear 4.
  • This profile of teeth, of the trochoid type, is known to increase the volumetric capacity of the 3-crown gear assembly 4, as described, for example, in patent applications US 2008/0187450 or US 3907470 .
  • this gear lies in the way of positioning the arc defining the crown tooth 4 so as to have a tooth flank generally more perpendicular to the tangent of the pitch diameter Dp4 of the crown 4 than on the profiles. known teeth. This makes it possible to maintain correct pressure angle and driving ratio parameters for a low tooth, and a reduced number of teeth.
  • tooth profiles of the 3-crown gear assembly 4 can reduce the pumping rate while maintaining sufficient suction capacity to allow only the correct operation of the pump 1, especially when the fuel tank is away from the burner, for example, several meters.
  • the pump 1 according to the invention is such that the profile of each tooth of the ring 4 is defined by the radius R4 between 0.66 and 1 times the value of Dm4, the distance L4 between 1 and 1.33 times the value of Dm4 and the angle A4 between 40 and 55 °, when it is in the position shown on the Figures 4 and 5 .
  • the profile of each tooth of the ring 4 is defined by the radius R4 between 15 and 16 mm, the distance L4 between 19 and 21 mm and the angle A4 between 45 and 50 °.
  • each profile is connected to the foot and head circles of said pinion 3 respectively by rounded Rp3 and Rt3.
  • each tooth of said ring 4 is connected to the top and bottom circles of the latter respectively by rounded Rp4 and Rt4.
  • the inner cylindrical surface 51 of the separator 5 extending on either side of the axis passing through the respective centers C3, C4 of the pinion 3 and the ring 4 along an arc forming a lower angle at 180 ° with respect to the center C3, and the outer cylindrical surface 52 of the separator 5 extending on either side of the axis passing through the respective centers C3, C4, along a arc forming an angle greater than 180 ° with respect to the center C4.
  • the maximum width G5 of the separator 5 is between 20 and 25% of the pitch diameter Dm4 of the ring 4.
  • the low-flow fuel pump 1 according to the invention is more particularly applicable to boiler burners, but it can also be used in other fields.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
EP17158191.1A 2016-02-29 2017-02-27 Heizölpumpe mit zahnradgetriebe Active EP3228866B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR1651673A FR3048268B1 (fr) 2016-02-29 2016-02-29 Pompe a fuel a engrenages

Publications (2)

Publication Number Publication Date
EP3228866A1 true EP3228866A1 (de) 2017-10-11
EP3228866B1 EP3228866B1 (de) 2023-08-30

Family

ID=56087311

Family Applications (1)

Application Number Title Priority Date Filing Date
EP17158191.1A Active EP3228866B1 (de) 2016-02-29 2017-02-27 Heizölpumpe mit zahnradgetriebe

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EP (1) EP3228866B1 (de)
FR (1) FR3048268B1 (de)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1553035A1 (de) * 1966-04-29 1975-04-10 Eckerle Otto Hochdruck-innenlaeufer-zahnradmaschine
US3907470A (en) 1971-08-19 1975-09-23 Hohenzollern Huettenverwalt Gear machine
DE2758376A1 (de) 1977-12-28 1979-07-05 Schwaebische Huettenwerke Gmbh Kolbenkraft- oder -arbeitsmaschine mit innenlaeuferzahnradoelpumpe
US5360325A (en) * 1993-09-30 1994-11-01 The United States Of America As Represented By The Secretary Of The Navy Gear pump with reduced fluid-borne noise
US20080187450A1 (en) 2005-02-16 2008-08-07 Liavas Vasilios B Crescent Gear Pump with Novel Rotor Set

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1553035A1 (de) * 1966-04-29 1975-04-10 Eckerle Otto Hochdruck-innenlaeufer-zahnradmaschine
US3907470A (en) 1971-08-19 1975-09-23 Hohenzollern Huettenverwalt Gear machine
DE2758376A1 (de) 1977-12-28 1979-07-05 Schwaebische Huettenwerke Gmbh Kolbenkraft- oder -arbeitsmaschine mit innenlaeuferzahnradoelpumpe
US5360325A (en) * 1993-09-30 1994-11-01 The United States Of America As Represented By The Secretary Of The Navy Gear pump with reduced fluid-borne noise
US20080187450A1 (en) 2005-02-16 2008-08-07 Liavas Vasilios B Crescent Gear Pump with Novel Rotor Set

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
N.N.: "Adaptabilité, Qualité, Innovation, Mondialisation et Développement", 17 November 2015 (2015-11-17), XP055312846, Retrieved from the Internet <URL:http://www.suntec.fr/document/Press/Communique_SUNTEC_17Nov_FR.pdf> [retrieved on 20161021] *

Also Published As

Publication number Publication date
FR3048268A1 (fr) 2017-09-01
EP3228866B1 (de) 2023-08-30
FR3048268B1 (fr) 2021-04-30

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