EP0802326B1 - Machine à engrenages à gradient de pression contrôlé - Google Patents

Machine à engrenages à gradient de pression contrôlé Download PDF

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Publication number
EP0802326B1
EP0802326B1 EP96105855A EP96105855A EP0802326B1 EP 0802326 B1 EP0802326 B1 EP 0802326B1 EP 96105855 A EP96105855 A EP 96105855A EP 96105855 A EP96105855 A EP 96105855A EP 0802326 B1 EP0802326 B1 EP 0802326B1
Authority
EP
European Patent Office
Prior art keywords
gears
pressure
machine according
distribution spaces
displacing machine
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
EP96105855A
Other languages
German (de)
English (en)
Other versions
EP0802326A1 (fr
Inventor
Fred Rausch
Horst Weidhaas
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.)
Haldex Hydraulics GmbH
Original Assignee
Haldex Barnes GmbH
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 Haldex Barnes GmbH filed Critical Haldex Barnes GmbH
Priority to ES96105855T priority Critical patent/ES2160737T3/es
Priority to EP96105855A priority patent/EP0802326B1/fr
Priority to DE59607362T priority patent/DE59607362D1/de
Priority to US08/673,529 priority patent/US5730589A/en
Priority to DE19713907A priority patent/DE19713907A1/de
Publication of EP0802326A1 publication Critical patent/EP0802326A1/fr
Application granted granted Critical
Publication of EP0802326B1 publication Critical patent/EP0802326B1/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

