EP1921319A2 - Verdrängungsrotationspumpe mit Spiralrotoren - Google Patents

Verdrängungsrotationspumpe mit Spiralrotoren Download PDF

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Publication number
EP1921319A2
EP1921319A2 EP08101970A EP08101970A EP1921319A2 EP 1921319 A2 EP1921319 A2 EP 1921319A2 EP 08101970 A EP08101970 A EP 08101970A EP 08101970 A EP08101970 A EP 08101970A EP 1921319 A2 EP1921319 A2 EP 1921319A2
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EP
European Patent Office
Prior art keywords
positive
teeth
rotary pump
displacement rotary
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.)
Withdrawn
Application number
EP08101970A
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English (en)
French (fr)
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EP1921319A3 (de
Inventor
Mario Antonio Morselli
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Individual
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Individual
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Publication date
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First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=11438276&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP1921319(A2) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Individual filed Critical Individual
Publication of EP1921319A2 publication Critical patent/EP1921319A2/de
Publication of EP1921319A3 publication Critical patent/EP1921319A3/de
Withdrawn legal-status Critical Current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
    • 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
    • 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
    • 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
    • F04C2/088—Elements in the toothed wheels or the carter for relieving the pressure of fluid imprisoned in the zones of engagement
    • 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
    • F04C2/16—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 helical teeth, e.g. chevron-shaped, screw type

