EP0093917B1 - Reversible gear machine (motor or pump) - Google Patents

Reversible gear machine (motor or pump) Download PDF

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Publication number
EP0093917B1
EP0093917B1 EP83103941A EP83103941A EP0093917B1 EP 0093917 B1 EP0093917 B1 EP 0093917B1 EP 83103941 A EP83103941 A EP 83103941A EP 83103941 A EP83103941 A EP 83103941A EP 0093917 B1 EP0093917 B1 EP 0093917B1
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EP
European Patent Office
Prior art keywords
gasket
pressure
bores
gearwheels
faces
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Expired
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EP83103941A
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German (de)
French (fr)
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EP0093917A1 (en
Inventor
Wilhelm Dworak
Hayno Dipl.-Ing. Rustige
Günter Wolff
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP0093917A1 publication Critical patent/EP0093917A1/en
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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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0023—Axial sealings for working fluid
    • F04C15/0026—Elements specially adapted for sealing of the lateral faces of intermeshing-engagement type machines or pumps, e.g. gear machines or pumps

Definitions

  • the invention relates to a gear machine (pump or motor) according to the preamble of the claim.
  • the seal has two narrow, approximately radially outwardly extending extensions. The field between them is subjected to high pressure, and the entire field under this seal is also subjected to high pressure (GB-A-12 10 824 / GB-A-12 10 825).
  • the object of the invention is to provide a gear machine according to the type of the claim, in which not only the liquid forces acting on the sealing plates or bearing bodies are particularly well compensated, but which also has very good operational reliability and a long service life.
  • FIG. 1 shows a longitudinal section through a gear motor
  • FIG. 2 shows a section along 11-11 according to FIG. 1
  • FIG. 1 shows a single part
  • FIG. 4 shows a section along IV-IV according to FIG. 3
  • FIGS. 5, 6 and 7 show another single part in plan view, Side view and bottom view
  • FIG. 8 shows a section along VIII-VIII according to FIG. 5
  • FIG. 9 shows the individual parts according to FIGS. 3 to 8 in the installed state
  • FIG. 10 shows a further individual part in plan view
  • FIG. 11 shows a section along XI-XI according to FIG 10,
  • FIG. 12 shows a diagram of the pressure fields.
  • 10 denotes the housing of a gear motor or a gear pump, which is closed on both sides by covers 11, 12.
  • the interior 13 of the housing 10 is formed by two intersecting bores 14, 15 so that it takes the form of an 8.
  • bush-shaped bearing bodies 16 to 19 are arranged in pairs, which have aligned central bores 20 to 23 in pairs.
  • the shaft journals 24, 25 of an externally toothed gear 26 are mounted, in the bearing bodies 18, 19 or their bores 22, 23, the shaft journals 27, 28 of a gear 29, which with the gear 26 meshes in external engagement.
  • a shaft extension 31 Connected to the shaft journal 25 of the gearwheel 26 is a shaft extension 31 which penetrates to the outside through a bore 32 formed in the cover 12 and is used to drive the pump or to deliver a torque in engine operation.
  • the two ends of the bores 20, 22 are connected by a channel 33 formed in the cover 11, which leads to a bore 34 penetrating the cover.
  • the gearwheel 29, together with its shaft journals 27, 28, is penetrated by a continuous bore 35 which also has a connection to the bore 34.
  • a channel 37 leads from the bore 32 in the cover 12 to the bore 23 in the bearing body 19.
  • the channels or bores 33 to 37 are used only for drainage of oil, ie. H. the ends of the shaft journals and the ends of the holes 20-23 are relieved of the bore 34 and the container.
  • FIGS. 10 and 11 most clearly show one of the bearing bodies 16 to 19, for example the bearing body 16. All of the bearing bodies are of the same design.
  • the bearing body 16 has on its end face facing the cover 11 an annular groove 39 which runs at a short distance a from the bore 20 and which, compared to the flattened side 40 of the bearing body, has an approximately segment-shaped, relatively wide extension 41 which extends to the edge of the bearing body.
  • the groove 39 On its area facing the flat side, the groove 39 has a narrow outlet 44 which extends to the flat side 40.
  • the cross section of the groove 39 can be seen in FIG. 9.
  • the groove has a rectangular cross section and a rounded bottom 39 '.
  • a seal is arranged in the groove 39 together with the extension 41 and the outlet 44, which consists of a support ring 46 made of plastic and a sealing body 47 made of rubber.
  • the support ring 46 is shown in detail in FIGS. 3 and 4, the sealing body 47 in FIGS. 5 to 8.
