EP0802326A1 - 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
EP0802326A1
EP0802326A1 EP96105855A EP96105855A EP0802326A1 EP 0802326 A1 EP0802326 A1 EP 0802326A1 EP 96105855 A EP96105855 A EP 96105855A EP 96105855 A EP96105855 A EP 96105855A EP 0802326 A1 EP0802326 A1 EP 0802326A1
Authority
EP
European Patent Office
Prior art keywords
pressure
displacement machine
machine according
gears
pressure distribution
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
EP96105855A
Other languages
German (de)
English (en)
Other versions
EP0802326B1 (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
John S 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 John S Barnes GmbH filed Critical John S Barnes GmbH
Priority to ES96105855T priority Critical patent/ES2160737T3/es
Priority to DE59607362T priority patent/DE59607362D1/de
Priority to EP96105855A priority patent/EP0802326B1/fr
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 with two intermeshing, externally toothed gears according to the preamble of claim 1.
  • Displacement machines of the type mentioned are known. Such machines are characterized by high running noise and relatively strong flow pulsations, which are annoying and therefore undesirable. Due to specifications and tolerances (pinion head circle and housing inner diameter) there is play between the tooth head and the housing of the displacement machine or the housing inner surface against which the tooth head rests. As a result, the system pressure on the pressure side can partially act on the peripheral area of the gearwheels, so that a radial force is exerted on them. In addition, the wheels are loaded by a drive torque.
  • a displacement machine which has the features mentioned in claim 1. Characterized in that the pressure prevailing in the connection area having the higher pressure level is returned via a circumferential area of the gearwheels to the connection area having the lower pressure level, so that the gearwheels are pressed against one another by hydraulic forces, it is ensured in a simple manner that the resultant forces acting on the gearwheels Forces or their lines of action intersect in an area on the suction side. This leads to the movements of the gear wheels being directed towards one another, as a result of which the teeth are pushed into one another in the region in which they mesh with one another, so that on the one hand the backlash of the gear wheels and on the other hand the space which the two teeth enclose are reduced.
  • the reduction of the included The volume of the space leads directly to a reduction in the amount of fluid enclosed in this space, also referred to as the squeeze volume, and thus to a considerable reduction in the flow pulsation, i.e. the pressure fluctuations in the connection area having the higher pressure level, due to which the sound power level of the displacement machine is significantly reduced.
  • connection areas are separated from one another by a double-flank seal: the gearwheels are moved towards one another by the resulting forces acting on them so that the meshing teeth separate the suction side and pressure side by means of three contact or sealing points .
  • the two-flank seal thus formed is thus realized in that a tooth rolls with its two flanks simultaneously on the flanks of two teeth of the other gear, whereby three sealing points are permanently present, which are arranged on an engagement line and move along it.
  • the double-flank seal also leads to a reduction in the pinch volume, which means that the flow rate pulsation is reduced by 75% compared to a single-flank seal that only has two engagement or sealing points in the separation area between the suction and pressure side. Due to the proportionality between running noise and flow pulsation, the noise level is reduced accordingly.
  • An embodiment of the displacement machine is also preferred, in which the resultants from the hydraulic radial forces and from the mechanical forces based on the torques acting on the axis of rotation of the gearwheels each enclose an angle that is less than 90 ° with an axis of symmetry. This causes a movement of the two gearwheels towards one another in the area of the play which is possible due to the manufacturing tolerances, as a result of which the teeth of the gearwheels mesh in such a way that both flanks of the teeth of one gearwheel separating the suction side from the pressure side bear against the flanks of a tooth of the other gearwheel .
  • the displacement machine is operated as a pump, that is to say a gearwheel is subjected to a drive torque, so that a fluid is conveyed. It is possible to reverse the functioning of the displacement machine and to operate it as a motor.
  • the gearwheels are set in rotation by a fluid flow and the torque acting on the gearwheels is tapped off by means of suitable devices on the axes of rotation of the gearwheels acting as output shaft. So that is the torque over the Output shaft of the hydraulic motor passed on to a consumer.
  • the figure shows a schematic sectional view of a displacement machine 1 with a housing, of which only the inner surface 3 of the housing is shown.
  • the housing inner surface 3 encloses an inner space 5 which is delimited on its end faces by sealing surfaces.
  • the sealing surfaces are usually closed by covers also referred to as pressure plates.
  • the front cover is removed and only the rear cover 7 with its sealing surface 9 is shown.
  • the interior 5 has a cross section in the form of an eight, which is formed by two axially parallel bores.
  • two externally toothed gears 11 and 13 are arranged, which are non-rotatably connected to axes of rotation 15 and 17 and the side surfaces of which lie closely against the sealing surfaces.
  • the center points of the gearwheels 11 and 13 each lie on an intersection point which is formed by an axis of symmetry 19 and a plane E1 or by an axis of symmetry 19 and a plane E2.
  • the planes E1 and E2 run parallel to one another and orthogonal to the axis of symmetry 19.
  • the gear wheels 11 and 13 mesh with one another in a separating area 21 which separates two connecting areas 23 and 25 from one another.
  • the fluid to be conveyed is conveyed from the connection area 23 (suction side) having the lower pressure level to the connection area 25 (pressure side), which has a higher pressure level than the connection area 23.
  • a conveying space 27 is formed between two teeth of a gearwheel and the housing inner surface 3, in which the fluid is conveyed from the suction side to the pressure side.
  • a bore 29 is made in the housing of the displacement machine 1, by means of which the interior 5 is connected to a line which supplies the fluid and is not shown here.
  • the housing has a further bore 31, which is arranged in the connection region 25 and into which the pressurized fluid delivered by the delivery spaces 27 is conveyed out of the displacement machine 1 and, for example, supplied to a consumer.
