EP0685650B1 - Aussenzahnradhydraulikeinrichtung - Google Patents

Aussenzahnradhydraulikeinrichtung Download PDF

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Publication number
EP0685650B1
EP0685650B1 EP95201391A EP95201391A EP0685650B1 EP 0685650 B1 EP0685650 B1 EP 0685650B1 EP 95201391 A EP95201391 A EP 95201391A EP 95201391 A EP95201391 A EP 95201391A EP 0685650 B1 EP0685650 B1 EP 0685650B1
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EP
European Patent Office
Prior art keywords
divider plate
cavity
hydraulic device
chambers
inlet
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Expired - Lifetime
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EP95201391A
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English (en)
French (fr)
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EP0685650A1 (de
Inventor
Giuseppe Salami
Gianfranco Leo
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SALAMI SpA
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SALAMI SpA
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    • 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
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • F04C11/001—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle

Definitions

  • the invention concerns an external gear hydraulic device, i.e. an external volumetric gear pump, or motor, comprising a hollow body acting as casing closed off axially at one end by a cover and by a flange at the opposite end, the hollow body having a seat in the form of two opposing lobes in which are coupled rotationally pairs of gearwheels that mesh with each other.
  • an external gear hydraulic device i.e. an external volumetric gear pump, or motor
  • the prior art comprises gear pumps of the type described above, in which the hollow body is generally obtained by extruding high strength aluminium, or by casting metallic material, for example, special cast iron.
  • supports are provided for the rotational coupling of the shafts, onto which the gearwheels are keyed, said supports being set into in the two-lobe cavity in which the said gearwheels are positioned: in this way the gearwheels are automatically positioned coaxially in the relative lobe of the cavity in which they are placed.
  • two or more independent pumping elements When two or more independent pumping elements are required, having the same displacements or even displacements that are not the same, they are arranged in series, whereby the driving shaft of the pair of gearwheels of one pumping element is coupled in series, by means of a coupling, with the driving shaft of the next pumping element, and so on: the resulting axial dimension corresponding to the sum of the axial lengths of the bodies of each pumping element, to which have to be added the axial lengths of the couplings, the thickness of a cover and that of a flange.
  • the supports of the shafts of each pumping element are set into the cover and into the flange, thereby requiring these to be positioned with respect to the body by means of centering pins that entail a high degree of precision during machining and therefore high costs: when a number of pumping elements are required, the body of the pump is split into sections in order to insert, between the shaft of one pumping element and the next, the coupling for transmitting the rotation, this entailing further machining difficulties, considerable costs and sizeable overall dimensions.
  • the technical problem to be solved by the invention is that of simplifying the manufacture of hydraulic devices, such as gear motor or pumps.
  • the problem consists in achieving, in an extremely simple and economical manner, a number of independent chambers in a single gear motor or pump.
  • a gear motor or pum having the features of claim 1.
  • a device comprising a casing having a lobed cavity, said casing being fitted with positionable partitioning means that divide the lobed cavity into at least two distinct and independent chambers.
  • Each chamber may be provided with an inlet and a respective outlet; this is particularly advantageous when the hydraulic device has to be used as a bi-directional gear motor or pump.
  • the chambers may also have a common inlet and distinct outlets, which is preferable when the hydraulic device has to be used as uni-directional pump, or as a gear motor flow-divider.
  • outlets may be conected toghether and a check valve may be interposed between them, particularly when the device has to be used as an high-low (hi-lo) pump.
  • the said positionable partitioning means consists of at least one divider plate that may be placed axially inside the cavity with two opposing lobes in correspondence with a transverse plane perpendicular to the axis of the said cavity.
  • One of the advantages of the present invention lies in the reduction in overall dimensions achieved by adopting the said solution when at least two independent pumping or motor elements are required.
  • Another advantage lies in the fact that it is possible, using the same pump, or motor, body of a predetermined length, to obtain a range of different displacements for the chambers in function of the axial position in which the divider plate is set during assembly: this gives significant benefits in terms of the reduction of spare parts kept in stock and greatly simplifies the production cycle; also, the solution as described is suitable for use both with pumps, or motors, having bodies obtained by extrusion and with pumps having bodies obtained from a casting.
  • the divider plate can advantageously be made of a wearproof low friction material suitable for coupling with the ends of the gearwheels, solution which is impracticable with prior art pumps, in particular those obtained from a casting, in which only one material is used in the manufacture of the body of the pump, and impossible with pumps, or motors, having extruded bodies in which it is not possible to obtain structural elements formed in a plane that is perpendicular to the axis of extrusion.