Definitions

  • the present invention relates to the field of positive-displacement rotary pumps.
  • Rotary pumps of various types are known, amongst which gear pumps, lobe pumps and screw pumps are mentioned.
  • Gear pumps are generally constituted by two gears with straight teeth of which one, known as the driving gear, is connected to a drive shaft and rotates the other gear, which is known as the driven gear.
  • a disadvantage noticed particularly in the above-mentioned gear pumps is the risk of the fluid pumped being encapsulated and compressed in the spaces enclosed between the profiles of the teeth in the meshing region and giving rise to dangerous local stress peaks, especially when the fluid is incompressible.
  • it is necessary to adopt particular construction designs consisting, for example, in the formation of recesses in the side walls or head elements of the pump, enabling the fluid trapped to escape towards the delivery or the intake.
  • Lobe pumps are also constituted by at least two rotors with mating profiles which rotate inside a fixed casing.
  • Lobe pumps with mating external profiles have the advantage over gear pumps that they have greater displacement for a given space occupied, but they require external devices, for example, an additional pair of gears, to synchronize the movement of the rotors.
  • lobe pumps with mating internal profiles do not require external synchronization devices, they have small specific displacement and generally mediocre volumetric output.
  • Screw pumps implement the same liquid-transfer system in axial and peripheral directions as is implemented by the above-mentioned gear pumps purely in a peripheral direction. Although they have good flow-regularity characteristics, screw pumps generally have disadvantages similar to those of gear pumps, particularly with regard to the risk of the encapsulation of fluid.
  • a solution proposed for solving the problem indicated above is that of providing two identical positive-displacement rotary pumps in parallel in a manner such that the oscillations generated by one are in phase opposition with and hence at least partially compensated by the oscillations of the other.
  • the main disadvantage of this solution is its particular structural complexity and, more generally, its high cost.
  • 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 considerably reduces ripple noise without this leading to an increase in cost and in structural complexity in comparison with more conventional screw or gear pumps.
  • a further object of the invention is to provide a pump which has good leaktightness characteristics, which is easy and inexpensive to produce and to maintain, and which has good reliability over time whilst, at the same time, eliminating encapsulation problems.
  • the subject of the invention is a positive-displacement pump comprising a pair of meshing rotors or gears, that is, a driving rotor or gear and a driven rotor or gear, respectively, enclosed in a casing with a delivery opening and an intake opening for a fluid, characterized in that the gears comprise a plurality of teeth meshing without encapsulation and at the same defining helical sets of teeth with a face overlap substantially equal to or close to unity.
  • a positive-displacement rotary pump comprises a first gear or rotor 10 and a second gear or rotor 11.
  • the first gear 10 is connected integrally or by means of a fixing of a type generally known in the art, to a drive shaft 12 which takes the drive from a drive member (not shown) when the pump is in use.
  • the second gear 11 meshes with the first gear and is rotated thereby in use.
  • Both of the gears 10, 11 have shanks or shafts 13, 14a, 14b which, in similar manner to the drive shaft 12, are mounted rotatably in a leaktight manner in head elements 15, only one of which is shown in Figure 1 for clarity of illustration.
  • the gears 10, 11 are enclosed in a casing (not shown) having an intake opening and a delivery opening for the fluid to be pumped.
  • Each gear 10, 11 has a series of peripheral teeth 16a, 16b with identical profiles, preferably produced in accordance with the teachings of patent document IT-BO95A000095 , which is incorporated herein by reference, and in any case such as to ensure an absence of fluid-encapsulation areas for each relative angular position of the gears.
  • IT-BO95A000095 which is incorporated herein by reference, and in any case such as to ensure an absence of fluid-encapsulation areas for each relative angular position of the gears.
  • the profile preferably adopted is, in cross-section, an involute portion such as to render the profile satisfactorily insensitive to variations in the interaxial spacing between the two gears 10, 11.
  • the profile preferably selected is easy to manufacture since, in contrast, for example, with "cycloidal" profiles, it does not have portions with radii of curvature tending to zero, particularly in the vicinity of the pitch circle.
  • each gear 10, 11 has seven teeth 16a, 16b but, naturally, the number of teeth may vary according to the specific design details in embodiments of the present invention, particularly according to the dimensions and to the interaxial spacing of the rotary pump.
  • the teeth 16a, 16b extend helically along the height of each gear 10, 11 with a face overlap substantially equal to or close to unity, that is - in other words - with an axial pitch between two successive teeth equal to or close to the height of the gear in the direction of its axis of rotation.
  • the cross-section of a tooth 16a or 16b at the level of one end face 17a, 17b of the respective gear 10, 11 is substantially aligned - along an axis parallel to the axis of rotation of the gear - with the cross-section of an adjacent tooth 16a, 16b at the level of the other end face 18a, 18b of the respective gear 10, 11.
  • Figure 2 shows in detail a solution for compensating for the axial thrusts which, as is known, are generated by the pair of helical gears 10, 11 and by the spatial configuration of the teeth which are exposed to pressure variation.
  • the ends of the shafts or shanks 13, 14a bear against a pair of respective abutment pins 19, 20 which are mounted so as to be slidable axially in a leaktight manner in respective axial housings 21, 22 formed in a flange 23.
  • the ends of the abutment pins 19, 20 remote from the shafts or shanks 13, 14a face a common chamber 24 which is formed in a closure plate 25 and, in use, is preferably in communication with the delivery of the rotary pump.
  • the pressurized fluid which comes to occupy the chamber 24 thus opposes the axial thrust generated by the gears 10, 11. If, as is preferable, the pressure in the chamber 24 is generated by the pump itself, the balancing of the axial thrusts is regulated automatically and maintains its effectiveness with variations in pressure.
  • Figures 3 to 5 show, in cross-section, relative to the axis of rotation of the gears 10, 11, the positions adopted by the teeth 16a, 16b at successive moments of meshing. It is clear that no closed spaces are formed between the sets of teeth of the gears 10, 11 at any time, particularly in the position shown in Figure 4 which, in pumps with conventional gears, in contrast, leads to the problematic generation of such a closed space, defined by the sides of the teeth which come into contact along two pitch lines.
  • Figures 3 to 5 are also representative of the configurations adopted by the teeth 16a, 16b at the same moment in time but in different transverse planes identified along the height of the gears 10, 11.
  • cross-sections are taken progressively along the entire face height of the pair of gears, all of the possible configurations of meshing between the gears are found and all of these configurations can be utilized by virtue of the fact that there is no discontinuity in the meshing at the roots of the teeth, that is, there is no encapsulation.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
EP08101970A 2000-03-08 2001-03-08 Verdrängungsrotationspumpe mit Spiralrotoren Withdrawn EP1921319A3 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IT2000BO000119A ITBO20000119A1 (it) 2000-03-08 2000-03-08 Pompa volumetrica rotativa a rotori elicoidali .
EP01105738A EP1132618B1 (de) 2000-03-08 2001-03-08 Drehkolben-Verdrängungspumpe mit Schraubenrotoren

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
EP01105738A Division EP1132618B1 (de) 2000-03-08 2001-03-08 Drehkolben-Verdrängungspumpe mit Schraubenrotoren

Publications (2)

Publication Number Publication Date
EP1921319A2 true EP1921319A2 (de) 2008-05-14
EP1921319A3 EP1921319A3 (de) 2008-06-25

Family

ID=11438276

Family Applications (2)

Application Number Title Priority Date Filing Date
EP08101970A Withdrawn EP1921319A3 (de) 2000-03-08 2001-03-08 Verdrängungsrotationspumpe mit Spiralrotoren
EP01105738A Expired - Lifetime EP1132618B1 (de) 2000-03-08 2001-03-08 Drehkolben-Verdrängungspumpe mit Schraubenrotoren

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP01105738A Expired - Lifetime EP1132618B1 (de) 2000-03-08 2001-03-08 Drehkolben-Verdrängungspumpe mit Schraubenrotoren

Country Status (6)

