EP0802326A1 - Pressure gradient controlled gear machine - Google Patents

Pressure gradient controlled gear machine Download PDF

Info

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)
French (fr)
Other versions
EP0802326B1 (en
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 DE59607362T priority Critical patent/DE59607362D1/en
Priority to ES96105855T priority patent/ES2160737T3/en
Priority to EP96105855A priority patent/EP0802326B1/en
Priority to US08/673,529 priority patent/US5730589A/en
Priority to DE19713907A priority patent/DE19713907A1/en
Publication of EP0802326A1 publication Critical patent/EP0802326A1/en
Application granted granted Critical
Publication of EP0802326B1 publication Critical patent/EP0802326B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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)

Abstract

The machine has externally toothed meshing gears in a housing with two connection sections at different pressure levels. The pressure in the section (25) with the higher level is returned to the section (23) with the lower level via a circumferential section of the gears (11, 13). This causes the gears to be pressed against each other by hydraulic forces. The connection sections are separated by a dual-flank seal. The high pressure acting on the gear circumferences generates hydraulic radial forces, which move the gears against the inner housing surface, so that two, pref. three teeth of each gear engage sealing on that wall.

Description

Die Erfindung betrifft eine Verdrängermaschine mit zwei miteinander kämmenden, außenverzahnten Zahnrädern gemäß Oberbegriff des Anspruchs 1.The invention relates to a displacement machine with two intermeshing, externally toothed gears according to the preamble of claim 1.

Verdrängermaschinen der eingangs genannten Art sind bekannt. Derartige Maschinen zeichnen sich durch hohe Laufgeräusche sowie relativ starke Förderstrompulsationen aus, die störend und daher unerwünscht sind. Durch Vorgabe und Toleranzen (Ritzelkopfkreis- und Gehäuseinnendurchmesser) entsteht ein Spiel zwischen dem Zahnkopf und dem Gehäuse der Verdrängermaschine beziehungsweise der Gehäuseinnenfläche, an der der Zahnkopf anliegt. Dadurch kann der auf der Druckseite anstehende Systemdruck teilweise auf den Umfangsbereich der Zahnräder einwirken, so daß diese radial mit einer Kraft beaufschlagt werden. Zusätzlich werden die Räder durch ein Antriebsdrehmoment belastet. Die an einem Zahnrad angreifenden Kräfte ergeben eine resultierende Kraft, deren Wirkungslinie mit der Wirklinie der resultierenden Kraft des anderen Zahnrades divergiert, das heißt die Zahnräder werden durch die voneinander weg gerichteten resultierenden Kräfte auseinandergedrückt. Dadurch ergibt sich ein erhöhtes Flankenspiel in dem Bereich, in dem die Zähne der Zahnräder miteinander kämmen und die Saugseite von der Druckseite der Verdrängermaschine trennen. Das erhöhte Flankenspiel hat zur Folge, daß ein relativ großes Volumen zwischen den Zähnen eingequetscht wird, wodurch der Fluid-Förderstrom auf der Druckseite pulsierenden Druckstößen unterworfen wird, die auch zu einem erhöhten Schalleistungspegel führen.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. The forces acting on a gearwheel result in a resultant force, the line of action of which diverges with the line of action of the resultant force of the other gearwheel, that is to say the gearwheels are pressed apart by the resulting forces directed away from one another. This results in an increased backlash in the area in which the teeth of the gears mesh and the Separate the suction side from the pressure side of the displacement machine. The increased backlash results in a relatively large volume being squeezed between the teeth, as a result of which the fluid flow on the pressure side is subjected to pulsating pressure surges, which also lead to an increased sound power level.

Es ist daher Aufgabe der Erfindung, eine Verdrängermaschine zu schaffen, die eine geringe Förderstrompulsation und einen reduzierten Schalleistungspegel aufweist.It is therefore an object of the invention to provide a displacement machine which has a low flow pulsation and a reduced sound power level.