  • the support ring 46 is approximately in the form of glasses and has an approximately sector-like extension 49, 50 on each of its two diametrically opposite regions, which extends into the extensions 41 on the bearing bodies 16 to 19 fits.
  • the two circular parts are connected by a web 51 which fits into the outlet 44 of the bearing body.
  • the support ring 46 - as shown in Figure 4 - is U-shaped.
  • the sealing body 47 is inserted into this U-shaped recess. This is shown in Figures 5 to 8. It has the same shape as the support ring 46, but has a different cross section, which is shown in FIG. With its upper broad part 53, the sealing body fits into the U-shaped recess of the support ring 46.
  • the sealing body 53 In its central region, the sealing body 53 has two transverse webs 54, 55, the width of which corresponds to that of the support ring. A central, longer web 56 adjoins the webs 54, 55. In the installed state, the web 56 forms two spaces 57, 58 with the groove 39, which lie on the bottom of the groove, but which are connected to one another in the operating state when the support ring together with the sealing ring are pressed against the cover. This also indicates the installation position of the two parts in the groove.
  • the support ring 46 rests on the cover 11, 12, while the sealing body 47 faces the groove base.
  • the sealing body 47 has on its diametrically opposite sides circular sector-shaped extensions 60, 61 which fit into extensions 49, 50 of the support ring.
  • the cross section of the sealing body in the area of the extension 60, 61 results from the section according to FIG. 6, from which it can be seen that the web 56 runs out laterally in this area.
  • two axially identical bores 65, 66 penetrate into the interior 13 of the housing and open in the region of the gearwheels 26, 29. These holes are used to supply or discharge the pressure medium.
  • the gear machine works as a gear motor and high-pressure pressure medium is supplied to the bore 65. This is fed through the rotating gears along the circumference of the bore 66 now serving as an outlet.
  • the high-pressure pressure medium penetrates through an approximately triangular gusset 67, which is formed between the interior 13 of the housing and the bearing bodies 16-19 and extends over the entire height thereof, into the gap which is formed between the bearing bodies and the covers is.
  • a first pressure field 68 ′, 68 ′′ and a second pressure field build up on the high-pressure side between the support ring 46 and the end faces of the bearing bodies, which corresponds exactly to the entire surface of the support ring 46 and lies below it - that is, between the grooves 39, 41 44 on the bearing bodies and the support ring 46 - which pressure field is also acted on by the high pressure via the grooves 42, 43 on the outer circumference of the bearing bodies 46.
  • the support rings 46 together with the seals 47 are pressed against the covers 11, 12 by liquid pressure.
  • the pressure prevailing in the outlet bore 66 prevails at the third pressure fields 70 ′, 70 ′′ opposite the pressure fields 68 ′, 68 ′′, because these fields have an approximately triangular gusset 72 that lies between the interior 13 of the housing and the bearing bodies is connected to hole 66.
  • the outlet pressure can be very low, but also high if a second gear motor is connected to the bore 66.
  • Fourth pressure fields are formed in the annular spaces 74-75 located between the support ring 46 and the bearing bores 20-23. These are always loaded by the leakage oil pressure prevailing in the bores 33, 34, which can be a maximum of 5-8 bar. Due to the four pressure fields described, the bearing bodies 16-19 are brought into sealing contact with the gear side surfaces. The force to be compensated for by the annular pressure fields 74, 75 results from an area on the face of the gearwheel, which lies approximately between the root circle of the gearwheels and the diameter of the bores 20-23 times the leakage oil pressure prevailing there.
  • the gear machine is reversible, i. H. the high pressure can also be supplied at the bore 66; the low pressure side is then at the bore 65.
  • the high pressure fields now build up at 70 ', 70 "and again under the support ring surface, the low pressure fields are at 68', 68".
  • the effect is exactly the same as described above. It is of course possible to arrange pressurized bearing bodies only on one side of the gearwheels, while the other two bearing bodies are not pressurized and rest rigidly on the cover.
  • the diagram according to FIG. 12 again clearly shows the position of the four pressure fields, the 68 ', 68 "and the support ring surface 46 (all cross-hatched) being acted upon by the same pressure (high pressure), the surfaces 70', 70" by the return pressure (hatched in the right direction) and the ring surfaces (shaded to the left) from the leakage oil pressure.