Definitions

  • the invention relates to a displacement machine two intermeshing, externally toothed gears according to the preamble of claim 1.
  • Displacement machines are known. Such machines are characterized by high running noise as well relatively strong flow pulsations that are disruptive and are therefore undesirable.
  • Tolerances pinion head circle and housing inner diameter
  • the gears act so that they are radial with be subjected to a force.
  • the wheels are loaded by a drive torque.
  • the forces acting on a gear result a resulting force whose line of action with the line of action of the resulting power of the other Gear diverges, that is, the gears become by the resulting resulting directed away from each other Forces pressed apart.
  • a displacement machine is used to solve this task proposed that mentioned in claim 1 Features. Because the im the higher Prevailing connection area Pressure over a peripheral area of the gears to the one with the lower pressure level Connection area is returned, whereby the Gears pressed against each other by hydraulic forces are guaranteed in a simple way, that the resulting resulting on the gears Forces or their lines of action in an area on the suction side to cut. This causes the movements the gears are facing each other, which makes the teeth in the area where they are together comb, be pushed together so that on the one hand the backlash of the gears and on the other hand the space is reduced, the two teeth include with each other.
  • the reduction of the included Room volume leads directly to one Reduction of the enclosed in this room also referred to as the squeeze volume of fluid and thus to a significant reduction the flow pulsation, i.e. the pressure vibrations in the connection area with the higher pressure level, due to this the sound power level the displacement machine is significantly reduced is.
  • the fact that the first pressure distribution rooms over a circumferential area of the gears of Extend 70 ° and approximately symmetrical to the axis of symmetry lie and that the second pressure distribution rooms - starting from the first - to the Extend circumferential area of the gears, the 45 ° in front of the suction area are the noise level and further reduces the flow pulsation.
  • connection areas separated from each other by a double flank seal are:
  • the gears are affected by those acting on them resulting forces towards each other moved that the meshing teeth the Suction side and pressure side by means of three touch or Separate sealing points.
  • the thus trained Double-flank sealing is thus realized that a tooth with its two flanks simultaneously on the flanks of two teeth of the other Gear rolls, which permanently three Sealing points are given on an engagement line are arranged and move along this.
  • the double flank seal also leads to a Reduction of the squeezing volume, which causes the flow pulsation compared to a single flank seal, the only two interventional respectively Sealing points in the separation area between suction and Printed page is reduced by 75%. Because of the proportionality between running noise and flow pulsation is the noise level reduced accordingly.
  • An embodiment of the displacement machine is also preferred, where the resultant from the hydraulic radial forces and from on to the Torque acting on the axis of rotation of the gearwheels mechanical forces with an axis of symmetry each include an angle that is smaller Is 90 °. This causes in the area of by Manufacturing tolerances possible play one another too directed movement of the two gears, whereby the teeth of the gears mesh in such a way that both flanks of the suction from the Teeth on the pressure side separating a gear Flanks of one tooth of the other gear.
  • the displacement machine operated as a pump that is a gear with a driving torque pressurized so that a fluid is required becomes. It is possible to understand how the Reverse displacement machine and this also as To operate the engine.
  • the figure shows a schematic sectional view a displacement machine 1 with a housing, of which is shown here only the inner surface 3 of the housing is.
  • the housing inner surface 3 encloses an interior 5 which on its end faces by Sealing surfaces is limited.
  • the sealing surfaces are usually also referred to as printing plates Lids closed.
  • the interior 5 has a cross section in Form an eight on, by two axially parallel Holes is formed.
  • two externally toothed gears 11 and 13 arranged, the rotatably connected to axes of rotation 15 and 17 are and their side surfaces close to the sealing surfaces issue.
  • the centers of the gears 11 and 13 each lie on an intersection, the of an axis of symmetry 19 and a plane El respectively from the axis of symmetry 19 and one Level E2 is formed.
  • the levels E1 and E2 run parallel to each other and orthogonal to the axis of symmetry 19.
  • the gears 11 and 13 mesh in one Separation area 21 with each other, the two connection areas 23 and 25 separates. That too promoting fluid is the lower of the pressure level having connection area 23 (suction side) conveyed to the connection area 25 (pressure side), which is a higher pressure level than the connection area 23 has.
  • connection area 23 is a bore 29 in the housing of the displacement machine 1, by means of which the interior 5 with a fluid supply - not shown here - Line is connected.
  • the case points a further bore 31 on the connection area 25 is arranged and in which the of the conveying spaces 27 delivered, pressurized fluid the displacer 1 promoted and for example is supplied to a consumer.
  • the desired game between the tooth heads 37 of the Gears 11 and 13 and the housing inner surface 3 leads to that of the one having the higher pressure level Connection area 25 the pressure over the peripheral area of the gears in the direction of Connection area 23 expands.
  • the one on the scope The pressure applied to each of the gears creates two gears one facing the center of the gear Radial force by one by the drive torque generated mechanical force superimposed becomes.
  • the radial force and the mechanical Force can be added to a vector by vectorial addition resulting force, in the following briefly resultant called, are summarized, their direction of action or line through the center of the corresponding gear.
  • the groove-like pressure distribution space 33 is symmetrical trained to the axis of symmetry 19 and in this exemplary embodiment in the sealing surface 9 brought in.
  • a pressure distribution room 35 Extending from the pressure distribution space 33 there is a groove-like channel in the direction of the connection area 23, here as a pressure distribution room 35 is designated.
  • the pressure distribution space 35 has a tapering towards the suction side Cross-section and leads on the pressure side prevailing system pressure up to approximately 45 ° before Bore 29 of the connection area 23 back.
  • the pressure distribution space 35 in the housing the displacement machine 1 or in the inner surface of the housing 3 another pressure return duct, -bore, groove or the like provided his.
  • the positioning of the pressure distribution rooms 33 and 35 in or on the displacement machine is generally freely selectable. It's important, that the system pressure is defined on the periphery of the Gears is distributable that the gears are pressed against each other become.
  • the gear 13 has a first Print field D1, which is from the print side in Direction of the suction side over an angular range of extends approximately 230 °.
  • the width of the as an annulus segment shown pressure field D1 corresponds to the maximum acting on the connection area 25 Pressure p1 (system pressure).
  • a second pressure field D2 extends over an angular range of approximately 30 ° and in which there is approximately 80% of the maximum pressure p1.
  • the pressure in the pressure field D2 is designated p2.
  • Another, third pressure field D3 connects to the pressure field D2 and extends itself up to the bore 29 of the connection area 23.
  • Pressure p3 which corresponds to approximately 10% of the maximum pressure p1.
  • Due to the arrangement and Design of the pressure distribution rooms 33 and 35 is the extension of the pressure fields D1 to D3 over the circumference of the gear 13 and their pressures p1 exactly defined up to p3.
  • the resulting - Radial force, not shown here, is as above already described - by a mechanical force, superimposed on the drive torque.
  • the one formed from it Resulting R1 takes center stage Gear 13 and closes with the axis of symmetry 19 an angle ⁇ which is less than 90 °.
  • a pressure field D4 a pressure p4, which is approximately 60% of the maximum Pressure is p1.
  • the pressure forces of the Pressure fields D1 and D4 are created by the drive torque induced mechanical force a resultant R2 summarized with the Axis of symmetry 19 includes an angle ⁇ that is less than 90 °.