Zur Lösung dieser Aufgabe wird eine Verdrängermaschine vorgeschlagen, die die in Anspruch 1 genannten Merkmale aufweist. Dadurch, daß der im das höhere Druckniveau aufweisenden Anschlußbereich herrschende Druck über einen Umfangsbereich der Zahnräder zu dem das niedrigere Druckniveau aufweisenden Anschlußbereich zurückgeführt wird, so daß die Zahnräder durch hydraulische Kräfte gegeneinandergepreßt werden, wird auf einfache Weise gewährleistet, daß die auf die Zahnräder wirkenden resultierenden Kräfte beziehungsweise deren Wirkungslinien sich in einem auf der Saugseite befindlichen Bereich schneiden. Dies führt dazu, daß die Bewegungen der Zahnräder aufeinander zu gerichtet sind, wodurch die Zähne in dem Bereich, in dem sie miteinander kämmen, ineinandergeschoben werden, so daß einerseits das Flankenspiel der Zahnräder sowie andererseits der Raum verkleinert ist, den zwei Zähne miteinander einschließen. Die Verringerung des eingeschlossenen Raumvolumens führt unmittelbar zu einer Reduzierung der in diesem Raum eingeschlossenen, auch als Quetschvolumen bezeichneten Fluidmenge und somit zu einer erheblichen Verringerung der Förderstrompulsation, also der Druckschwingungen in dem das höhere Druckniveau aufweisenden Anschlußbereich, aufgrund dessen der Schalleistungspegel der Verdrängermaschine wesentlich verringert ist.To solve this problem, a displacement machine is proposed 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.

Besonders bevorzugt wird eine Ausführungsform der Verdrängermaschine, bei der die Anschlußbereiche durch eine Zweiflankendichtung voneinander getrennt sind: Die Zahnräder werden durch die auf sie wirkenden resultierenden Kräfte derart aufeinander zu bewegt, daß die miteinander kämmenden Zähne die Saugseite und Druckseite mittels dreier Berühr- beziehungsweise Dichtpunkte trennen. Die somit ausgebildete Zweiflankendichtung wird also dadurch realisiert, daß ein Zahn mit seinen beiden Flanken gleichzeitig an den Flanken von zwei Zähnen des anderen Zahnrades abwälzt, wodurch permanent drei Dichtpunkte gegeben sind, die auf einer Eingriffslinie angeordnet sind und sich entlang dieser bewegen. Die Zweiflankendichtung führt auch zu einer Verringerung des Quetschvolumens, wodurch die Förderstrompulsation im Vergleich zu einer Einflankendichtung, die lediglich zwei Eingriffs- beziehungsweise Dichtpunkte im Trennbereich zwischen Saug- und Druckseite aufweist, um 75% reduziert ist. Aufgrund der Proportionalität zwischen Laufgeräusch und Förderstrompulsation ist der Geräuschpegel dementsprechend herabgesetzt.An embodiment of the displacement machine is particularly preferred in which the 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.

Bevorzugt wird auch eine Ausführungsform der Verdrängermaschine, bei der die Resultierenden aus den hydraulischen Radialkräften und aus den auf auf die Drehachse der Zahnräder wirkenden Drehmomenten beruhenden mechanischen Kräften mit einer Symmetrieachse jeweils einen Winkel einschließen, der kleiner 90° ist. Dies bewirkt im Bereich des durch die Fertigungstoleranzen möglichen Spiels eine aufeinander zu gerichtete Bewegung der beiden Zahnräder, wodurch die Zähne der Zahnräder derart ineinandergreifen, daß beide Flanken der die Saug- von der Druckseite trennenden Zähne eines Zahnrads an den Flanken eines Zahns des anderen Zahnrads anliegen.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 .

Weitere Ausgestaltungen ergeben sich aus den übrigen Unteransprüchen.Further configurations result from the remaining subclaims.

Die Erfindung wird im folgenden anhand der einzigen Figur erläutert, die einen schematischen Querschnitt einer Verdrängermaschine zeigt.The invention is explained below with reference to the single figure, which shows a schematic cross section of a displacement machine.

Im folgenden wird rein beispielhaft davon ausgegangen, daß die Verdrängermaschine als Pumpe betrieben wird, das heißt ein Zahnrad wird mit einem Antriebsmoment beaufschlagt, so daß ein Fluid gefördert wird. Es ist möglich, die Funktionsweise der Verdrängermaschine umzukehren und diese auch als Motor zu betreiben. In diesem Fall werden die Zahnräder von einem Fluidstrom in Drehung versetzt und das dabei an den Zahnrädern wirkende Drehmoment mittels geeigneter Einrichtungen an den als Abtriebswelle wirkenden Drehachsen der Zahnräder abgegriffen. Damit wird also das Drehmoment über die Abtriebswelle des Hydromotors an einen Verbraucher weitergegeben.In the following it is assumed, purely by way of example, that 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. In this case, 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.