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

Description

Die Erfindung geht aus von einer Zahnradmaschine (Pumpe oder Motor) nach der Gattung des Patentanspruchs. Bei einer derartigen bekannten Zahnradmaschine weist die Dichtung zwei schmale, etwa radial unter einem Winkel von 90° nach außen verlaufende Fortsätze auf. Das zwischen diesen liegende Feld ist mit Hochdruck beaufschlagt, weiterhin ist mit Hochdruck auch das gesamte Feld unter dieser Dichtung beaufschlagt (GB-A-12 10 824/GB-A-12 10 825).The invention relates to a gear machine (pump or motor) according to the preamble of the claim. In such a known gear machine, the seal has two narrow, approximately radially outwardly extending extensions. The field between them is subjected to high pressure, and the entire field under this seal is also subjected to high pressure (GB-A-12 10 824 / GB-A-12 10 825).

Um Druckfelder begrenzende Dichtungen bei Hochleistungszahnradmaschinen besonders gut zu schützen, ist es bekannt, die Dichtungen zweiteilig auszubilden, wobei das eine, an der Dichtplatte anliegende Dichtungsteil aus einem härteren Werkstoff besteht als das andere, in ersteres eingebettete. (GB-A-20 33 478).In order to protect seals which limit pressure fields particularly well in high-performance gear machines, it is known to form the seals in two parts, the one sealing part lying against the sealing plate being made of a harder material than the other, embedded in the former. (GB-A-20 33 478).

Die Aufgabe der Erfindung besteht darin, eine Zahnradmaschine nach der Gattung des Patentanspruchs zu schaffen, bei der nicht nur die auf die Dichtplatten bzw. Lagerkörper wirkenden Flüssigkeitskräfte besonders gut kompensiert werden, sondern die auch eine sehr gute Betriebssicherheit und lange Lebensdauer aufweist.The object of the invention is to provide a gear machine according to the type of the claim, in which not only the liquid forces acting on the sealing plates or bearing bodies are particularly well compensated, but which also has very good operational reliability and a long service life.

Diese Aufgabe wird erfindungsgemäß durch die im Kennzeichnungsteil des Patentanspruchs angegebenen Merkmale gelöst. Man erreicht hiermit eine gute Funktionsfähigkeit der Maschine, insbesondere auch dann, wenn sie als Hydromotor betrieben wird, Gerade in diesem Betriebszustand ist dies besonders wichtig, da das Anlaufen eines Hydromotors ein besonders kritischer Betriebszustand ist. Darüber hinaus ist die Zahnradmaschine auch nicht sehr aufwendig gestaltet, da die die Zahnradwellen aufnehmenden Buchsen zugleich als Dichtplatten ausgebildet sind.This object is achieved by the features specified in the characterizing part of the patent claim. A good functionality of the machine is hereby achieved, in particular also when it is operated as a hydraulic motor. This is particularly important in this operating state, since starting up a hydraulic motor is a particularly critical operating state. In addition, the gear machine is also not very expensive, since the bushings receiving the gear shaft are also designed as sealing plates.

Zeichnungdrawing

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 einen Längsschnitt durch einen Zahnradmotor, Figur 2 einen Schnitt längs 11-11 nach Figur 1, Figur ein Einzelteil, Figur 4 einen Schnitt längs IV-IV nach Figur 3, Figuren 5, 6 und 7 ein weiteres Einzelteil in Draufsicht, Seitenansicht und Ansicht von unten, Figur 8 einen Schnitt längs VIII-VIII nach Figur 5, Figur 9 die Einzelteile nach den Figuren 3 bis 8 in eingebautem Zustand, Figur 10 ein weiteres Einzelteil in Draufsicht und Figur 11 einen Schnitt längs XI-XI nach Figur 10, Figur 12 ein Schema der Druckfelder.An embodiment of the invention is shown in the drawing and explained in more detail in the following description. 1 shows a longitudinal section through a gear motor, FIG. 2 shows a section along 11-11 according to FIG. 1, FIG. 1 shows a single part, FIG. 4 shows a section along IV-IV according to FIG. 3, FIGS. 5, 6 and 7 show another single part in plan view, Side view and bottom view, FIG. 8 shows a section along VIII-VIII according to FIG. 5, FIG. 9 shows the individual parts according to FIGS. 3 to 8 in the installed state, FIG. 10 shows a further individual part in plan view and FIG. 11 shows a section along XI-XI according to FIG 10, FIG. 12 shows a diagram of the pressure fields.