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

Claims (9)

  1. Machine volumétrique (1) comprenant deux roues dentées à denture extérieure (11, 13) engrenant l'une dans l'autre qui sont logées dans un carter de telle manière que les dents des roues dentées (11, 13) sont en prise de manière étanche avec une surface interne de carter (3), comprenant également des zones de raccordement (23, 25) avec deux niveaux de pression qui sont étanchées l'une par rapport à l'autre par les dents des roues dentées (11, 13) engrenant les unes dans les autres, sachant que la pression régnant dans la zone de raccordement (25) présentant le niveau de pression le plus élevé est ramenée, par l'intermédiaire d'espaces de répartition de la pression (33, 35), vers la zone de raccordement (23) présentant le niveau de pression le plus bas en passant sur une zone périphérique des roues dentées (11, 13), d'où une action exercée par la pression sur le pourtour des roues dentées (11, 13) et une compression des roues dentées l'une vers l'autre due à des forces hydrauliques, caractérisée en ce que, vu dans la direction allant de la première zone de raccordement (25) présentant le niveau de pression le plus élevé à la zone de raccordement (23) présentant le niveau de pression le plus bas, des premiers espaces de répartition de la pression (33) s'étendent sur une zone périphérique des roues dentées (11, 13) de 70° et sont disposés de manière approximativement symétrique par rapport à l'axe de symétrie (19), les centres des roues dentées (11, 13) étant situés sur l'axe de symétrie (19), et en ce que des seconds espaces de répartition de la pression (35) s'étendent, à partir des premiers espaces de répartition de la pression (33), jusque dans une zone périphérique des roues dentées (11, 13) qui est avancée de 45° par rapport à la zone de raccordement (23) présentant le niveau de pression le plus bas.
  2. Machine volumétrique selon la revendication 1, caractérisée en ce que les zones de raccordement (23, 25) sont séparées l'une de l'autre par un joint à deux flancs.
  3. Machine volumétrique selon l'une des revendications précédentes, caractérisée en ce que l'action du niveau de pression élevé sur la zone périphérique des roues dentées (11, 13) génère des forces hydrauliques radiales qui déplacent les roues dentées (11, 13) vers la surface interne (3) du carter, si bien qu'au moins deux dents de chaque roue dentée (11, 13) sont appliquées contre la surface interne (3) du carter de manière à réaliser l'étanchéité.
  4. Machine volumétrique selon l'une des revendications précédentes, caractérisée en ce que les résultantes (R1, R2) issues des forces hydrauliques radiales et de forces mécaniques reposant sur des couples agissant sur l'axe de rotation des roues dentées (11, 13) forment chacune avec l'axe de symétrie (19) un angle (α, β) inférieur à 90°.
  5. Machine volumétrique selon l'une des revendications précédentes, caractérisée en ce que la pression élevée est répartie de façon ciblée sur les zones périphériques des roues dentées (11, 13) par l'intermédiaire des premiers et des seconds espaces de répartition de la pression (33, 35).
  6. Machine volumétrique selon la revendication 1 ou 5, caractérisée en ce que les premiers et seconds espaces de répartition (33, 35) sont réalisés sous forme de rainure dans la surface interne (3) du carter.
  7. Machine volumétrique selon la revendication 5 ou 6, caractérisée en ce que les premiers et seconds espaces de répartition de la pression (33, 35), vus dans la direction radiale, sont situés dans des zones de la surface interne (3) du carter qui sont adjacentes aux dents des roues dentées (11, 13).
  8. Machine volumétrique selon l'une des revendications précédentes, caractérisée en ce que les premiers et seconds espaces de répartition de la pression (33, 35) sont situés dans les surfaces d'étanchéité (9) appliquées contre les surfaces latérales des roues dentées.
  9. Machine volumétrique selon l'une des revendications 5 à 8, caractérisée en ce que les seconds espaces de répartition de la pression (35) présentent une section transversale se rétrécissant en direction de la zone de raccordement (23) présentant le niveau de pression le plus bas.
EP96105855A 1996-04-15 1996-04-15 Machine à engrenages à gradient de pression contrôlé Expired - Lifetime EP0802326B1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
ES96105855T ES2160737T3 (es) 1996-04-15 1996-04-15 Maquina de engranajes con control del campo de presion compensado.
EP96105855A EP0802326B1 (fr) 1996-04-15 1996-04-15 Machine à engrenages à gradient de pression contrôlé
DE59607362T DE59607362D1 (de) 1996-04-15 1996-04-15 Zahnradmaschine mit kontrollierbar ausgeglichenem Druckfeld
US08/673,529 US5730589A (en) 1996-04-15 1996-07-01 Hydraulic displacement machine having gears pressed toward each other
DE19713907A DE19713907A1 (de) 1996-04-15 1997-04-04 Verdrängermaschine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP96105855A EP0802326B1 (fr) 1996-04-15 1996-04-15 Machine à engrenages à gradient de pression contrôlé

