EP0293585B1 - Reversible gear machine (pump or motor) - Google Patents

Reversible gear machine (pump or motor) Download PDF

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Publication number
EP0293585B1
EP0293585B1 EP19880106171 EP88106171A EP0293585B1 EP 0293585 B1 EP0293585 B1 EP 0293585B1 EP 19880106171 EP19880106171 EP 19880106171 EP 88106171 A EP88106171 A EP 88106171A EP 0293585 B1 EP0293585 B1 EP 0293585B1
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EP
European Patent Office
Prior art keywords
pressure
bores
sealing
rings
machine
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP19880106171
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German (de)
French (fr)
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EP0293585A1 (en
Inventor
Hayno Dipl.-Ing. Rustige
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Publication of EP0293585A1 publication Critical patent/EP0293585A1/en
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Publication of EP0293585B1 publication Critical patent/EP0293585B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/06—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for stopping, starting, idling or no-load operation
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2225/00—Synthetic polymers, e.g. plastics; Rubber
    • F05C2225/04—PTFE [PolyTetraFluorEthylene]

Definitions

  • the invention relates to a gear machine according to the preamble of the main claim.
  • a gear machine has become known from DD-B 157 874.
  • this known machine there are two control valves in connection channels from the high or low pressure side to the pressure fields and to a leakage oil chamber, which have the task of the pressure fields with the high pressure side and to connect a leakage oil duct to the low pressure side.
  • Such a gear machine has the disadvantage that it requires two control valves, which requires a considerable installation space and also causes high costs.
  • a gear machine has also become known from DE-A 2 403 319, which shows similar pressure fields and which is also suitable for so-called reversing operation, i.e. Operation in both directions of rotation is suitable.
  • this machine there is at least one seal to delimit them on each side of the gearwheels between the pressure spaces of the pressure fields and the bearing bodies, the seals being designed so that they have a U-shaped cross section, with the base side facing the sealing plate, and that a support body is provided within this seal.
  • Such a machine has the disadvantage that the pressure fields cannot be applied arbitrarily, but are tied to the pressure conditions in the machine.
  • the gear machine according to the invention with the characterizing features of the main claim has the advantage that the application of at least two pressure fields can be controlled by only one valve, as a result of which the operating behavior of the machine is very adaptable and the design effort is kept within reasonable limits.
  • FIG. 1 shows a longitudinal section through a gear motor, in FIG. 2 a cross section along II-II according to FIG. 1, FIG. 3 a cross section along III-III according to FIG. 2, FIG. 4 a detail.
  • the gear motor has a housing 10, the interior 11 of which is closed by two covers 12, 13. In the interior, two gears 14, 15 mesh with each other in external engagement, the shafts 16, 17 of which are mounted in bush-shaped or spectacle-shaped bearing bodies 18, 19, which are slightly axially and radially displaceable in the housing.
  • the shaft 17 has an extension 23 which penetrates to the outside through a bore in the cover 13 and is sealed there by a sealing ring 24.
  • a sealing plate 26 is arranged between the bearing body 18 and the gearwheel side surfaces, on the side facing away from the gearwheels pressure fields are formed, as are clearly shown in particular in FIG. 2.
  • the pressure fields AD are delimited by a seal 27, which is arranged in a suitable groove in the end face of the bearing body 18.
  • the seal consists of two concentrically extending, approximately glasses-shaped rings 28, 29, the inner rings 29 being connected to one another by a web 30 which runs in the imaginary axial direction of the center of the gear shaft.
  • the inner and outer rings are also connected to each other by webs 31, 32 which extend approximately radially outward from the inner rings, approximately at right angles to the web 30, their axial direction also referring to the center of the gear shaft.
  • the diameter of the outer rings 28 extends to the edge of the interior 11 or to the edge of the sealing plate 26, while the inner rings 29 are at a short distance from the shaft bores.
  • a bore 40, 41 also penetrates into the external pressure fields C and D, which likewise penetrate through the sealing plate and are connected to bores 42, 44 or 43, 45 in the bearing body 18 or cover 12, which run in the same axis. There they have connections to a line 46 to which a pressure valve 47 is connected, advantageously an electromagnetically actuated proportional valve, with which the pressure in the pressure fields C and D is controlled.
  • the bores 40, 41 are designed as throttle bores.
  • the seal 27 is shown in more detail. It is formed in two parts and consists of a support body 27A with a U-shaped cross section, the underside of which rests on the sealing plate 26.
  • the support body consists of a plastic, for example PTFE.
  • a soft, rubber-like seal 27B which has a cross-sectional shape shown in FIG. 3, is inserted into the support body.
  • the seal 27 is arranged in a correspondingly shaped groove 48 in the bearing body 18.
  • the sealing body 27B has two longitudinal grooves 27C, 27D on its part lying on the rounded groove base.
  • a circumferential groove 49 runs around the bearing body at a small distance from the groove 48.
  • the throttle bores 40, 41 ensure that only a small pressure medium flow is branched off from the gear machine.
  • a sealing plate 26 with corresponding pressure fields can also be arranged on the other side of the gear wheel. However, this is not absolutely necessary.
  • the gear machine can be operated both as a hydraulic motor and as a gear pump. It is reversible; if high pressure fluid is supplied to the bore 51, then the field B is pressurized and the field A is pressurized.
  • the groove 49 prevents pressure medium under high pressure from leaking along the outside of the bearing body toward the covers. As a result, the interior of the housing remains largely relieved of pressure.