Beschreibung des AusführungsbeispielsDescription of the embodiment

In den Figuren 1 und 2 ist mit 10 das Gehäuses eines Zahnradmotors bzw. einer Zahnradpumpe bezeichnet, das beidseitig durch Deckel 11, 12 verschlossen ist. Der Innenraum 13 des Gehäuses 10 ist gebildet durch zwei sich überschneidende Bohrungen 14, 15, so daß er die Form einer 8 erhält. Im Innenraum 13 sind paarweise buchsenförmige Lagerkörper 16 bis 19 angeordnet, die paarweise fluchtende mittige Bohrungen 20 bis 23 aufweisen. In den zusammengehörigen Lagerkörpern 16, 17 bzw. deren Bohrungen 20, 21 sind die Wellenzapfen 24, 25 eines außenverzahnten Zahnrads 26 gelagert, in den Lagerkörpern 18, 19 bzw. deren Bohrungen 22, 23 die Wellenzapfen 27, 28 eines Zahnrads 29, das mit dem Zahnrad 26 im Außeneingriff kämmt. An den Wellenzapfen 25 des Zahnrads 26 schließt sich ein Wellenfortsatz 31 an, der durch eine im Deckel 12 ausgebildete Bohrung 32 nach außen dringt und zum Antrieb der Pumpe bzw. zur Abgabe eines Drehmoments im Motorbetrieb dient.In Figures 1 and 2, 10 denotes the housing of a gear motor or a gear pump, which is closed on both sides by covers 11, 12. The interior 13 of the housing 10 is formed by two intersecting bores 14, 15 so that it takes the form of an 8. In the interior 13, bush-shaped bearing bodies 16 to 19 are arranged in pairs, which have aligned central bores 20 to 23 in pairs. In the associated bearing bodies 16, 17 or their bores 20, 21, the shaft journals 24, 25 of an externally toothed gear 26 are mounted, in the bearing bodies 18, 19 or their bores 22, 23, the shaft journals 27, 28 of a gear 29, which with the gear 26 meshes in external engagement. Connected to the shaft journal 25 of the gearwheel 26 is a shaft extension 31 which penetrates to the outside through a bore 32 formed in the cover 12 and is used to drive the pump or to deliver a torque in engine operation.

Die beiden Enden der Bohrungen 20, 22 sind durch einen im Deckel 11 ausgebildeten Kanal 33 verbunden, der zu einer den Deckel durchdringenden Bohrung 34 führt. Das Zahnrad 29 ist samt seinen Wellenzapfen 27, 28 von einer durchgehenden Bohrung 35 durchdrungen, die ebenfalls Verbindung zur Bohrung 34 hat. Von der Bohrung 32 im Deckel 12 führt ein Kanal 37 zur Bohrung 23 im Lagerkörper 19. Die Kanäle bzw. Bohrungen 33 bis 37 dienen lediglich zur Leckölabfuhr, d. h. die Enden der Wellenzapfen bzw. die Enden der Bohrungen 20-23 sind zur Bohrung 34 und zum Behälter entlastet.The two ends of the bores 20, 22 are connected by a channel 33 formed in the cover 11, which leads to a bore 34 penetrating the cover. The gearwheel 29, together with its shaft journals 27, 28, is penetrated by a continuous bore 35 which also has a connection to the bore 34. A channel 37 leads from the bore 32 in the cover 12 to the bore 23 in the bearing body 19. The channels or bores 33 to 37 are used only for drainage of oil, ie. H. the ends of the shaft journals and the ends of the holes 20-23 are relieved of the bore 34 and the container.

