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EP1291526B2 - Pompe à engrenages - Google Patents
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EP1291526B2 - Pompe à engrenages - Google Patents

Pompe à engrenages Download PDF

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Publication number
EP1291526B2
EP1291526B2 EP02020146.3A EP02020146A EP1291526B2 EP 1291526 B2 EP1291526 B2 EP 1291526B2 EP 02020146 A EP02020146 A EP 02020146A EP 1291526 B2 EP1291526 B2 EP 1291526B2
Authority
EP
European Patent Office
Prior art keywords
gears
bushings
bushing
positive
axial
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.)
Expired - Lifetime
Application number
EP02020146.3A
Other languages
German (de)
English (en)
Other versions
EP1291526A2 (fr
EP1291526A3 (fr
EP1291526B1 (fr
Inventor
Mario Antonio Morselli
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.)
Settima Meccanica Srl - A Socio Unico Soc
Original Assignee
Settima Meccanica Srl A Socio Unico Soc
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Filing date
Publication date
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Application filed by Settima Meccanica Srl A Socio Unico Soc filed Critical Settima Meccanica Srl A Socio Unico Soc
Publication of EP1291526A2 publication Critical patent/EP1291526A2/fr
Publication of EP1291526A3 publication Critical patent/EP1291526A3/fr
Application granted granted Critical
Publication of EP1291526B1 publication Critical patent/EP1291526B1/fr
Publication of EP1291526B2 publication Critical patent/EP1291526B2/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
    • 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
    • F04C15/0023—Axial sealings for working fluid
    • F04C15/0026—Elements specially adapted for sealing of the lateral faces of intermeshing-engagement type machines or pumps, e.g. gear machines or pumps