  • the device has a single inlet opening that passes through the body of the pump, divided into two parts by the underlying divider plate, so as to supply a flow to the two pumping chambers separately, said flow being advantageously proportional to the displacement of each chamber.
  • the divider plate may be positioned centrally with respect to the said opening, or even offset with respect to it, that is, displaced along the axis of the cavity towards one of the chambers.
  • the axial length of the divider plate that is, its dimension in a direction parallel to the axis of the cavity with two opposing lobes, is less than the sum of the axial lengths of the end supports: it being envisaged that the reduction in length may be of the order of approximately 30% or even up to 50%.
  • the reduction in the axial length envisaged for the divider plate enables, taking into account the manner in which the pump, or motor, is operated during its working life, the quantity of materials used in its manufacture to be optimised eliminating onerous waste caused by over designing.
  • the said divider plate has a plane of symmetry parallel to the axis of the cavity with two opposing lobes and is divided into two parts at the said plane.
  • each one of the two parts into which the divider plate is divided can be obtained by axial-symmetric machining from a semifinished piece obtained by forming, for example by casting, or forged, or even swarf machined from bars using normal machine tools.
  • the divider plate has a first recess, positioned on the side corresponding to the inlet, thereby making the pumping, or motor, chambers axially intercommunicating so as to improve the filling of them.
  • the divider plate On its side facing the outlet, the divider plate may have a second recess, analogous to said first recess, but coupling with a plugging element of the same shape protruding from the surface defining the cavity and extending inwards in a position corresponding to the join between the lobes, so as to prevent the pumping chambers from being interconnected on the outlet side.
  • the divider plate can be symmetrical with respect to a plane that is perpendicular to the axis of the cavity with two opposing lobes of the body of the pump.
  • the hydraulic device may include a gear pump 1 having a body 2, for example, obtained by extrusion, to which are fitted axially a cover 3 and, at the opposite end, a flange 4 for coupling it to driving means not shown.
  • the body 2 has a through opening 5, or cavity, preferably having the shape of two opposing symmetrical lobes, for the insertion into them with wet seal of two pairs of end supports 6 of a driving shaft 7 and of a driven shaft 8 ( Figure 2), coupled to each other by means of pairs of driving gearwheels 9, 9a, that is, keyed onto the driving shaft 7, meshing with a corresponding pair of driven gearwheels 10, 10a mounted on the driven shaft 8.
  • the supports 6 are equipped with bushes 6b for the rotary coupling in them of the shafts 7, 8, said bushes being fitted into corresponding axial holes 6a of the supports 6.
  • the cover 3 and the flange 4 are locked onto the body 2, by means of ties 10c; frontal peripheral seals 2a being positioned between the body 2, the cover 3 and the flange 4 respectively.
  • the flange 4 is provided with a through hole 10d for the shaft 7, equipped with rotary sealing elements 10e on the shaft itself.
  • a divider plate 11 In the vicinity of an intermediate section of each shaft 7, 8 there is a divider plate 11 having a pair of through holes 12 for the rotary coupling in them of the shafts 7, 8 with bushes 11 a positioned between them.
  • the divider plate 11 defines, inside the opening 5 of the body 2 having the shape of two opposing lobes, two distinct pumping chambers 13 delimited axially between the said divider plate and the supports 6; said lobes serving as seat for the gearwheels 9, 10, 9a, 10a. It has to be noted that the ends of the gearwheels 9, 9a, 10, 10a have a sliding contact with the divider plate 11 on one side and the end supports 6 on the other side: this making it possible to obtain a range of displacements with predetermined proportions between the pumping chambers 3 by using gearwheels having suitable axial dimensions as shown in Figure 3.
  • the divider plate 11, manufactured separately from the body 2, can be inserted, during assembly, in an appropriate axial position within the opening 5, so as to define chambers 13 that are the same as each other or different from each other, using one single pump body 2: the positioning and fixing in place is preferably achieved by interference-fit assembly, advantageously by heating the body 2 and cooling the divider plate 11.
  • the body can be heated to approximately +250°C and the divider plate can be cooled to approximately -20°C; the temperature levels being equivalent to those suitable in the case of cast iron pumps.
  • the device used for inserting the divider plate in a predetermined axial position inside the body 2 can comprise an assembly manipulator.