Die Figuren 10 und 11 zeigen am deutlichsten einen der Lagerkörper 16 bis 19, beispielsweise den Lagerkörper 16. Sämtliche Lagerkörper sind gleich ausgebildet. Der Lagerkörper 16 hat an seiner dem Deckel 11 zugewandten Stirnseite eine in geringem Abstand a zur Bohrung 20 verlaufende ringförmige Nut 39, die gegenüber der abgeflachten Seite 40 des Lagerkörpers eine etwa segmentförmige, relativ breite Erweiterung 41 aufweist, die bis zum Rande des Lagerkörpers reicht. Im Bereich der Erweiterung 41 sind auch zwei sich am Außenumfang des Lagerkörpers 16 verlaufende Längsnuten 42, 43 ausgebildet, die sich über die gesamte Höhe des Lagerkörpers erstrecken. An ihrem der Flachseite zugewandten Bereich hat die Nut 39 einen schmalen Ausgang 44, der bis zur Flachseite 40 reicht. Der Querschnitt der Nut 39 ist aus der Figur 9 ersichtlich. Die Nut hat rechteckigen Querschnitt und eine gerundete Unterseite 39'. In der Nut 39 samt Erweiterung 41 und Ausgang 44 ist eine Dichtung angeordnet, die aus einem Stützring 46 aus Kunststoff und einem Dichtkörper 47 aus Gummi angeordnet. Der Stützring 46 ist in den Figuren 3 und 4 im einzelnen dargestellt, der Dichtkörper 47 in den Figuren 5 bis 8.FIGS. 10 and 11 most clearly show one of the bearing bodies 16 to 19, for example the bearing body 16. All of the bearing bodies are of the same design. The bearing body 16 has on its end face facing the cover 11 an annular groove 39 which runs at a short distance a from the bore 20 and which, compared to the flattened side 40 of the bearing body, has an approximately segment-shaped, relatively wide extension 41 which extends to the edge of the bearing body. In the area of the extension 41 there are also two longitudinal grooves 42, 43 which extend on the outer circumference of the bearing body 16 and extend over the entire height of the bearing body. On its area facing the flat side, the groove 39 has a narrow outlet 44 which extends to the flat side 40. The cross section of the groove 39 can be seen in FIG. 9. The groove has a rectangular cross section and a rounded bottom 39 '. A seal is arranged in the groove 39 together with the extension 41 and the outlet 44, which consists of a support ring 46 made of plastic and a sealing body 47 made of rubber. The support ring 46 is shown in detail in FIGS. 3 and 4, the sealing body 47 in FIGS. 5 to 8.

Der Stützring 46 weist etwa die Form einer Brille auf und hat an seinen beiden diametral gegenüberliegenden Bereichen jeweils eine etwa sektorartige Erweiterung 49, 50, welche in die Erweiterungen 41 an den Lagerkörpern 16 bis 19 paßt. Die beiden kreisförmigen Teile sind durch einen Steg 51 verbunden, der in den Ausgang 44 der Lagerkörper paßt. Im Querschnitt ist der Stützring 46 - wie Figur 4 zeigt - U-förmig ausgebildet. In diese U-förmige Vertiefung wird der Dichtkörper 47 eingesetzt. Dieser ist in den Figuren 5 bis 8 dargestellt. Er weist dieselbe Form auf wie der Stützring 46, hat jedoch einen anderen Querschnitt, der in Figur 8 dargestellt ist. Mit seinem oberen breiten Teil 53 paßt der Dichtkörper in die U-förmige Ausnehmung des Stützrings 46. In seinem mittleren Bereich weist der Dichtkörper 53 zwei querverlaufende Stege 54, 55 auf, deren Breite derjenigen des Stützrings entspricht. Ein mittiger, längerer Steg 56 schließt sich an die Stege 54, 55 an. In eingebautem Zustand bildet der Steg 56 mit der Nut 39 zwei Räume 57, 58, die am Nutgrund liegen, die aber im Betriebszustand miteinander verbunden sind, wenn Stützring samt Dichtring gegen den Deckel gedrückt werden. Damit ist auch schon die Einbaulage der beiden Teile in die Nut gekennzeichnet. Der Stützring 46 liegt an dem Deckel 11, 12 an, während der Dichtkörper 47 dem Nutgrund zugewandt ist. Der Dichtkörper 47 weist an seinen diametral gegenüberliegenden Seiten kreissektorförmige Erweiterungen 60, 61 auf, die in Erweiterungen 49, 50 des Stützrings passen.The support ring 46 is approximately in the form of glasses and has an approximately sector-like extension 49, 50 on each of its two diametrically opposite regions, which extends into the extensions 41 on the bearing bodies 16 to 19 fits. The two circular parts are connected by a web 51 which fits into the outlet 44 of the bearing body. In cross section, the support ring 46 - as shown in Figure 4 - is U-shaped. The sealing body 47 is inserted into this U-shaped recess. This is shown in Figures 5 to 8. It has the same shape as the support ring 46, but has a different cross section, which is shown in FIG. With its upper broad part 53, the sealing body fits into the U-shaped recess of the support ring 46. In its central region, the sealing body 53 has two transverse webs 54, 55, the width of which corresponds to that of the support ring. A central, longer web 56 adjoins the webs 54, 55. In the installed state, the web 56 forms two spaces 57, 58 with the groove 39, which lie on the bottom of the groove, but which are connected to one another in the operating state when the support ring together with the sealing ring are pressed against the cover. This also indicates the installation position of the two parts in the groove. The support ring 46 rests on the cover 11, 12, while the sealing body 47 faces the groove base. The sealing body 47 has on its diametrically opposite sides circular sector-shaped extensions 60, 61 which fit into extensions 49, 50 of the support ring.