Definitions

  • the present invention relates to the sector of positive-displacement rotary pumps.
  • rotary pump including gear pumps, lobe pumps and screw pumps.
  • Gear pumps generally comprise two gears, one of which, known as the driving gear, is connected to a drive shaft and causes the other wheel, known as the driven gear, to rotate.
  • the pumps of this type for high pressures are generally produced with a so-called “balanced” or “equilibrated” configuration, in which the two opposing faces of the bushings for supporting the gears are subjected to pressures over areas which, although they are large in absolute terms, are not very different from each other in order to generate a moderate differential force which tends to keep each bushing in contact with the gears.
  • Figures 1 and 2 illustrate an example of a gear pump of known type and comprising the features of the preamble of claim 1.
  • Figure 1 is a longitudinal section along a plane which extends through the axes of rotation of the two gears
  • Figure 2 is a section taken on line II-II in Figure 1 .
  • the driving gear 13 and the driven gear 14, whose shafts are supported by two bushings 15, are housed inside a shell 10 which is closed by a front cover 11 and a rear cover 12.
  • Omega-shaped ( ⁇ ) seals 16 which separate the intake zone (A), at lower pressure, from the output zone (M), at higher pressure, are housed on the outer face 17a of the bushings 15.
  • the bushings 15 are subjected to a pressure both on the outer faces 17a thereof and on the inner faces 17b thereof.
  • the omega-like configuration of the seals 16 is such that the portion of outer face 17a of each bushing 15 on which the output pressure, which is greater than the intake pressure, acts is greater than the portion of inner face 17b of the bushing which is subjected to the same output pressure. Since the area on which the output pressure acts in the region of the inner face 17b of each bushing cannot be determined with accuracy, the optimum configuration of the omega-like seal 16 is usually identified by trial and error.
  • the bushings 15 are urged with a force which is moderate, and controlled, against the gears 13 and 14 so as to minimize the leakages over the faces of the gears themselves as a result of the difference in pressure between the intake and output.
  • the two bushings are floating in an axial sense.
  • the above-mentioned solutions of the prior art have the common problem consisting in the noise of operation caused by the instantaneous oscillations of the output over time, better known as ripple noise.
  • the above-mentioned oscillations generate a pulsating wave which, by way of the fluid, is transmitted to the surroundings and, in particular, to the walls of the pump, to the pipes and to the output ducts.
  • the noise produced can reach levels which are also unpredictable where the above-mentioned members begin to resonate with the frequency of oscillation or ripple.
  • the object of the present invention is to provide a positive-displacement rotary pump which overcomes the disadvantages of the prior art and, in particular, which substantially reduces the noise without resulting in a substantial increase in the cost and complexity of production in comparison with pumps of known type.
  • a further object of the invention is to provide a pump which has good leak-tightness characteristics between the intake and output, which is simple and economic to produce and maintain and which has good reliability over time.
  • the subject-matter of the invention is a positive-displacement pump which comprises the features indicated in the claims appended to the present description.
  • One advantage of the present invention consists in that the axial position of the rotors is unambiguously defined even in the event that they are subjected to axial loads or pressures owing to mechanical contact with the shell or portions thereof.
  • the present invention by providing a fixed plane of reference, also ensures the correct positioning of the rotors in the initial running-in stage of the pump, and even in the event of interference between the rotors and the shell, when unknown axial forces resulting from the above-mentioned mechanical contact are added to the axial forces expected in normal operation of the pump.
  • a gear pump 20 comprises, as already described above with reference to the known pump in Figures 1 and 2 , a shell 10 having an output opening and an intake opening for a fluid, inside which are housed the driving gear 13 and the driven gear 14.
  • the gears 13 and 14 are of the cylindrical type having helical teeth.
  • the shell 10 is closed at the two ends by the front cover 11 and the rear cover 12.
  • the end 21 of the shaft 23 of the driving gear 13 protrudes from the front cover 11.
  • the seals between the shaft 23 and the front cover 11 have been omitted in Figure 3 .
  • the shafts 23 and 24 of the gears 13 and 14, respectively are supported by two bushing sets, a front bushing set 15a and rear bushing set 15b.
  • Each of the bushing sets 15a and 15b can be produced in one piece, as in the case of the known pump in Figure 1 , or preferably in two separate pieces 22a, 22b, as illustrated in detail in Figure 4 .
  • bushing sets minimizes the axial output passages for fluid, in the region of the central zones 27 of the bushing sets 15a, 15b which correspond to the meshing zone of the gears 13, 14.
  • Longitudinal channels 25 are preferably, but not in a limiting manner, provided on the two flanks of each bushing set 15a, 15b and promote the distribution of the output pressure over the flanks of the bushing sets so as to keep the two separate pieces 22a, 22b close together.
  • the bushing sets 15a, 15b both in the one-piece version and in the version produced by means of separate pieces 22a, 22b, can preferably have passages having variable width in order to allow the hydrodynamic lubrication thereof.
  • One embodiment is illustrated in Figures 7 and 8 , wherein the face 17b of each piece 22a, 22b of one or both of the bushing sets 15a, 15b has depressions or channels 50 which extend in a radial direction and whose profile-section is slightly concave in a direction orthogonal to the radius of the piece 22a, 22b.
  • a slightly deeper slot or channel 51 is preferably provided in a substantially central position in respect of each depression or channel 50 for better distribution of the lubricating fluid.
  • the shafts 23, 24 react against a pair of check pins or balancing pistons 29, 30 which are mounted for axial sliding in a close-fitting manner in respective axial housings 31, 32 which are provided in an intermediate plate 26.
  • the ends of the check pins 29, 30 that are remote from the shafts 23, 24 are directed towards a common chamber 34 which is provided in the rear cover 12 and which, in use, is preferably in communication with the output of the rotary pump. In this manner, the pressurized fluid which will occupy the chamber 34 acts on the check pins 29, 30 so as to oppose the axial load produced by the gears 13, 14.
  • a groove 27 for accommodating a seal 16 which is, for example, substantially configured in an "omega"-like manner, is provided in the face of the intermediate plate 26.
  • An opening 28 is provided at the side of the plate that, when the pump is in use, communicates with the intake A.
  • the configuration of the intermediate plate 26, which is similar to that of the lower cover of the pumps of the prior art in Figures 1 and 2 , allows, during use of the pump, a distribution of output pressure M to be obtained over the outer face 17a of the rear bushing 15b which substantially affects the area P MAX indicated with hatching in Figure 5 .
  • This area is greater than the area of the inner face 17b of the rear bushing 15b which is subjected to the output pressure, as long as the force differential owing to the pressure provides for the production of an axial load on the rear bushing 15b directed towards the gears 13, 14, as indicated by arrow S' in Figure 3 .
  • the inner face of the front cover 11 unlike the pumps of known type, does not have the omega-like seal, and is instead provided with a large opening 36 which communicates with the intake A of the pump.
  • Two limbs 37 which communicate with the openings 38, 39 for housing the shafts 23, 24 of the gears 13, 14 extend from the opening 36.
  • This configuration of the face of the front cover 11 ensures that the outer face 17a of the front bushing 15a is subjected only to the intake pressure, which affects, by way of indication, the hatched area, which is denoted P MIN in Figure 6 .
  • the pressure differential acts on the front bushing 15a in a manner counter to that seen previously for the rear bushing 15b, as long as during use of the pump, the front bushing 15a, and in particular the two pieces 22a, 22b thereof, are urged firmly against the face of the front cover 11, as indicated by arrow S" in Figure 3 .
  • the check pins 29, 30 have different diameters in order to apply different axial loads to the two gears 13, 14. This is because, in the example of the Figure, the driving gear 13 and driven gear 14 are of a helical type and therefore, during operation, produce per se axial loads whose direction is counter to and in accordance with the direction of the axial load applied by the check pins 29, 30. Naturally, in the case of gears having straight teeth which do not produce per se axial loads, the check pins 29, 30 can have substantially corresponding diameters so as to apply an axial load of equal intensity to both of the gears.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Claims (9)