Die Figur zeigt eine schematische Schnittansicht einer Verdrängermaschine 1 mit einem Gehäuse, von dem hier lediglich die Gehäuseinnenfläche 3 dargestellt ist. Die Gehäuseinnenfläche 3 umschließt einen Innenraum 5, der an seinen Stirnseiten von Dichtflächen begrenzt wird. Die Dichtflächen werden üblicherweise von auch als Druckplatten bezeichneten Deckeln verschlossen. In dieser Darstellung ist der vordere Deckel abgenommen und lediglich der hintere Deckel 7 mit seiner Dichtfläche 9 dargestellt. Der Innenraum 5 weist einen Querschnitt in Form einer Acht auf, der durch zwei achsparallele Bohrungen gebildet ist. In dem Innenraum 5 sind zwei außenverzahnte Zahnräder 11 und 13 angeordnet, die drehfest mit Drehachsen 15 und 17 verbunden sind und deren Seitenflächen dicht an den Dichtflächen anliegen. Die Mittelpunkte der Zahnräder 11 und 13 liegen jeweils auf einem Schnittpunkt, der von einer Symmetrieachse 19 und einer Ebene E1 beziehungsweise von der Symmetrieachse 19 und einer Ebene E2 gebildet ist. Die Ebenen E1 und E2 verlaufen parallel zueinander und orthogonal zur Symmetrieachse 19. Die Zahnräder 11 und 13 kämmen in einem Trennbereich 21 miteinander, der zwei Anschlußbereiche 23 und 25 voneinander trennt. Das zu fördernde Fluid wird von dem das niedrigere Druckniveau aufweisenden Anschlußbereich 23 (Saugseite) zu dem Anschlußbereich 25 (Druckseite) gefördert, der ein höheres Druckniveau als der Anschlußbereich 23 aufweist.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. In this illustration, 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. In the interior 5, 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.

Zwischen jeweils zwei Zähnen eines Zahnrads und der Gehäuseinnenfläche 3 wird ein Förderraum 27 ausgebildet, in dem das Fluid von der Saugseite zur Druckseite gefördert wird. Im Anschlußbereich 23 ist eine Bohrung 29 in das Gehäuse der Verdrängermaschine 1 eingebracht, mittels der der Innenraum 5 mit einer das Fluid anliefernden -hier nicht dargestellten- Leitung verbunden ist. Das Gehäuse weist eine weitere Bohrung 31 auf, die im Anschlußbereich 25 angeordnet ist und in die das von den Förderräumen 27 angelieferte, unter Druck stehende Fluid aus der Verdrängermaschine 1 gefördert und beispielsweise einem Verbraucher zuführt wird.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. In the connection area 23, 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.

In der Dichtfläche 9 des stirnseitigen Deckels 7 sind Druckverteilungsräume 33 und 35 vorgesehen, auf deren Funktion im folgenden näher eingegangen wird. Aufgrund der Symmetrie der Verdrängermaschine 1 bezüglich einer Horizontalen H wird nachstehend lediglich auf die dem oberen Zahnrad 11 zugeordneten Druckverteilungsräume 33 und 35 eingegangen.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.

Das gewünschte Spiel zwischen den Zahnköpfen 37 der Zahnräder 11 und 13 und der Gehäuseinnenfläche 3 führt dazu, daß von dem das höhere Druckniveau aufweisenden Anschlußbereich 25 der Druck sich über den Umfangsbereich der Zahnräder in Richtung des Anschlußbereichs 23 ausweitet. Der auf dem Umfang der Zahnräder anstehende Druck erzeugt an jedem der beiden Zahnräder eine zum Zahnradmittelpunkt gerichtete Radialkraft, die von einer durch das Antriebsdrehmoment erzeugten mechanischen Kraft überlagert wird. Die Radialkraft und die mechanische Kraft können durch vektorielle Addition zu einer resultierenden Kraft, im folgenden kurz Resultierende genannt, zusammengefaßt werden, deren Wirkungsrichtung beziehungsweise -linie durch den Mittelpunkt des entsprechenden Zahnrads verläuft.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.