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

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Zahnradmaschine nach der Gattung des Hauptanspruchs. Eine derartige Zahnradmaschine ist bekanntgeworden aus der DD-B 157 874. Bei dieser bekannten Maschine befinden sich in Verbindungskanälen von der Hoch- bzw. Niederdruckseite zu den Druckfeldern und zu einem Leckölraum zwei Steuerventile, welche die Aufgabe haben, die Druckfelder jeweils mit der Hochdruckseite und einen Leckölkanal jeweils mit der Niederdruckseite zu verbinden. Eine derartige Zahnradmaschine hat den Nachteil, daß sie zwei Steuerventile benötigt, was einen erheblichen Einbauraum bedingt und außerdem hohe Kosten verursacht.The invention relates to a gear machine according to the preamble of the main claim. Such a gear machine has become known from DD-B 157 874. In this known machine there are two control valves in connection channels from the high or low pressure side to the pressure fields and to a leakage oil chamber, which have the task of the pressure fields with the high pressure side and to connect a leakage oil duct to the low pressure side. Such a gear machine has the disadvantage that it requires two control valves, which requires a considerable installation space and also causes high costs.

Es ist weiterhin eine Zahnradmaschine aus der DE-A 2 403 319 bekanntgeworden, die ähnliche Druckfelder zeigt und die ebenfalls für sogenannten Reversierbetrieb, d.h. Betrieb in beiden Drehrichtungen geeignet ist. Bei dieser Maschine befindet sich auf jeder Seite der Zahnräder zwischen den Druckräumen der Druckfelder und den Lagerkörpern mindestens eine Dichtung zum Abgrenzen derselben, wobei die Dichtungen so ausgebildet sind, daß sie einen U-förmigen Querschnitt besitzen, wobei die Basisseite der Dichtplatte zugewandt ist, und daß innerhalb dieser Dichtung noch ein Stützkörper vorgesehen ist. Eine derartige Maschine hat den Nachteil, daß die Beaufschlagung der Druckfelder nicht willkürlich erfolgen kann, sondern an die Druckverhältnisse in der Maschine gebunden sind.A gear machine has also become known from DE-A 2 403 319, which shows similar pressure fields and which is also suitable for so-called reversing operation, i.e. Operation in both directions of rotation is suitable. In this machine, there is at least one seal to delimit them on each side of the gearwheels between the pressure spaces of the pressure fields and the bearing bodies, the seals being designed so that they have a U-shaped cross section, with the base side facing the sealing plate, and that a support body is provided within this seal. Such a machine has the disadvantage that the pressure fields cannot be applied arbitrarily, but are tied to the pressure conditions in the machine.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Zahnradmaschine mit den kennzeichnenden Merkmalen des Hauptanspruchs hat den Vorteil, daß die Beaufschlagung mindestens zweier Druckfelder durch nur ein Ventil steuerbar ist, wodurch das Betriebsverhalten der Maschine sehr anpassungsfähig ist und wobei der konstruktive Aufwand sich in vertretbaren Grenzen hält.The gear machine according to the invention with the characterizing features of the main claim has the advantage that the application of at least two pressure fields can be controlled by only one valve, as a result of which the operating behavior of the machine is very adaptable and the design effort is kept within reasonable limits.