  • the inlet opening A for the fluid to be pumped generally oil, consists of a through opening 14 set into the body 2 in a position corresponding to that of the divider plate 11 so as to supply both the pumping chambers 13 in appropriate proportions:
  • the plan view shape of the opening 14 can be circular or rectangular, elongated and radiused at the ends, or mixed (see Figures 6, 7), or other suitable shape.
  • the inlet opening A, 14 can also have a constant oil flow section, or even variable, in particular increasing towards the pumping chambers 13 that it supplies; in this embodiment, the side walls of the opening 14 can have stretches 14a advantageously diverging towards the inside in order to facilitate the complete filling of the pumping chambers, particularly when they extend a long way axially, as in the embodiments shown in Figures 4, 5. Furthermore, such a configuration of the opening 14 makes an optimal filling of the pumping chambers 13 possible even when the divider plate 11, for example, for reasons of strength, extends a long way axially.
  • the divider plate can be placed in a position corresponding to the axis of symmetry of the opening 14, as in Figure 6, or in an off centre position as in Figure 7: in the first case the position of the opening has to be determined in function of the ratio between the displacements of the pumping chambers 13, whereas in the second case the positioning is essentially independent of the position of the divider plate 11.
  • Figures 1, 3, 4 also show how the driving shaft 7 can be provided with coupling means, at the opposite end to the end coupled to the driving means, for example, by means of shank 7a and key 7b, preferably for driving the drive shaft of another pump coupled in series with pump 1: the said driving means possibly consisting of a splined portion 7c.
  • FIG 4 shows an embodiment of a pump in which each pumping chamber 13 is occupied by a pair of gearwheels 15 meshing with each other, each having two ring gears 15a between which a spacer ring 16 is placed.
  • Each ring gear 15a is angularly offset with respect to the other ring gear 15a inserted in the same chamber 13, by an angle corresponding to a fraction of the pitch, preferably 1/2 the pitch between the teeth of each gearwheel: this in order to reduce the noise level of the pump.
  • Each chamber 13, furthermore, is made communicating with the hydraulic circuit downstream by means of a relative outlet M, consisting of a through opening 17 set into the body 2.
  • Figure 5 shows an embodiment in which the body 18, analogously hollow, is obtained from a casting and coupled to a cover 19 and a flange 20.
  • the supports 6 are an integral part of the said cover and said flange and are each equipped with a pair of bushes 6a.
  • the ends of the gearwheels 9, 9a and similarly 10, 10a have a sliding contact, as regards the internal ends, directly on the divider plate 11 and, as regards the external ends, on the respective cover 19 and flange 20 with anti-friction plates 21 positioned between them, that is, manufactured using a material having a low coefficient of friction: it is to be noted that making the divider plate separately from the body makes it possible to save on production costs as anti-friction plates between the ends of the gearwheels 9, 9a, 10, 10a and the divider plate 11 are not required because the divider plate is preferably made from a wearproof material with a low coefficient of friction.
  • Figures 8 to 10 show two possible embodiments of the divider plate 11: it is to be noted that the external surface of the divider plate has to have two opposing lobes 22 so that they may marry with the internal surface of the axial opening 5 with a stable coupling of the forms on assembly.
  • the divider plate On the inlet side A, the divider plate has a first recess 23, in order to improve the filling of the pumping chambers 13.
  • the divider plate has a pair of grooves 23a, interconnecting through holes 12, that are intended to avoid the possibility of cavitation.
  • a second recess 26 can be provided, corresponding to the first recess 23 and positioned opposite it: inside the cavity 5 a plugging element 27 is positioned between the said second recess and the said cavity 5, to prevent the pumping chambers 13 from being intercommunicating on the outlet side.
  • the plugging element 27 may be integral with the body of the hydraulic device 1, and may consist of an internally projecting appendix of the lobed cavity 5.
  • the divider plate is advantageously provided with two pairs of opposing grooves 24, each being "V" shaped, that allow the oil to exit more gradually from the chamber defined by the meshing teeth in a position corresponding to that of the chamber with the highest pressure so as to reduce noise levels.
  • the divider plate is symmetrical with respect to a first plane parallel to the axes of the holes 12, and therefore to the lobed cavity 5: it can therefore be divided into two parts along a first plane of symmetry S, as in the embodiment of Figure 8, positioned with respect to each other by a locating pin on assembly, or it can be made from a single piece, as in the embodiment shown in Figure 10.
  • the divider plate is advantageously symmetrical also in a third plane of symmetry perpendicular to the axis of hole 12.