  • Pressure distribution spaces 33 and 35 are provided in the sealing surface 9 of the front cover 7, the function of which will be discussed in more detail below. Due to the symmetry of the displacement machine 1 with respect to a horizontal H, only the pressure distribution spaces 33 and 35 assigned to the upper gearwheel 11 will be discussed below.
  • the desired play between the tooth heads 37 of the gearwheels 11 and 13 and the housing inner surface 3 leads to the pressure of the connection area 25 having the higher pressure level expanding over the circumferential area of the gearwheels in the direction of the connection area 23.
  • the pressure applied to the circumference of the gearwheels generates on each of the two gearwheels a radial force directed towards the gearwheel center, which is superimposed by a mechanical force generated by the drive torque.
  • the radial force and the mechanical Force can be combined by vectorial addition to a resultant force, hereinafter referred to as resultant, the direction or line of action of which runs through the center of the corresponding gear.
  • the resulting force causes the gears to be displaced, as a result of which some of the tooth heads 37 are pressed against the inner surface 3 of the housing in the region of the suction side, so that there is a separation of the pressure region from the suction region on the circumference of the gears 11 and 13. Due to the displacement, the gears 11 and 13 assume an eccentric position in the housing of the displacement machine. In order to be able to influence the direction of the resultants in a targeted manner, the pressure distribution spaces 33 and 35 are introduced into the sealing surface 9.
  • the pressure prevailing in the connection area 25 expands over the circumferential area of the gearwheels, is passed on in a targeted manner through the pressure distribution space 33 arranged in the sealing surface 9 and is guided over a circumferential area of the gearwheels in the direction of the suction side.
  • the pressure distribution chamber 33 begins — viewed in the direction opposite to the conveying direction — approximately 90 ° in front of the bore 31 and extends in the manner of a partial ring over an angular range of approximately 70 ° over the periphery of the gearwheel.
  • the groove-like pressure distribution space 33 is formed symmetrically to the axis of symmetry 19 and is introduced into the sealing surface 9 in this exemplary embodiment.
  • a groove-like channel extends in the direction of the connection area 23, which is referred to here as the pressure distribution space 35.
  • the pressure distribution chamber 35 has a cross section tapering in the direction of the suction side and guides the system pressure prevailing on the pressure side back up to approximately 45 ° in front of the bore 29 of the connection region 23.
  • a further pressure return duct, bore, groove or the like can be provided in the housing of the displacement machine 1 or in the housing inner surface 3.
  • the positioning of the pressure distribution spaces 33 and 35 in or on the displacement machine is generally freely selectable. It is important that the system pressure can be distributed so defined on the periphery of the gears that the gears are pressed against each other.
  • the instantaneous pressure curve occurring in this gearwheel engagement position on the circumference of the gearwheels 11 and 13 is indicated by a hatched area 39.
  • the gear 13 thus has a first pressure field D1, which extends from the pressure side in the direction of the suction side over an angular range of extends approximately 230 °.
  • the width of the pressure field D1 shown as a circular ring segment corresponds to the maximum pressure p1 (system pressure) acting on the connection area 25.
  • the pressure field D1 is followed by a second pressure field D2, which extends over an angular range of approximately 30 ° and in which approximately 80% of the maximum pressure p1 prevail.
  • the pressure in the pressure field D2 is designated p2.
  • Another, third pressure field D3 adjoins the pressure field D2 and extends directly to the bore 29 of the connection area 23.
  • this pressure field D3 there is a pressure p3 which corresponds to approximately 10% of the maximum pressure p1.
  • the arrangement and configuration of the pressure distribution spaces 33 and 35 according to the invention precisely define the extent of the pressure fields D1 to D3 over the circumference of the gear 13 and their pressures p1 to p3.
  • the resulting radial force - not shown here - is - as already described above - superimposed by a mechanical force on the drive torque.
  • the resultant R1 formed therefrom engages in the center of the gearwheel 13 and forms an angle ⁇ with the axis of symmetry 19 which is less than 90 °.
  • a pressure field D1 with the pressure p1 also extends over an angular range of approximately 230 °.
  • a pressure field D4 with a pressure p4 which is approximately 60% of the maximum pressure p1 is arranged thereafter.
  • the pressure forces of the pressure fields D1 and D4 increase with the mechanical force caused by the drive torque a resultant R2 is summarized, which includes an angle ⁇ with the axis of symmetry 19 which is less than 90 °.
  • the two resultants R1 and R2 or their lines of action are aligned with one another in such a way that they intersect on the suction side of the displacement machine 1 in a region which is to the left of the axis of symmetry 19 between the planes E1 and E2.
  • the gears 11 and 13 are pushed into one another in the separating region 21, so that a two-flank seal results.
  • a two-flank seal is - as explained above - to be understood that a tooth of a gear wheel with its two flanks rests on adjacent teeth of the other gear wheel and rolls on them.
  • the position of the pressure distribution spaces 33 and 35 as well as their design and extent over the circumferential area of the gear wheels can be varied depending on the tooth design (number of teeth, tooth geometry). It is crucial that the system pressure prevailing in the connection area 25 is fed back and distributed over the circumference of the gearwheels in such a way that the lines of action of the resultants R1 and R2 intersect in the area of the suction side as described above or enclose an angle with the axis of symmetry 19 which is smaller Is 90 °. In this way, an optimal seal between the suction and pressure side of the displacement machine is achieved, which is based solely on hydraulic forces. There is no need for additional mechanical aids that press the gears against each other and that are subject to considerable wear.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Hydraulic Motors (AREA)
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.
DE59607362T DE59607362D1 (de) 1996-04-15 1996-04-15 Zahnradmaschine mit kontrollierbar ausgeglichenem Druckfeld
EP96105855A EP0802326B1 (fr) 1996-04-15 1996-04-15 Machine à engrenages à gradient de pression contrôlé
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 true EP0802326A1 (fr) 1997-10-22
EP0802326B1 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 (7)