(Fortsetzung ursprüngliche Seite 2 "Zeichnung")(Continued from original page 2 "Drawing") Zeichnungdrawing

Ein Ausführungsbeispiel der Erfindung ist in der nachfolgenden Beschreibung und Zeichnung wiedergegeben. Diese zeigt in Figur 1 einen Längsschnitt durch einen Zahnradmotor, in Figur 2 einen Querschnitt längs II-II nach Figur 1, Figur 3 einen Querschnitt längs III-III nach Figur 2, Figur 4 eine Einzelheit.An embodiment of the invention is shown in the following description and drawing. 1 shows a longitudinal section through a gear motor, in FIG. 2 a cross section along II-II according to FIG. 1, FIG. 3 a cross section along III-III according to FIG. 2, FIG. 4 a detail.

Beschreibung des AusführungsbeispielsDescription of the embodiment

Der Zahnradmotor weist ein Gehäuse 10 auf, dessen Innenraum 11 durch zwei Deckel 12, 13 verschlossen ist. Im Innenraum kämmen zwei Zahnräder 14, 15 im Außeneingriff miteinander, deren Wellen 16, 17 in buchsen- oder brillenförmigen Lagerkörpern 18, 19 gelagert sind, die axial und radial geringfügig im Gehäuse verschiebbar sind. Die Welle 17 hat einen Fortsatz 23, der durch eine Bohrung im Deckel 13 nach außen dringt und dort durch einen Dichtring 24 abgedichtet ist.The gear motor has a housing 10, the interior 11 of which is closed by two covers 12, 13. In the interior, two gears 14, 15 mesh with each other in external engagement, the shafts 16, 17 of which are mounted in bush-shaped or spectacle-shaped bearing bodies 18, 19, which are slightly axially and radially displaceable in the housing. The shaft 17 has an extension 23 which penetrates to the outside through a bore in the cover 13 and is sealed there by a sealing ring 24.

Zwischen dem Lagerkörper 18 und den Zahnradseitenflächen ist eine Dichtplatte 26 angeordnet, an deren den Zahnrädern abgewandten Seite Druckfelder ausgebildet sind, wie sie insbesondere in Figur 2 deutlich erkennbar dargestellt sind. Die Druckfelder A-D sind begrenzt durch eine Dichtung 27, die in einer passenden Nut in der Stirnfläche des Lagerkörpers 18 angeordnet ist. Wie insbesondere Figur 2 zeigt, besteht die Dichtung aus zwei konzentrisch verlaufenden, etwa brillenförmigen Ringen 28, 29, wobei die innenliegenden Ringe 29 durch einen Steg 30 miteinander verbunden sind, welcher in der gedachten Achsrichtung der Mitte der Zahnradwellen verläuft. Die inneren und äußeren Ringe sind außerdem jeweils durch Stege 31, 32 miteinander verbunden, die etwa radial von den inneren Ringen nach außen verlaufen, etwa rechtwinklig zum Steg 30, wobei sich ihre Achsrichtung ebenfalls auf die Mitte der Zahnradwellen bezieht. Der Durchmesser der äußeren Ringe 28 reicht bis zum Rand des Innenraums 11 bzw. bis zum Rand der Dichtplatte 26, während die inneren Ringe 29 einen geringen Abstand zu den Wellenbohrungen haben.A sealing plate 26 is arranged between the bearing body 18 and the gearwheel side surfaces, on the side facing away from the gearwheels pressure fields are formed, as are clearly shown in particular in FIG. 2. The pressure fields AD are delimited by a seal 27, which is arranged in a suitable groove in the end face of the bearing body 18. As particularly shown in Figure 2, the seal consists of two concentrically extending, approximately glasses-shaped rings 28, 29, the inner rings 29 being connected to one another by a web 30 which runs in the imaginary axial direction of the center of the gear shaft. The inner and outer rings are also connected to each other by webs 31, 32 which extend approximately radially outward from the inner rings, approximately at right angles to the web 30, their axial direction also referring to the center of the gear shaft. The The diameter of the outer rings 28 extends to the edge of the interior 11 or to the edge of the sealing plate 26, while the inner rings 29 are at a short distance from the shaft bores.

Auf diese Weise entstehen zweinebeneinanderliegende Druckfelder A und B beidseitig des Stegs 30 und zwei einander diametral gegenüberliegende Druckfelder C und D, die _ bezogen auf die Längsausdehnung der Dichtung 28 _ außen liegen. In die Druckfelder A und B dringt je eine Bohrung 34, 35 ein, die durch die Dichtplatte hindurchgehen und an den darunterliegenden Zahnlücken münden. In den Innenraum dringen, in Höhe der Zahnräder 14, 15 von außen her und achsgleich verlaufend zwei Bohrungen 50, 51 ein, welche der Druckmittelzu- bzw. abfuhr dienen.In this way, two mutually adjacent pressure fields A and B arise on both sides of the web 30 and two diametrically opposed pressure fields C and D, which, based on the longitudinal extent of the seal 28, lie on the outside. A bore 34, 35 penetrates into the pressure fields A and B, which pass through the sealing plate and open at the tooth gaps underneath. Penetrate into the interior, at the level of the gearwheels 14, 15 from the outside and running in the same axis, two bores 50, 51, which serve to supply or discharge the pressure medium.