  1. Pompe rotative à déplacement positif comprenant une paire d'engrenages engrenés (13, 14) ou rotors, constituée d'un engrenage d'entrainement et d'un engrenage entrainé, qui sont contenus dans une enveloppe (10) ayant une ouverture de sortie et une ouverture d'entrée d'un fluide, les engrenages (13, 14) comprenant des arbres (23, 24) qui sont supportés par des bagues (15a, 15b) ayant deux faces (17a, 17b) soumises, en fonctionnement, à des pressions qui entrainent une charge axiale (S', S") sur la bague elle-même, dans laquelle la résultante des charges axiales (S', S") sur les deux bagues a une direction prédéterminée de manière à faire bouger les bagues (15a, 15b) et les engrenages (13, 14) ensemble, en butée étroite avec un plan de référence prédéterminé (VI-VI), caractérisée en ce que la paire d'engrenages engrenés (13, 14) ou rotors est du type ayant des dents hélicoïdales et en ce que des moyens sont prévus dans la pompe de telle sorte que la pression agissant sur les bagues (15a, 15b) fournit, en fonctionnement, des charges axiales (S', S") sur ces bagues (15a, 15b) qui agissent toujours dans le même sens les unes comme les autres dans la direction du plan de référence (VI-VI), dans laquelle la face externe (17a) d'une (15a) des deux bagues est dirigée vers le plan de référence (VI-VI) et est affecté seulement par la pression d'entrée (PMIN), et une partie (PMAX) de la face externe (17a) de l'autre (15b) des deux bagues est affectée par la pression de sortie (M), la partie (PMAX) étant séparée de la partie restante de la face externe (17a), qui est affectée par la pression d'entrée (A), par un joint de séparation (16) qui est connecté à une plaque (26) dirigée vers la face externe (17a) de la bague (15b), de telle manière que la résultante des pressions agissant sur la face externe (17a) de la bague (15b) est continuellement supérieure à la résultante des pressions agissant sur la face interne (17b) et en ce qu'elle comprend un système de compensation des charges, comprenant des moyens de charge axiale (29, 30) qui agissent sur la même extrémité de chaque arbre (23, 24) des engrenages (13, 14), les moyens de charge axiale (29, 30) provoquant, en fonctionnement, une charge axiale (S" ') sur les engrenages (13, 14) qui l'emporte sur les forces axiales produites par l'engrènement et ayant la même direction que la résultante des charges axiales (S', S") sur les bagues (15a, 15b).
  2. Pompe à déplacement positif selon la revendication 1, caractérisée en ce que les moyens de charge axiale comportent des broches de contrôle ou des pistons d'équilibrage (29, 30) qui sont montés pour glisser axialement de façon étanche dans des logements respectifs (31, 32) qui sont prévus dans une plaque (26) fixée à l'un des deux couvercles (11, 12) de l'enveloppe (10) de la pompe.
  3. Pompe à déplacement positif selon la revendication 2, caractérisée en ce que les extrémités des broches de contrôle (29, 30) pressent, d'un côté, sur les extrémités des arbres (23, 24) des engrenages (13, 14) et, de l'autre côté, sont dirigées vers une chambre commune (34) qui est prévue dans le couvercle (12) de l'enveloppe (10), la chambre commune (34) étant en communication avec l'ouverture de sortie de la pompe rotative.
  4. Pompe à déplacement positif selon la revendication 1, caractérisée en ce que les moyens de charge axiale (29, 30) ont des dimensions différentes de manière à appliquer des charges axiales différentes (S" ') sur chacun des engrenages.
  5. Pompe à déplacement positif selon les revendications 2 et 4, caractérisée en ce que les broches de contrôle ont des diamètres différents.
  6. Pompe à déplacement positif selon l'une des revendications précédentes, caractérisée en ce qu'au moins une bague (15a, 15b) comporte au moins deux pièces séparées (22a, 22b), chacune étant destinée à soutenir en rotation une extrémité de l'un des deux arbres (23, 24) des engrenages (13, 14).
  7. Pompe à déplacement positive selon la revendication 6, caractérisée en ce qu'au moins un canal longitudinal (25) est prévu sur les flancs de chaque pièce séparée (22a, 22b) de ladite au moins une bague (15a, 15b) et favorise la répartition de la pression de sortie sur les flancs de la bague (15a, 15b), de manière à garder les deux pièces séparées (22a, 22b) proches l'une de l'autre.
  8. Pompe à déplacement positif selon la revendication 1, caractérisée en ce que ces creux ou canaux localisés (50) sont prévus sur l'une (17b) des deux faces d'au moins l'une des bagues (15a, 15b) afin de permettre la lubrification hydrodynamique de celui-ci.
  9. Pompe à déplacement positif selon la revendication 8, caractérisée en ce que les creux ou canaux s'étendent radialement sur la face (17b) de la bague, la section de profil de chaque creux étant légèrement concave dans la direction orthogonale par rapport au rayon, une fente ou canal (51) légèrement plus profonde étant prévu dans une zone sensiblement centrale de chaque creux (50).
EP02020146.3A 2001-09-07 2002-09-09 Pompe à engrenages Expired - Lifetime EP1291526B2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IT2001BO000540A ITBO20010540A1 (it) 2001-09-07 2001-09-07 Perfezionamenti in una pompa volumetrica rotativa
ITBO20010540 2001-09-07