* 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
GB965470A (en) * 1960-10-08 1964-07-29 Bosch Gmbh Robert Improvements in or relating to hydraulic pumps or motors
FR2264199A1 (fr) * 1974-03-11 1975-10-10 Bosch Gmbh Robert
US4087216A (en) * 1976-10-05 1978-05-02 Permco, Inc. Flow diverter pressure plate
EP0018216A1 (fr) * 1979-04-19 1980-10-29 Donald L. Shumate Pompe ou moteur réversible à engrenages et plaques d'écartement y relatives
US4239468A (en) * 1978-09-08 1980-12-16 The Rexroth Corporation Apparatus for controlling pressure distribution in gear pump
EP0029356A1 (fr) * 1979-11-19 1981-05-27 General Signal Corporation Machine hydraulique rotative à gradient de pression contrôlé

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
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
SU907302A1 (ru) * 1980-01-14 1982-02-23 Винницкий Проектно-Конструкторский Технологический Институт Гидроагрегатов Шестеренна гидромашина
ES2229228T3 (es) * 1994-07-14 2005-04-16 Casappa S.P.A. Bomba de engranajes.

Patent Citations (7)

* 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
GB965470A (en) * 1960-10-08 1964-07-29 Bosch Gmbh Robert Improvements in or relating to hydraulic pumps or motors
FR2264199A1 (fr) * 1974-03-11 1975-10-10 Bosch Gmbh Robert
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
EP0018216A1 (fr) * 1979-04-19 1980-10-29 Donald L. Shumate Pompe ou moteur réversible à engrenages et plaques d'écartement y relatives
EP0029356A1 (fr) * 1979-11-19 1981-05-27 General Signal Corporation Machine hydraulique rotative à gradient de pression contrôlé

Also Published As

Publication number Publication date
ES2160737T3 (es) 2001-11-16
EP0802326B1 (fr) 2001-07-25
DE59607362D1 (de) 2001-08-30
DE19713907A1 (de) 1997-11-06
US5730589A (en) 1998-03-24

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