Der Querschnitt des Dichtkörpers im Bereich der Erweiterung 60, 61 ergibt sich aus dem Schnitt nach Figur 6, woraus zu erkennen ist, daß in diesem Bereich der Steg 56 seitlich ausläuft.The cross section of the sealing body in the area of the extension 60, 61 results from the section according to FIG. 6, from which it can be seen that the web 56 runs out laterally in this area.

In die Lagerkörper 16, 18 bzw. 17, 19 ist jeweils ein obenbeschriebener Stütz- und Dichtkörper eingelegt - siehe hierzu Figur 2. Da die Dichtungen identisch sind, tragen sie jeweils dieselbe Bezeichnung.In the bearing bodies 16, 18 and 17, 19, respectively, a support and sealing body described above is inserted - see FIG. 2. Since the seals are identical, they each have the same designation.

In den Innenraum 13 des Gehäuses dringen von gegenüberliegenden Seiten des Gehäuses 10 zwei achsgleiche Bohrungen 65, 66 ein, die im Bereich der Zahnräder 26, 29 münden. Diese Bohrungen dienen zum Zuführen bzw. Abführen des Druckmittels.From the opposite sides of the housing 10, two axially identical bores 65, 66 penetrate into the interior 13 of the housing and open in the region of the gearwheels 26, 29. These holes are used to supply or discharge the pressure medium.

Es sei angenommen, die Zahnradmaschine arbeite als Zahnradmotor und unter Hochdruck stehendes Druckmittel wird an der Bohrung 65 zugeführt. Dieses wird durch die rotierenden Zahnräder entlang dem Umfang der jetzt als Auslaß dienenden Bohrung 66 zugeführt. Das unter Hochdruck stehende Druckmittel dringt über einen etwa dreieckförmigen Zwickel 67, welcher zwischen dem Innenraum 13 des Gehäuses und den Lagerkörpern 16-19 gebildet ist und sich über die gesamte Höhe derselben erstreckt, in den Spaltraum ein, welcher zwischen den Lagerkörpern und den Deckeln gebildet ist. Dort baut sich nun auf der Hochdruckseite zwischen dem Stützring 46 und den Stirnseiten der Lagerkörper ein erstes Druckfeld 68', 68" und ein zweites Druckfeld auf, das exakt der gesamten Fläche des Stützrings 46 entspricht und unter diesem liegt - also zwischen den Nuten 39, 41 44 an den Lagerkörpern und dem Stützring 46 - welches Druckfeld ebenfalls vom Hochdruck beaufschlagt ist über die Nuten 42, 43 am Außenumfang der Lagerkörper. Die Stützringe 46 werden zusammen mit den Dichtungen 47 durch Flüssigkeitsdruck gegen die Deckel 11, 12 gepreßt.It is assumed that the gear machine works as a gear motor and high-pressure pressure medium is supplied to the bore 65. This is fed through the rotating gears along the circumference of the bore 66 now serving as an outlet. The high-pressure pressure medium penetrates through an approximately triangular gusset 67, which is formed between the interior 13 of the housing and the bearing bodies 16-19 and extends over the entire height thereof, into the gap which is formed between the bearing bodies and the covers is. There, a first pressure field 68 ′, 68 ″ and a second pressure field build up on the high-pressure side between the support ring 46 and the end faces of the bearing bodies, which corresponds exactly to the entire surface of the support ring 46 and lies below it - that is, between the grooves 39, 41 44 on the bearing bodies and the support ring 46 - which pressure field is also acted on by the high pressure via the grooves 42, 43 on the outer circumference of the bearing bodies 46. The support rings 46 together with the seals 47 are pressed against the covers 11, 12 by liquid pressure.

An den den Druckfeldern 68', 68" gegenüberliegenden dritten Druckfeldern 70', 70" herrscht der in der Auslaßbohrung 66 herrschende Druck, und zwar deshalb, da diese Felder über einen etwa dreieckförmigen Zwickel 72, der zwischen dem Innenraum 13 des Gehäuses und den Lagerkörpern liegt, Verbindung zur Bohrung 66 haben. Der Auslaßdruck kann sehr niedrig, aber auch hoch sein, falls an die Bohrung 66 ein zweiter Zahnradmotor angeschlossen ist.The pressure prevailing in the outlet bore 66 prevails at the third pressure fields 70 ′, 70 ″ opposite the pressure fields 68 ′, 68 ″, because these fields have an approximately triangular gusset 72 that lies between the interior 13 of the housing and the bearing bodies is connected to hole 66. The outlet pressure can be very low, but also high if a second gear motor is connected to the bore 66.