Related Child Applications (1)

Application Number Title Priority Date Filing Date
EP10186253.0 Division-Into 2010-10-01

Publications (4)

Publication Number Publication Date
EP1291526A2 EP1291526A2 (fr) 2003-03-12
EP1291526A3 EP1291526A3 (fr) 2003-11-12
EP1291526B1 EP1291526B1 (fr) 2014-03-05
EP1291526B2 true EP1291526B2 (fr) 2020-03-18

Family

ID=11439585

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02020146.3A Expired - Lifetime EP1291526B2 (fr) 2001-09-07 2002-09-09 Pompe à engrenages

Country Status (2)

Country Link
EP (1) EP1291526B2 (fr)
IT (1) ITBO20010540A1 (fr)

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2063126A3 (fr) * 2007-11-22 2014-03-12 Robert Bosch GmbH Machine hydraulique à roue dentée et procédé d'étanchéification d'une machine hydraulique à roue dentée
DE102009012853A1 (de) 2009-03-12 2010-09-16 Robert Bosch Gmbh Hydraulische Zahnradmaschine
DE102009012854A1 (de) 2009-03-12 2010-09-16 Robert Bosch Gmbh Hydraulische Zahnradmaschine
DE102009012916A1 (de) * 2009-03-12 2010-09-16 Robert Bosch Gmbh Hydraulische Zahnradmaschine
DE102009012856A1 (de) 2009-03-12 2010-09-16 Robert Bosch Gmbh Hydraulische Zahnradmaschine
CN101586561B (zh) * 2009-05-22 2011-12-28 王良仁 高压齿轮油泵
DE102010005900A1 (de) 2010-01-27 2011-07-28 Robert Bosch GmbH, 70469 Hydraulische Zahnradmaschine
JP6119748B2 (ja) * 2012-06-11 2017-04-26 株式会社島津製作所 歯車ポンプ又はモータ
WO2014141377A1 (fr) * 2013-03-12 2014-09-18 株式会社 島津製作所 Pompe ou moteur à roue dentée
JP5761283B2 (ja) * 2013-09-18 2015-08-12 ダイキン工業株式会社 ギヤポンプまたはギヤモータ
WO2015082257A1 (fr) * 2013-12-03 2015-06-11 Oerlikon Textile Gmbh & Co. Kg Pompe à engrenage
CN107532587B (zh) * 2015-04-01 2020-01-10 瑟提马麦肯尼加有限公司 齿轮传动正排量式机器
JP2021042730A (ja) 2019-09-12 2021-03-18 株式会社島津製作所 歯車ポンプ又は歯車モータ

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2855855A (en) * 1949-06-30 1958-10-14 Thompson Prod Inc High pressure pump
US2756684A (en) * 1954-11-12 1956-07-31 Sier Bath Gear And Pump Co Inc Rotary gear-type pump
US2891483A (en) * 1956-04-13 1959-06-23 Thompson Ramo Wooldridge Inc Movable bushing for pressure loaded gear pumps
US2981200A (en) 1956-10-05 1961-04-25 Parker Appliance Co Gear pump structure
FR1197750A (fr) 1958-01-06 1959-12-02 Pompe à engrenage exempte de poussée axiale
GB880539A (en) * 1959-04-15 1961-10-25 Clark Equipment Co Pressure loaded gear pump
GB908687A (en) 1960-03-01 1962-10-24 Bosch Gmbh Robert Improvements in and relating to hydraulic machines operable as rotary pumps or motors
FR1343908A (fr) * 1962-11-22 1963-11-22 Clark Equipment Co Pompe ou moteur
GB1181224A (en) 1966-06-20 1970-02-11 Dowty Hydraulic Units Ltd Gearing and Lubricating Means Therefor
US5641281A (en) * 1995-11-20 1997-06-24 Lci Corporation Lubricating means for a gear pump

Also Published As

Publication number Publication date
EP1291526A2 (fr) 2003-03-12
ITBO20010540A1 (it) 2003-03-07
ITBO20010540A0 (it) 2001-09-07
EP1291526A3 (fr) 2003-11-12
EP1291526B1 (fr) 2014-03-05

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