Durch die resultierende Kraft werden die Zahnräder verlagert, wodurch einige der Zahnköpfe 37 im Bereich der Saugseite an die Gehäuseinnenfläche 3 gepreßt werden, so daß eine Trennung des Druckbereichs vom Saugbereich am Umfang der Zahnräder 11 und 13 gegeben ist. Durch die Verlagerung nehmen die Zahnräder 11 und 13 eine exzentrische Lage im Gehäuse der Verdrängermaschine ein. Um den Richtungssinn der Resultierenden gezielt beeinflussen zu können, sind die Druckverteilungsräume 33 und 35 in die Dichtfläche 9 eingebracht. Der im Anschlußbereich 25 herrschende Druck weitet sich über den Umfangsbereich der Zahnräder aus, wird durch den in der Dichtfläche 9 angeordneten Druckverteilungsraum 33 gezielt weitergeleitet und über einen Umfangsbereich der Zahnräder in Richtung der Saugseite geführt. Der Druckverteilungsraum 33 beginnt -entgegen der Förderrichtung betrachtet- circa 90° vor der Bohrung 31 und erstreckt sich teilringartig über einen Winkelbereich von annähernd 70° über die Peripherie des Zahnrads.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.

Der nutartige Druckverteilungsraum 33 ist symmetrisch zur Symmetrieachse 19 ausgebildet und in diesem Ausführungsbeispiel in die Dichtfläche 9 eingebracht. Alternativ dazu ist es möglich, den Druck von der Druckseite über eine in der Gehäuseinnenfläche 3 angeordnete, als Druckverteilungsraum wirkende Ausnehmung, eine Nut, einen Rückströmkanal oder dergleichen zurückzuführen.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. As an alternative to this, it is possible to print from the pressure side via an in the housing inner surface 3 arranged, acting as a pressure distribution space, a groove, a return flow channel or the like.

Ausgehend von dem Druckverteilungsraum 33 erstreckt sich ein nutartiger Kanal in Richtung des Anschlußbereichs 23, der hier als Druckverteilungsraum 35 bezeichnet ist. Der Druckverteilungsraum 35 weist einen in Richtung zur Saugseite verjüngenden Querschnitt auf und führt den auf der Druckseite herrschenden Systemdruck bis auf circa 45° vor die Bohrung 29 des Anschlußbereichs 23 zurück. Anstelle oder zusätzlich zum Druckverteilungsraum 35 kann, in einem weiteren Ausführungsbeispiel, im Gehäuse der Verdrängermaschine 1 beziehungsweise in die Gehäuseinnenfläche 3 ein weiterer Druckrückführungskanal, -bohrung, -nut oder dergleichen vorgesehen sein. Die Positionierung der Druckverteilungsräume 33 und 35 in oder an der Verdrängermaschine ist generell frei wählbar. Wichtig ist, daß der Systemdruck definiert so auf der Peripherie der Zahnräder verteilbar ist, daß die Zahnräder gegeneinandergepreßt werden.Starting from the pressure distribution space 33, 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. Instead of or in addition to the pressure distribution space 35, in a further exemplary embodiment, 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.