Country Link
EP (2) EP1921319A3 (de)
AT (1) ATE393882T1 (de)
DE (1) DE60133786T2 (de)
DK (1) DK1132618T3 (de)
ES (1) ES2306681T3 (de)
IT (1) ITBO20000119A1 (de)

Families Citing this family (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1371848B1 (de) 2002-06-12 2006-01-04 Mario Antonio Morselli Zahnradpumpe mit Splinefunktion erzeugtem Zahnradprofil
US6887055B2 (en) 2002-10-25 2005-05-03 Mario Antonio Morselli Positive-displacement rotary pump
US7530217B2 (en) 2005-12-16 2009-05-12 General Electric Company Axial flow positive displacement gas generator with combustion extending into an expansion section
US7726115B2 (en) 2006-02-02 2010-06-01 General Electric Company Axial flow positive displacement worm compressor
ITBO20070172A1 (it) * 2007-03-14 2008-09-15 Mario Antonio Morselli Apparecchiatura idraulica ad ingranaggi perfezionata
US8708643B2 (en) 2007-08-14 2014-04-29 General Electric Company Counter-rotatable fan gas turbine engine with axial flow positive displacement worm gas generator
US7854111B2 (en) 2008-03-07 2010-12-21 General Electric Company Axial flow positive displacement turbine
IT1390747B1 (it) * 2008-08-12 2011-09-23 Settima Flow Mechanisms Srl Pompa volumetrica rotativa ad ingranaggi
IT1398817B1 (it) * 2009-10-30 2013-03-21 Morselli Ruota dentata con profilo atto ad ingranare con semi-incapsulamento in un'apparecchiatura idraulica ad ingranaggi
US9404366B2 (en) 2009-10-30 2016-08-02 Settima Meccanica S.R.L. Gear wheel with profile capable of meshing with semi-encapsulation in a geared hydraulic apparatus
DE102010005900A1 (de) * 2010-01-27 2011-07-28 Robert Bosch GmbH, 70469 Hydraulische Zahnradmaschine
ITRM20110378A1 (it) 2011-07-19 2013-01-20 Mario Antonio Morselli Pompa volumetrica rotativa a ruote dentate bielicoidali
CN103850932A (zh) * 2012-12-05 2014-06-11 上海易昆机械工程有限公司 一种无脉动转子泵
CN103486023B (zh) * 2013-07-10 2015-10-28 重庆德衡科技有限公司 螺杆泵及螺杆
RU2553848C1 (ru) * 2014-05-28 2015-06-20 Виктор Владимирович Становской Шестеренная машина

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITBO950095A1 (it) 1995-03-10 1996-09-10 Stem Numerical Engineering Srl Profili per rotori di compressori roots

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1620261A (en) * 1924-06-11 1927-03-08 Laval Steam Turbine Co Rotary gear pump
US1742597A (en) * 1927-05-20 1930-01-07 Joseph Mercadante Rotary pump
GB661329A (en) * 1948-06-24 1951-11-21 Guinard Paul Andre Balanced screw pumps
US3164099A (en) * 1961-08-09 1965-01-05 Iyoi Hitosi Toothed profiles of rotors of gear pump
US3658452A (en) * 1969-11-18 1972-04-25 Shimadzu Corp Gear pump or motor
US4017223A (en) * 1975-03-24 1977-04-12 Houdaille Industries, Inc. Axial thrust adjustment for dual screw-type pump
DE2828348A1 (de) * 1978-06-28 1980-01-10 Allweiler Ag Schraubenspindelmaschine
IT1124357B (it) * 1979-11-23 1986-05-07 Marzocchi Paolo & Adriano Perfezionamenti particolarmente adatti per le pompe e per i motori idraulici ad ingranaggi di tipo elicoidale
DE3920901C2 (de) * 1989-06-26 1995-02-16 Allweiler Ag Schraubenspindelpumpe
DE4330085A1 (de) * 1993-09-06 1995-03-09 Hugo Vogelsang Maschinenbau Gm Rotationskolben für Verdrängerpumpen nach dem Roots-Prinzip für inkompressible Medien

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITBO950095A1 (it) 1995-03-10 1996-09-10 Stem Numerical Engineering Srl Profili per rotori di compressori roots

Also Published As

Publication number Publication date
EP1921319A3 (de) 2008-06-25
EP1132618A3 (de) 2002-07-10
EP1132618B1 (de) 2008-04-30
EP1132618A2 (de) 2001-09-12
DK1132618T3 (da) 2008-08-25
ITBO20000119A1 (it) 2001-09-10
DE60133786D1 (de) 2008-06-12
ATE393882T1 (de) 2008-05-15
DE60133786T2 (de) 2009-06-25
ES2306681T3 (es) 2008-11-16

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