In die äußeren Druckfelder C und D dringt ebenfalls je eine Bohrung 40, 41 ein, die ebenfalls durch die Dichtplatte dringen und mit achsgleich verlaufenden Bohrungen 42, 44 bzw. 43, 45 im Lagerkörper 18 bzw. Deckel 12 verbunden sind. Dort haben sie Verbindungen mit einer Leitung 46 an die ein Druckventil 47 angeschlossen ist, zweckmäßigerweise ein elektromagnetisch betätigbares Proportionalventil, mit dem der Druck in den Druckfeldern C und D gesteuert wird. Die Bohrungen 40, 41 sind als Drosselbohrungen ausgebildet.A bore 40, 41 also penetrates into the external pressure fields C and D, which likewise penetrate through the sealing plate and are connected to bores 42, 44 or 43, 45 in the bearing body 18 or cover 12, which run in the same axis. There they have connections to a line 46 to which a pressure valve 47 is connected, advantageously an electromagnetically actuated proportional valve, with which the pressure in the pressure fields C and D is controlled. The bores 40, 41 are designed as throttle bores.

Im Schnitt nach Figur 4 ist die Dichtung 27 näher dargestellt. Sie ist zweiteilig ausgebildet und besteht aus einem Stützkörper 27A mit U-förmigem Querschnitt, dessen Unterseite an der Dichtplatte 26 anliegt. Der Stützkörper besteht aus einem Kunststoff, z.B. PTFE. In den Stützkörper ist eine weiche, gummiartige Dichtung 27B eingelegt, die eine in der Figur 3 dargestellte Querschnittsform aufweist. Die Dichtung 27 ist in einer entsprechend geformte Nut 48 im Lagerkörper 18 angeordnet. Der Dichtkörper 27B hat an seinem am abgerundeten Nutgrund liegenden Teil zwei längsverlaufende Nuten 27C, 27D. Um den Lagerkörper herum verläuft in geringem Abstand zur Nut 48 eine umlaufende Nut 49.In the section of Figure 4, the seal 27 is shown in more detail. It is formed in two parts and consists of a support body 27A with a U-shaped cross section, the underside of which rests on the sealing plate 26. The support body consists of a plastic, for example PTFE. A soft, rubber-like seal 27B, which has a cross-sectional shape shown in FIG. 3, is inserted into the support body. The seal 27 is arranged in a correspondingly shaped groove 48 in the bearing body 18. The sealing body 27B has two longitudinal grooves 27C, 27D on its part lying on the rounded groove base. A circumferential groove 49 runs around the bearing body at a small distance from the groove 48.

Es sei angenommen, daß an der Bohrung 50 unter Hochdruck stehendes Druckmittel zugeführt wird. Dieses treibt nun die Zahnräder an, so daß an der Welle 23 ein Drehmoment abgenommen werden kann. Das Druckmittel verläßt die Bohrung 51 an der Niederdruckseite. In den Druckfeldern A und B herrscht nun über die Bohrungen 34 und 35 der Einlaß- bzw. der Auslaßdruck. Das Druckventil 47 ist geöffnet, so daß in denDruckfeldern C und D kein Druck herrscht. Dies deshalb, damit die Dichtplatte nicht zu stark an die Zahnradseitenflächen angedrückt wird. Dadurch bleiben die Reibungskräfte gering, und der Zahnradmotor kann gut anfahren. Nach dem Anfahren des Zahnradmotors werden die Druckfelder C und D durch zunehmendes Schließen des Schaltventils mit höherem Druck beaufschlagt, so daß die Dichtplatte 26 stärker an die Zahnradseitenflächen gedrückt wird. Damit erreicht man, daß entlang der Zahnradseitenflächen nun kein Druckmittel mehr von der Hochdruck- zur Niederdruckseite strömen kann, so daß der Wirkungsgrad des Zahnradmotors entsprechend hoch bleibt. Die Drosselbohrungen 40, 41 sorgen dafür, daß nur ein geringer Druckmittelstrom aus der Zahnradmaschine abgezweigt wird.It is assumed that high pressure pressure medium is supplied to the bore 50. This now drives the gears so that a torque can be taken from the shaft 23. The pressure medium leaves the bore 51 on the low pressure side. In the pressure fields A and B, the inlet and outlet pressures now prevail through the bores 34 and 35. The pressure valve 47 is open so that there is no pressure in the pressure fields C and D. This is so that the sealing plate is not pressed too hard on the gear side surfaces. This keeps the frictional forces low and the gear motor can start up well. After starting the gear motor, the pressure fields C and D are acted upon by increasing closing of the switching valve with higher pressure, so that the sealing plate 26 is pressed more strongly against the gear side surfaces. This ensures that no more pressure medium can now flow from the high-pressure to the low-pressure side along the gear side surfaces, so that the efficiency of the gear motor remains correspondingly high. The throttle bores 40, 41 ensure that only a small pressure medium flow is branched off from the gear machine.