In der Figur ist der in dieser Zahnrädereingriffstellung sich einstellende, momentane Druckverlauf am Umfang der Zahnräder 11 und 13 mit einer schraffierten Fläche 39 angedeutet. Je nach Stellung der Zahnräder 11 und 13 ergeben sich unterschiedliche Drücke aufweisende Druckfelder an deren Peripherie. So weist das Zahnrad 13 ein erstes Druckfeld D1 auf, das sich von der Druckseite in Richtung der Saugseite über einen Winkelbereich von circa 230° erstreckt. Die Breite des als Kreisringsegment dargestellten Druckfeldes D1 entspricht dem maximalen, an dem Anschlußbereich 25 wirkenden Druck p1 (Systemdruck). An das Druckfeld D1 schließt sich ein zweites Druckfeld D2 an, das sich über einen Winkelbereich von circa 30° erstreckt und in dem etwa 80% des maximalen Drucks p1 herrschen. Der Druck im Druckfeld D2 ist mit p2 bezeichnet. Ein weiteres, drittes Druckfeld D3 schließt sich an das Druckfeld D2 an und erstreckt sich bis unmittelbar zur Bohrung 29 des Anschlußbereichs 23. In diesem Druckfeld D3 herrscht ein Druck p3, der etwa 10% des maximalen Drucks p1 entspricht. Durch die erfindungsgemäße Anordnung und Ausgestaltung der Druckverteilungsräume 33 und 35 ist die Erstreckung der Druckfelder D1 bis D3 über den Umfang des Zahnrads 13 sowie deren Drücke p1 bis p3 exakt definiert. Die sich daraus ergebende - hier nicht dargestellte- Radialkraft wird -wie oben bereits beschrieben- von einer mechanischen Kraft, dem Antriebs-Drehmoment überlagert. Die daraus gebildete Resultierende R1 greift im Mittelpunkt des Zahnrads 13 an und schließt mit der Symmetrieachse 19 einen Winkel α ein, der kleiner 90° ist. Am Zahnrad 11 erstreckt sich, ausgehend vom Anschlußbereich 25, ebenfalls ein Druckfeld D1 mit dem Druck p1 über einen Winkelbereich von circa 230°. Daran anschließend ist ein Druckfeld D4 mit einem Druck p4 angeordnet, der ungefähr 60% des maximalen Drucks p1 beträgt. Die Druckkräfte der Druckfelder D1 und D4 werden mit der durch das Antriebsmoment hervorgerufenen mechanischen Kraft zu einer Resultierenden R2 zusammengefaßt, die mit der Symmetrieachse 19 einen Winkel β einschließt, der kleiner 90° ist.In the figure, 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. Depending on the position of the gears 11 and 13, there are different pressure fields at their periphery. 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. In 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 α with the axis of symmetry 19 which is less than 90 °. On the gearwheel 11, starting from the connection area 25, 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 β with the axis of symmetry 19 which is less than 90 °.

Die beiden Resultierenden R1 und R2 beziehungsweise deren Wirkungslinien sind derart zueinander ausgerichtet, daß sie sich auf der Saugseite der Verdrängermaschine 1 in einem Bereich schneiden, der links von der Symmetrieachse 19 zwischen den Ebenen E1 und E2 liegt. Dadurch werden die Zahnräder 11 und 13 im Trennbereich 21 ineinandergeschoben, so daß sich eine Zweiflankendichtung ergibt. Unter einer Zweiflankendichtung ist -wie oben erläutert- zu verstehen, daß ein Zahn eines Zahnrads mit seinen beiden Flanken an jeweils benachbarten Zähnen des anderen Zahnrads anliegt und sich an diesen abwälzt. Dadurch ergeben sich drei Eingriffspunkte zwischen den Zahnrädern 11 und 13 im Trennbereich 21, so daß zwei Räume 41 und 43 gebildet werden, in denen ein Volumen eingequetscht und praktisch ständig im Kreis gefördert wird. Die Eingriffspunkte sind immer auf einer gleichbleibenden Eingriffslinie 45 angeordnet und bewegen sich auf dieser entlang. Durch die Zweiflankendichtung wird das eingequetschte Volumen in den Räumen 41 und 43 minimiert, wodurch sich eine erheblich reduzierte Förderstrompulsation ergibt.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. As a result, 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. This results in three points of engagement between the gears 11 and 13 in the separation area 21, so that two spaces 41 and 43 are formed, in which a volume is squeezed and practically continuously conveyed in a circle. The engagement points are always arranged on a constant engagement line 45 and move along this. The squeezed volume in rooms 41 and 43 is minimized by the double-flank seal, which results in a considerably reduced flow pulsation.

Das Abdichten der Saugseite von der Druckseite mittels einer Zweiflankendichtung stellt eine Maßnahme entgegen dem in der Fachwelt allgemein verbreiteten Vorurteil dar, daß diese Abdichtung fertigungstechnisch zu aufwendig ist. Die in bekannten Verdrängermaschinen angewandte Einflankendichtung, mit lediglich zwei Eingriffspunkten im Trennbereich, weist eine Förderstrompulsation auf, die um einen Faktor 4 größer ist.Sealing the suction side from the pressure side by means of a two-flank seal represents a measure contrary to the common prejudice in the professional world that this seal is too complex to manufacture. The in known displacement machines applied single-flank seal, with only two points of engagement in the separation area, has a flow pulsation that is a factor of 4 larger.