Vierte Druckfelder werden in den zwischen dem Stützring 46 und den Lagerbohrungen 20-23 gelegenen Ringräumen 74-75 gebildet. Diese sind stets von dem in den Bohrungen 33, 34 herrschenden Lecköldruck belastet, der maximal 5-8 bar betragen kann. Durch die beschriebenen vier Druckfelder werden die Lagerkörper 16-19 in dichtende Berührung mit den Zahnradseitenflächen gebracht. Die von den ringförmigen Druckfeldern 74, 75 zu kompensierende Kraft ergibt sich aus einer Fläche an der Zahnradstirnseite, die etwa zwischen dem Fußkreis der Zahnräder und dem Durchmesser der Bohrungen 20-23 liegt mal dem dort herrschenden Lecköldruck.Fourth pressure fields are formed in the annular spaces 74-75 located between the support ring 46 and the bearing bores 20-23. These are always loaded by the leakage oil pressure prevailing in the bores 33, 34, which can be a maximum of 5-8 bar. Due to the four pressure fields described, the bearing bodies 16-19 are brought into sealing contact with the gear side surfaces. The force to be compensated for by the annular pressure fields 74, 75 results from an area on the face of the gearwheel, which lies approximately between the root circle of the gearwheels and the diameter of the bores 20-23 times the leakage oil pressure prevailing there.

Die Zahnradmaschine ist reversierbar, d. h. der Hochdruck kann auch an der Bohrung 66 zugeführt werden, an der Bohrung 65 ist dann die Niederdruckseite. Die Hochdruckfelder bauen sich nun bei 70', 70" und wieder unter der Stützringfläche auf, die Niederdruckfelder sind bei 68', 68". Die Wirkung ist genau dieselbe wie oben beschrieben. Es ist selbstverständlich möglich, druckbeaufschlagte Lagerkörper nur auf einer Seite der Zahnräder anzuordnen, während die beiden anderen Lagerkörper nicht druckbeaufschlagt sind und starr am Deckel anliegen.The gear machine is reversible, i. H. the high pressure can also be supplied at the bore 66; the low pressure side is then at the bore 65. The high pressure fields now build up at 70 ', 70 "and again under the support ring surface, the low pressure fields are at 68', 68". The effect is exactly the same as described above. It is of course possible to arrange pressurized bearing bodies only on one side of the gearwheels, while the other two bearing bodies are not pressurized and rest rigidly on the cover.

Die Maschine kann im Vier-Qadrantenbetrieb eingesetzt werden, d. h. als Pumpe und Motor und beidseitig beaufschlagbar. Sehr wesentlich ist, daß die Maschine durch Rücklaufdruck belastbar (= betreibbar) ist, d. h. am Auslaß kann ebenfalls Druck herrschen, z. B. im Motorbetrieb, wenn an den Auslaß ein zweiter Zahnradmotor angeschlossen ist, dem der Restdruck zur Verfügung steht.The machine can be used in four-quadrant mode, i. H. as a pump and motor and can be loaded on both sides. It is very important that the machine can be loaded (= operable) by the return pressure. H. there may also be pressure at the outlet, e.g. B. in motor operation, when a second gear motor is connected to the outlet, to which the residual pressure is available.

Das Schema nach Figur 12 zeigt nochmals deutlich die Lage der vier Druckfelder, wobei 68', 68" und Stützringfläche 46 (alle kreuzschraffiert) vom selben Druck (Hochdruck) beaufschlagt sind, die Flächen 70', 70" vom Rücklaufdruck (rechtslaufend schraffiert) und die Ringflächen (linkslaufend schraffiert) vom Lecköldruck.The diagram according to FIG. 12 again clearly shows the position of the four pressure fields, the 68 ', 68 "and the support ring surface 46 (all cross-hatched) being acted upon by the same pressure (high pressure), the surfaces 70', 70" by the return pressure (hatched in the right direction) and the ring surfaces (shaded to the left) from the leakage oil pressure.