  • the supports 6 and the plates 21 are such as to compensate the axial thrust acting on the ends of the gearwheels 9, 9a, 10, 10a, 15a of shafts 7, 8.
  • both the driving shaft 7 and the driven shaft 8 may be rotatably coupled to one of the support 6 and to the divider plate 11, thereby the further support 6 serving only as an axial balancing plate.
  • the hydraulic device may include a bi-directional gear motor, or pump, 1a; in the drawings, inlets A are associated to oultets M when the gearwheels 9, 9a are driven in a clockwise direction, while inlets A1 are associated to outlets M1 when the gearwheels 9, 9a are driven in counterclockwise direction.
  • Each chamber 13 is provided with an inlet A, A1, 14b and a respective outlet M, M1, provided for in the body 2 of the motor, or pump, 1a.
  • the divider plate 11b In order to obtain separation between the chambers 13, the divider plate 11b must have an external outline peripherally coupled to the internal outline of the cavity 5; this is preferably achieved by providing a divider plate 11 b which is also symmetrical with respect to a second plane of symmetry passing through the axis of the holes 12.
  • said divider plate 11b has a pair of opposed second recesses 26 engageable with corresponding appendixes 27 of the cavity 5.
  • Each second recess 26 is provided with a respective V-shaped groove 24.
  • a hydraulic hi-lo pump 1c has outlets joined together by a connecting channel 30 provided with a check valve 31, a pilot line 32 piloting a sequence valve 33; said sequence velve 33 being inserted into a by-pass line 34 of one chamber 13.
  • a gear motor flow divider 1d as shown in Figure 16, is provided with a divider plate 11c, having a first recess 23 and a second recess 26, both having a V-shaped groove 24: the gear motor flow divider 1d has a pair of opposing covers 4, both ends of shafts 7d being provided with coupling means 7c.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Claims (18)

  1. Außenverzahnungshydraulikeinrichtung (1, 1a, 1c, 1d) zur Verwendung als Zahnradmotor oder -pumpe mit: einem hohlen Körper (2), der als ein Gehäuse der Einrichtung fungiert und einen Leerraum (5) mit einer im Querschnitt weitgehend achtförmigen Konfiguration besitzt; Paaren von miteinander kämmenden Zahnrädern (9, 9a, 10, 10a, 15, 15a), die drehend gekoppelt und in dem Leerraum (5) angeordnet sind; einer Trenneinrichtung (11, 11b, 11c), die mit einem Sitz in dem Leerraum zu dessen Teilung in wenigstens zwei eigenständige unabhängige Kammern (13) positionierbar ist; einer Verschlusseinrichtung (3, 4, 19, 20) zum Verschließen des Leerraumee (5) an einander gegenüberliegenden Enden; und Einlass- (A, A1) und Auslass- (M, M1) Öffnungen für den Einlass beziehungsweise den Auslass eines hydraulischen Fluids in den Kammern (13) dadurch gekennzeichnet, dass die Trenneinrichtung von einer Trennplatte (11, 11b, 11c) gebildet ist, die in wenigstens zwei Symmetrieebenen, vorzugsweise in drei Symmetrieebenen symmetrisch ist und einen ersten (23) sowie einen zweiten (26) symmetrischen Aufnahmeraum (26) besitzt, der an den gegenüberliegenden Enden der Trennplatte (11, 11b, 11c) vorgesehen ist entsprechend der Einlass- und Auslassseite des Leerraumes (5) zur Verteilung der Fluidströmung zwischen den beiden Kammern an wenigstens der Einlassseite, wobei wenigstens der zweite Aufnahmeraum (26) durch ein Verschlusselement (27) verschließbar ist, welches die Fluidströmung zwischen den Kammern abschneidet und die Trennplatte (11, 11b, 11c) eine weitgehend achtförmige Konfiguration aufweist, die mit der Konfiguration des Leerraumes (5) übereinstimmt und in dem Leerraum (5) mit einem Sitz an mehreren ausgewählten Positionen zur Begrenzung von eigenständigen Kammern (13) mit unterschiedlichen axialen Erstreckungen aufnehmbar ist, die zur Aufnahme von jeweils Paaren der Zahnräder mit unterschiedlichen axialen Abmessungen ausgebildet sind, wodurch innerhalb eines Körpers (2) von einer vorbestimmten Länge eine beliebige einer Vielzahl von Pumpen- oder Motorkonfigurationen einstellbar sind, die zur Einstellung einer ausgewählten einer Vielzahl von unterschiedlichen Volumina und Fluideinlass- und Auslasskonfigurationen geeignet sind.