Die Lage der Druckverteilungsräume 33 und 35 sowie deren Ausgestaltung und Erstreckung über den Umfangsbereich der Zahnräder ist in Abhängigkeit der Verzahnungsauslegung (Zähnezahl, Zahngeometrie) variabel. Entscheidend ist, daß der im Anschlußbereich 25 herrschende Systemdruck so zurückgeführt und auf den Umfang der Zahnräder verteilt wird, daß sich die Wirkungslinien der Resultierenden R1 und R2 im Bereich der Saugseite -wie oben beschriebenschneiden beziehungsweise mit der Symmetrieachse 19 jeweils einen Winkel einschließen, der kleiner 90° ist. Auf diese Weise wird eine optimale Dichtung zwischen Saug- und Druckseite der Verdrängermaschine erreicht, die allein auf hydraulischen Kräften beruht. Es bedarf keiner zusätzlichen mechanischen Hilfsmittel, die die Zahnräder gegeneinanderpressen und die einem erheblichen Verschleiß unterliegen.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.

Claims (10)

Verdrängermaschine mit zwei miteinander kämmenden, außenverzahnten Zahnrädern, die in einem Gehäuse derart untergebracht sind, daß die Zähne der Zahnräder mit einer Gehäuseinnenfläche dichtend in Eingriff stehen, mit zwei verschiedene Druckniveaus aufweisenden Anschlußbereichen, die von den ineinandergreifenden Zähnen der Zahnräder gegeneinander abgedichtet sind, dadurch gekennzeichnet, daß der im das höhere Druckniveau aufweisenden Anschlußbereich (25) herrschende Druck über einen Umfangsbereich der Zahnräder (11,13) zu dem das niedrigere Druckniveau aufweisenden Anschlußbereich (23) zurückgeführt wird, so daß die Zahnräder (11,13) durch hydraulische Kräfte gegeneinandergepreßt werden.Displacement machine with two intermeshing externally toothed gears, which are housed in a housing such that the teeth of the gears are provided with a housing inner surface sealingly engages, having two different pressure levels terminal regions that are sealed by the intermeshing teeth of the gear wheels against one another, characterized that of having in the higher pressure level connection region, so that the gear wheels (11,13) pressed against each other (25) pressure prevailing over a circumferential region of the gears (11,13) to the lower pressure level having terminal region (23) is returned by hydraulic forces will. Verdrängermaschine nach Anspruch 1, dadurch gekennzeichnet, daß die Anschlußbereiche (23,25) durch eine Zweiflankendichtung voneinander getrennt sind.Displacement machine according to Claim 1, characterized in that the connection areas (23, 25) are separated from one another by a double-flank seal. Verdrängermaschine nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß durch das hohe auf den Umfangsbereich der Zahnräder (11,13) wirkende Druckniveau hydraulische Radialkräfte aufgebaut werden, die die Zahnräder (11,13) gegen die Gehäuseinnenfläche (3) verlagern, so daß wenigstens zwei, vorzugsweise drei Zähne des jeweiligen Zahnrads (11,13) an der Gehäuseinnenfläche (3) dichtend anliegen.Displacement machine according to one of the preceding claims, characterized in that hydraulic radial forces are built up by the high pressure level acting on the peripheral region of the gear wheels (11, 13), which force the gear wheels (11, 13). shift against the inner surface of the housing (3) so that at least two, preferably three teeth of the respective gear (11, 13) lie sealingly against the inner surface (3) of the housing. Verdrängermaschine nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Resultierenden (R1,R2) aus den hydraulischen Radialkräften und aus auf auf die Drehachse der Zahnräder (11,13) wirkenden Drehmomenten beruhenden mechanischen Kräften mit einer Symmetrieachse (19) jeweils einen Winkel (α,β) einschließen, der kleiner 90° ist.Displacement machine according to one of the preceding claims, characterized in that the resultants (R 1 , R 2 ) each have an axis of symmetry (19) from the hydraulic radial forces and from mechanical forces based on the torques acting on the axis of rotation of the gear wheels (11, 13) Include angle (α, β) that is less than 90 °. Verdrängermaschine nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß der hohe Druck mittels vorzugsweise als Nut ausgebildeten Druckverteilungsräumen (33,35) gezielt auf die Umfangsbereiche der Zahnräder (11,13) verteilt ist.Displacement machine according to one of the preceding claims, characterized in that the high pressure is deliberately distributed over the peripheral regions of the gearwheels (11, 13) by means of pressure distribution spaces (33, 35) which are preferably in the form of a groove. Verdrängermaschine nach Anspruch 5, dadurch gekennzeichnet, daß die Druckverteilungsräume (33,35) -in radialer Richtung gesehen- in zu den Zähnen der Zahnräder (11,13) benachbarten Bereichen der Gehäuseinnenfläche (3) angeordnet sind.Displacement machine according to Claim 5, characterized in that the pressure distribution spaces (33, 35) - viewed in the radial direction - are arranged in regions of the housing inner surface (3) adjacent to the teeth of the gear wheels (11, 13). Verdrängermaschine nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Druckverteilungsräume (33,35) an den Zahnradseitenflächen anliegenden Dichtflächen (9) angeordnet sind.Displacement machine according to one of the preceding claims, characterized in that the pressure distribution spaces (33, 35) are arranged on the sealing surfaces (9) abutting the gear side surfaces. Verdrängermaschine nach einem der Ansprüche 5 bis 7, dadurch gekennzeichnet, daß die Druckverteilungsräume (35) einen in Richtung des das niedrigere Druckniveau aufweisenden Anschlußbereich (23) verjüngenden Querschnitt aufweisen.Displacement machine according to one of Claims 5 to 7, characterized in that the pressure distribution spaces (35) have a cross section which tapers in the direction of the connection region (23) which has the lower pressure level. Verdrängermaschine nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Druckverteilungsräume (33) sich über einen Umfangsbereich der Zahnräder (11,13) von vorzugsweise 70° erstrecken und annähernd symmetrisch zur Symmetrieachse (19) angeordnet sind.Displacement machine according to one of the preceding claims, characterized in that the pressure distribution spaces (33) extend over a peripheral region of the gearwheels (11, 13) of preferably 70 ° and are arranged approximately symmetrically to the axis of symmetry (19). Verdrängermaschine nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Druckverteilungsräume (35) -ausgehend von den Druckverteilungsräumen (33)- sich bis in einen Umfangsbereich der Zahnräder erstrecken, der vorzugsweise 45° vor dem das niedrigere Druckniveau aufweisenden Anschlußbereich (23) angeordnet ist.Displacement machine according to one of the preceding claims, characterized in that the pressure distribution spaces (35) - starting from the pressure distribution spaces (33) - extend into a peripheral region of the gearwheels, which is preferably arranged 45 ° in front of the connection region (23) having the lower pressure level .
EP96105855A 1996-04-15 1996-04-15 Pressure gradient controlled gear machine Expired - Lifetime EP0802326B1 (en)

Priority Applications (5)

Application Number Priority Date Filing Date Title
DE59607362T DE59607362D1 (en) 1996-04-15 1996-04-15 Gear machine with controllable, balanced pressure field
ES96105855T ES2160737T3 (en) 1996-04-15 1996-04-15 GEAR MACHINE WITH COMPENSATED PRESSURE FIELD CONTROL.
EP96105855A EP0802326B1 (en) 1996-04-15 1996-04-15 Pressure gradient controlled gear machine
US08/673,529 US5730589A (en) 1996-04-15 1996-07-01 Hydraulic displacement machine having gears pressed toward each other
DE19713907A DE19713907A1 (en) 1996-04-15 1997-04-04 Displacement machine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP96105855A EP0802326B1 (en) 1996-04-15 1996-04-15 Pressure gradient controlled gear machine

Publications (2)

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

Family

ID=8222667

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96105855A Expired - Lifetime EP0802326B1 (en) 1996-04-15 1996-04-15 Pressure gradient controlled gear machine

Country Status (4)