Claims (1)

  1. Reversible gear machine (pump or motor) with externally meshing gearwheels, on the end faces of which, at least on one side, rests an axially movable sealing plate, on the side of which facing away from the end faces of the gearwheels are formed pressure zones which are limited and separated by a gasket arranged in a groove and are located between the sealing plate and the housing wall and of which one is subjected to pressure from the inflow side and the other from the return side, the gasket (46-50) having essentially the form of spectacles and possessing sheet-like extensions (49, 50 ; 60, 61) which are arranged on its two diametrically opposite outer faces and which reach to the inner wall (13) of the housing (10), whilst the other regions (46, 51) of the gasket are at a distance from the housing wall, and between the inside of the gasket and bores (20-23) receiving the gearwheel shafts (24-28) are formed two relatively narrow annular self- contained zones (74, 75) subjected to a pressure such as prevails in a region on the gearwheel end faces which is located approximately between the root circle and the diameter of the bores (20-23) receiving the gearwheels, characterized by the combination of the following features :
    a) The sealing plate consists of two mutually touching bush-shaped bearing bodies (16-19) which receive the gearwheel shafts and in which grooves (39, 41, 44) for receiving the gasket are formed,
    b) The sheet-like extensions of the outer faces of the gasket have a shape approximately in the form of a sector of a circle,
    c) The gasket consists of two parts, namely an axially outer supporting ring (46) made of plastic and an inner sealing body (47) made of rubber, both being connected positively to one another, and
    d) The supporting ring (46) has a U-shaped crosssection, and the sealing body (47) has a projecting web (56) which faces the bearing body and rests against the groove bottom (39') and which forms two pressure spaces (57, 58).
EP83103941A 1982-05-12 1983-04-22 Reversible gear machine (motor or pump) Expired EP0093917B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3217753 1982-05-12
DE19823217753 DE3217753A1 (en) 1982-05-12 1982-05-12 REVERSIBLE GEAR MACHINE (PUMP OR MOTOR)

Publications (2)

Publication Number Publication Date
EP0093917A1 EP0093917A1 (en) 1983-11-16
EP0093917B1 true EP0093917B1 (en) 1987-07-08

Family

ID=6163311

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83103941A Expired EP0093917B1 (en) 1982-05-12 1983-04-22 Reversible gear machine (motor or pump)

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US (1) US4465444A (en)
EP (1) EP0093917B1 (en)
BR (1) BR8302454A (en)
DE (2) DE3217753A1 (en)

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US4636155A (en) * 1984-06-29 1987-01-13 Commercial Shearing, Inc. Hydraulic seal having U-shaped gasket and a plurality of plastically deformable posts
FR2585083B1 (en) * 1985-07-16 1989-09-01 Hydroperfect Internal Hpi PURE HYDRAULIC ACTION DEVICE FOR HYDROSTATIC COMPENSATION OF GEAR TYPE HYDRAULIC PUMPS AND MOTORS
DE3766245D1 (en) * 1987-04-24 1990-12-20 Vickers Systems Gmbh GEAR PUMP OR MOTOR FOR FLUIDE.
DE8707256U1 (en) * 1987-05-20 1988-09-22 Robert Bosch Gmbh, 7000 Stuttgart Gear machine (pump or motor)
DE3863235D1 (en) * 1987-05-30 1991-07-18 Bosch Gmbh Robert REVERSIBLE GEAR MACHINE (PUMP OR MOTOR).
IT1220330B (en) * 1988-04-08 1990-06-15 Sauer Sundstrand Spa GEAR MACHINE OPERATING AS A PUMP OR MOTOR
US4927343A (en) * 1988-10-06 1990-05-22 Permco, Inc. Lubrication of gear pump trunnions
US6979185B2 (en) * 2000-08-01 2005-12-27 Kaempe Staffan I Bi-rotational pump/hydraulic actuator
JP2005163676A (en) * 2003-12-03 2005-06-23 Seiko Epson Corp Gear pump and liquid injection device
CN102465870B (en) * 2010-11-08 2014-12-17 西安航空动力控制科技有限公司 Planetary gear pump with axial sealing compensation
RU2477388C2 (en) * 2010-12-21 2013-03-10 Государственное образовательное учреждение высшего профессионального образования "Братский государственный университет" Gear pump
US11624361B1 (en) 2022-02-16 2023-04-11 Caterpillar Inc. Anchored low pressure gear pump wear plate

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US3270680A (en) * 1964-12-17 1966-09-06 Kingston Products Corp Pressure loaded gear pump
US3292551A (en) * 1965-04-26 1966-12-20 Clark Equipment Co Gear pump or motor
US3348492A (en) * 1966-12-05 1967-10-24 Borg Warner Reversible wear plate pump
US3473476A (en) * 1967-11-13 1969-10-21 Lear Siegler Inc Gear pump seal
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Also Published As

Publication number Publication date
DE3217753A1 (en) 1983-11-17
BR8302454A (en) 1984-01-17
US4465444A (en) 1984-08-14
EP0093917A1 (en) 1983-11-16
DE3372395D1 (en) 1987-08-13

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