  2. Hydraulikeinrichtung nach Anspruch 1, wobei jede Kammer (13) mit einer unabhängigen Auslassöffnung (M, M1, 17) und mit einer Einlassöffnung (A, 14, 14a) versehen ist, die mit einer zugehörigen Einlassöffnung (A, 14, 14a) einer weiteren Kammer (13) in Verbindung steht.
  3. Hydraulikeinrichtung nach Anspruch 1, wobei jede Kammer (13) mit einer unabhängigen Auslassöffnung (M, M1, 14b, 17) und einer unabhängigen Einlassöffnung (A, A1, 14, 14b, 17) versehen ist.
  4. Hydraulikeinrichtung nach einem der vorhergehenden Ansprüche, wobei die Trennplatte (11, 11b, 11c) ein Paar von Durchgangsöffnungen (12) zur drehenden Aufnahme von jeweiligen Wellen (7, 8) besitzt, an denen die Zahnräder (9 9a, 10, 10a, 15, 15a) vorgesehen sind.
  5. Hydraulikeinrichtung nach Anspruch 2, wobei eine einzelne Einlassöffnung (14) vorgesehen ist zum Durchsetzen des Körpers (2) der Pumpe, wobei die Öffnung von der darunterliegenden Trennplatte (11) in zwei Abschnitte geteilt ist.
  6. Hydraulikeinrichtung nach einem der vorhergehenden Ansprüche, wobei die Einlassöffnung (14a) Seitenwände besitzt, die einen zu den Kammern (13) hin zunehmenden Strömungsquerschnitt begrenzen.
  7. Hydraulikeinrichtung nach Anspruch 5, wobei die Anordnung der Trennplatte (11) bezüglich der Kammern (13) derart ist, dass der Strom der in jede Kammer (13) eintretenden Flüssigkeit proportional zu ihrem Volumen ist.
  8. Hydraulikeinrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass sie Paare von Endaufnahmen (6) aufweist, die an Enden des Leerraumes zum Abstützen der Zahnradwellen (7, 8) dichtend eingesetzt sind und dass die lineare Abmessung der Trennplatte (11) in einer Richtung parallel zu der Achse des Leerraumes (5) kleiner ist als die Summe der entsprechenden axialen Abmessungen der Endaufnahmen (6), wobei die Verkleinerung der Länge die Größenordnung von 30% oder sogar bis zu 50% aufweist.
  9. Hydraulikeinrichtung nach einem der vorhergehenden Ansprüche, wobei das Verschlusselement (27) in den Leerraum (5) an einer Position entsprechend der Verbindung zwischen den Hälften des Hohlraumes (5) vorsteht.
  10. Hydraulikeinrichtung nach einem der vorhergehenden Ansprüche, wobei die Trennplatte (11) zwei Paare von Nuten (23a) zweiseitig und einander gegenüberliegend besitzt, die sich zwischen den Durchgangsöffnungen (12) für die Wellenverbindung erstrecken.
  11. Hydraulikeinrichtung nach einem der vorhergehenden Ansprüche, wobei die Trennplatte (11, 11b, 11c) an der Seite der Auslassöffnung (17) zwei Paare von zweiseitig gegenüberliegenden Nuten (24) aufweist, die "V"-förmig sind.
  12. Hydraulikeinrichtung nach einem der vorhergehenden Ansprüche, wobei die Trennplatte (11, 11b, 11c) die erste Symmetrieebene (S) parallel zu der Achse des Leerraumes (5) aufweist.
  13. Hydraulikeinrichtung nach einem der vorhergehenden Ansprüche, wobei die Trennplatte (11b) die zweite Symmetrieebene die Achse der Bohrungen (12) durchsetzend besitzt.
  14. Hydraulikeinrichtung nach einem der vorhergehenden Ansprüche, wobei die Trennplatte (11, 11b, 11c) die dritte Symmetrieebene rechtwinklig zu der Achse der Bohrung (12) besitzt.
  15. Hydraulikeinrichtung nach einem der vorhergehenden Ansprüche, wobei die Trennplatte (11, 11b, 11c) aus einem abriebfesten Werkstoff mit einem niedrigen Reibungskoeffizienten gewonnen wird.
  16. Hydraulikeinrichtung nach einem der vorhergehenden Ansprüche, wobei jedes Zahnrad (10, 10a, 15, 15a) zwei Hohlräder (10a, 15a) besitzt, zwischen denen ein Abstandshaltering (16) angeordnet ist, wobei die Hohlräder Zähne aufweisen, die zueinander im Winkel versetzt sind.