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

Families Citing this family (4)

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

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 (en) * 1974-03-11 1975-10-10 Bosch Gmbh Robert
US4087216A (en) * 1976-10-05 1978-05-02 Permco, Inc. Flow diverter pressure plate
EP0018216A1 (en) * 1979-04-19 1980-10-29 Donald L. Shumate Reversible gear pump or motor and diverter plates therefor
US4239468A (en) * 1978-09-08 1980-12-16 The Rexroth Corporation Apparatus for controlling pressure distribution in gear pump
EP0029356A1 (en) * 1979-11-19 1981-05-27 General Signal Corporation Pressure gradient controlled rotary hydraulic machine

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 (en) * 1980-01-14 1982-02-23 Винницкий Проектно-Конструкторский Технологический Институт Гидроагрегатов Gear hydraulic machine
US5624251A (en) * 1994-07-14 1997-04-29 Casappa S.P.A. Gear pump

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 (en) * 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 (en) * 1979-04-19 1980-10-29 Donald L. Shumate Reversible gear pump or motor and diverter plates therefor
EP0029356A1 (en) * 1979-11-19 1981-05-27 General Signal Corporation Pressure gradient controlled rotary hydraulic machine

Also Published As

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

Similar Documents

Publication Publication Date Title
EP0043899B1 (en) Annular gear pump
EP0254077B1 (en) Internal gear pump
DE2242269C3 (en) Gear pump or motor
DE1503667A1 (en) Displacement machine with a screw rotor and fluid seals
EP0619430B1 (en) Internal gear pump for high rotary speed range
DE19613833A1 (en) Gear pump with meshing internal and external toothed wheels
DE60222884T2 (en) IMPROVED FLUID COUNTER DEVICE
DE4104397C2 (en) Internal gear pump
EP0802326A1 (en) Pressure gradient controlled gear machine
DE2016171A1 (en) Multi-flow metering device
DE102004046934B4 (en) Hydraulic machine
EP0607497B1 (en) Internal gear pump with sealings incorporated in the teeth
DE102007036608A1 (en) Gearwheel pump with variable flow volumes has displacement arrangement in tooth gaps with variable displacement volumes connected to control chamber in base body
DE69909339T2 (en) Internal gear motor and distributor valve
DE2029832A1 (en) Rotary piston working machine
DE2134241C3 (en) Two-stage external-axis rotary piston machine
DE4242217C2 (en) Gear machine (pump or motor)
DE102016213696B4 (en) Gear fluid machine
DE2339872A1 (en) Pump or rotor gearwheel unit - has pressur medium fed between gearwheel teeth without connection between feed chamber and outflow chamber
EP0244575B1 (en) Internal-gear pump
DE4225804C2 (en) Gear machine
DE1282385B (en) Rotary valve and process for its manufacture
EP0686771A2 (en) Internal gear pump with sealings incorporated in the teeth
DE2709913A1 (en) GEAR MACHINE (PUMP OR MOTOR)
DE3134668A1 (en) Annular gear motor

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE ES FR GB IT

17P Request for examination filed

Effective date: 19971115

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: HALDEX BARNES GMBH

17Q First examination report despatched

Effective date: 20000623

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE ES FR GB IT

REF Corresponds to:

Ref document number: 59607362

Country of ref document: DE

Date of ref document: 20010830

ITF It: translation for a ep patent filed
GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20010914

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2160737

Country of ref document: ES

Kind code of ref document: T3

EN Fr: translation not filed
REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

EN Fr: translation not filed

Free format text: BO 01/51 PAGES: 265, IL Y A LIEU DE SUPPRIMER: LA MENTION DE LA NON REMISE. LA REMISE EST PUBLIEE DANS LE PRESENT BOPI.

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: ES

Payment date: 20120424

Year of fee payment: 17

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20130418

Year of fee payment: 18

Ref country code: DE

Payment date: 20130427

Year of fee payment: 18

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20130515

Year of fee payment: 18

Ref country code: IT

Payment date: 20130423

Year of fee payment: 18

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 59607362

Country of ref document: DE

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20140415

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 59607362

Country of ref document: DE

Effective date: 20141101

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20141231

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20140415

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20141101

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20140430

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20140415

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20150527

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20140416