Publications (2)

Publication Number Publication Date
EP0802326A1 EP0802326A1 (fr) 1997-10-22
EP0802326B1 true EP0802326B1 (fr) 2001-07-25

Family

ID=8222667

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96105855A Expired - Lifetime EP0802326B1 (fr) 1996-04-15 1996-04-15 Machine à engrenages à gradient de pression contrôlé

Country Status (4)

Country Link
US (1) US5730589A (fr)
EP (1) EP0802326B1 (fr)
DE (2) DE59607362D1 (fr)
ES (1) ES2160737T3 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3830313B2 (ja) * 1999-09-06 2006-10-04 株式会社ジェイテクト ギヤポンプ
DE10002708C1 (de) * 2000-01-22 2001-07-26 Bosch Gmbh Robert Hydraulische Zahnradmaschine
US7597145B2 (en) * 2005-05-18 2009-10-06 Blue Marble Engineering, L.L.C. Fluid-flow system, device and method
JP6311644B2 (ja) * 2015-04-28 2018-04-18 株式会社Ｓｏｋｅｎ ギヤポンプ装置

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0692633A1 (fr) * 1994-07-14 1996-01-17 CASAPPA S.p.A. Pompe à engrenages

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB541961A (en) * 1939-03-16 1941-12-19 Frederic Mcintyre A metering or spinning pump primarily for use in the manufacture of rayon or other synthetic fibres
US2624287A (en) * 1949-10-08 1953-01-06 Borg Warner Gear pump
US2864315A (en) * 1954-02-11 1958-12-16 Holley Carburetor Co Liquid pump
DE1264958B (de) * 1960-10-08 1968-03-28 Bosch Gmbh Robert Zahnradpumpe oder -motor
US3285188A (en) * 1963-06-17 1966-11-15 Shimadzu Corp Hydraulic gear motor or hydraulic gear pump
US3474736A (en) * 1967-12-27 1969-10-28 Koehring Co Pressure loaded gear pump
DE2411492C2 (de) * 1974-03-11 1984-07-26 Robert Bosch Gmbh, 7000 Stuttgart Zahnradpumpe
US4087216A (en) * 1976-10-05 1978-05-02 Permco, Inc. Flow diverter pressure plate
US4239468A (en) * 1978-09-08 1980-12-16 The Rexroth Corporation Apparatus for controlling pressure distribution in gear pump
US4311444A (en) * 1979-04-19 1982-01-19 Shumate Donald L Pressure-balancing end plate for a reversible gear pump or motor
CA1162106A (fr) * 1979-11-19 1984-02-14 Charles J. Bowden Gradient de pression pour machine hydraulique rotative
SU907302A1 (ru) * 1980-01-14 1982-02-23 Винницкий Проектно-Конструкторский Технологический Институт Гидроагрегатов Шестеренна гидромашина

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0692633A1 (fr) * 1994-07-14 1996-01-17 CASAPPA S.p.A. Pompe à engrenages

Also Published As

Publication number Publication date
ES2160737T3 (es) 2001-11-16
US5730589A (en) 1998-03-24
EP0802326A1 (fr) 1997-10-22
DE59607362D1 (de) 2001-08-30
DE19713907A1 (de) 1997-11-06

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