  17. Verfahren zur Herstellung einer Außenverzahnungshydraulikeinrichtung (1, 1a, 1c, 1d) nach Anspruch 1 zur Verwendung als Zahnradmotor oder -pumpe, wobei das Verfahren folgende Schritte umfasst:
    Bereitstellen eines hohlen Körpern (2) von vorbestimmter Länge durch Extrusion oder Formgebung als ein Gehäuse der Einrichtung mit einem Leerraum (5) mit einer im Querschnitt weitgehend achtförmigen Konfiguration;
    Bereitstellen einer Verschlusseinrichtung (3, 4, 19, 20) zum Verschließen des Leerraumes (5) an seinen einander gegenüber liegenden Enden;
    Bereitstellen einer Trenneinrichtung (11, 11b, 11c), die mit einem Passsitz in dem Leerraum angeordnet werden kann zu dessen Teilung in wenigstens zwei eigenständige unabhängige Kammern (13) ;
    Bereitstellen von Einlass (A, A1) und Auslass (M, M1) Öffnungen an dem Körper (2) für den Einlass und den Auslass eines Hydraulikfluids in den Kammern (13) ;
    Bereitstellen in jeder der Kammern (13) von Paaren von miteinander kämmenden Zahnrädern, (9, 9a, 10, 10a, 15, 15a) die zur Drehung gekoppelt sind,
    dadurch gekennzeichnet, dass es weiterhin folgendes umfasst:
    Bereitstellen der Trenneinrichtung durch eine Bearbeitung in Form einer Trennplatte (11, 11b, 11c), die in wenigstens zwei Symmetrieebenen, vorzugsweise in drei Symmetrieebenen symmetrisch ist und eine weitgehend achtförmige Konfiguration aufweist, die mit der Konfiguration des Leerraumes (5) übereinstimmt und eine erste (23) sowie eine zweite (26) symmetrische Vertiefung (26) an gegenüberliegenden Seiten der Trennplatte (11, 11b, 11c) besitzt, um nach der Montage der Einrichtung der Einlaes- und Auslassseite des Leerraumes (5) zur Verteilung der Fluidströmung zwischen den beiden Kammern (13) an wenigstens der Einlassseite zu entsprechen;
    Bereitstellen wenigstens eines Verschlusselements (27), welches zum Verschließen nach der Montage der Einrichtung von wenigstens der zweiten Vertiefung (26) ausgebildet ist zum Absperren der Fluidströmung zwischen den Kammern (13);
    Positionieren und Festlegen der Trennplatte (11, 11b, 11c) mittels eines Presssitzes in dem Leerraum (5) an einer beliebigen von einer Vielzahl von ausgewählten Positionen zur Begrenzung von getrennten Kammern (13) mit unterschiedlichen axialen Erstreckungen, die zur Aufnahme von Zahnrädern mit unterschiedlichen axialen Dimensionen ausgebildet sind, wodurch innerhalb eines Körpers (2) von einer vorbestimmten Länge eine von einer Vielzahl von Pumpen- oder Motorkonfigurationen geschaffen wird, die zur Einstellung einer ausgewählten einer Vielzahl von unterschiedlichen Volumina und Fluideinlass- sowie Auslasskonfigurationen geeignet sind.
  18. Verfahren nach Anspruch 17, dadurch gekennzeichnet, dass die Trennplatte (11, 11b, 11c) aus einem widerstandsfähigen, reibungsarmen Werkstoff hergestellt ist.
EP95201391A 1994-05-31 1995-05-30 Aussenzahnradhydraulikeinrichtung Expired - Lifetime EP0685650B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ITMO940077 1994-05-31
ITMO940077A IT1269371B (it) 1994-05-31 1994-05-31 Pompa volumetrica ad ingranaggi

Publications (2)

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EP0685650A1 EP0685650A1 (de) 1995-12-06
EP0685650B1 true EP0685650B1 (de) 2000-03-15

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EP (1) EP0685650B1 (de)
JP (1) JPH08100774A (de)
DE (1) DE69515555D1 (de)
IT (1) IT1269371B (de)

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ITMO940077A0 (it) 1994-05-31
EP0685650A1 (de) 1995-12-06
JPH08100774A (ja) 1996-04-16
DE69515555D1 (de) 2000-04-20
IT1269371B (it) 1997-03-26
ITMO940077A1 (it) 1995-12-01

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