Es sei noch bemerkt, daß auch an der anderen Zahnradseitenfläche eine Dichtplatte 26 mit entsprechenden Druckfeldern angeordnet werden kann. Dies ist jedoch nicht unbedingt notwendig.It should also be noted that a sealing plate 26 with corresponding pressure fields can also be arranged on the other side of the gear wheel. However, this is not absolutely necessary.

Selbstverständlich kann die Zahnradmaschine sowohl als Hydromotor wie auch als Zahnradpumpe betrieben werden. Sie ist reversierbar; wenn unter Hochdruck stehendes Druckmittel an der Bohrung 51 zugeführt wird, dann ist das Feld B mit Hochdruck beaufschlagt und das Feld A mit Niederdruck.Of course, the gear machine can be operated both as a hydraulic motor and as a gear pump. It is reversible; if high pressure fluid is supplied to the bore 51, then the field B is pressurized and the field A is pressurized.

Durch die Nut 49 wird verhindert, daß unter Hochdruck stehendes Druckmittel entlang der Außenseite der Lagerkörper zu den Deckeln hin durchlecken kann. Dadurch bleibt das Gehäuseinnere weitgehend druckentlastet.The groove 49 prevents pressure medium under high pressure from leaking along the outside of the bearing body toward the covers. As a result, the interior of the housing remains largely relieved of pressure.

Claims (4)

1. Reversible gear machine (pump or motor) having two externally meshing gears (14, 15) and a sealing plate (26) which is arranged at least on one of their side faces and is loaded by pressure zones (A to D) which are formed on its side remote from the gears and are defined by a sealing arrangement (27) which consists of two concentrically running rings (28, 29) which are designed roughly in a spectacle shape and are connected to one another by webs and of which the outer rings run along the inner wall of the housing and the inner rings run close to the gear shafts, and in which arrangement the two inner rings (29), on an imaginary straight connecting line running through the centres of the gear shafts are connected by a first web (30), that [sic], in addition, in each case two webs (31, 32), running radially and roughly perpendicularly to the first web in opposite directions, lead off from the inner rings and are connected to the outer rings, which results in two diametrically opposite pressure zones (C, D) which are loaded by a pressure via bores (40, 41) leading into the same, which pressure is controlled by a pressure valve (46), and the two pressure zones (A, B) formed between the roughly radially running webs (31, 32) and the first web (30) are connected to the respective inlet and outlet (50, 51) via bores (34, 35) penetrating through the sealing plate (26), characterised in that the pressure medium for loading the pressure zones (C and D) is removed from the pressure space of the machine, namely via restrictor bores (40, 41) which are connected to the pressure valve (47) via bores (43, 45) penetrating through the bearing bodies, the pressure zones (C, D) and a housing cap (12), to which pressure valve (47) a vessel is connected.
2. Machine according to a [sic] Claim 1, characterised in that the bores (40, 41) leading into the pressure zones (C, D) are designed as restrictor bores.
3. Machine according to Claims 1 and 2, characterised in that the sealing arrangement is of two-piece design and consists of a plastic supporting ring (27A), which bears directly against the sealing plate (26), and a sealing body (27B) which is inserted into the supporting ring and is made of a softer material, and in that the sealing arrangement (27) is located in a groove (48) formed in the end face of the bearing body.
4. Machine according to one of Claims 1 to 3, characterised in that a small encircling groove (49) is formed at a slight distance from the sealing arrangement (27) on the outer periphery of the bearing bodies.
EP19880106171 1987-05-30 1988-04-19 Reversible gear machine (pump or motor) Expired - Lifetime EP0293585B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3718229 1987-05-30
DE3718229 1987-05-30

Publications (2)

Publication Number Publication Date
EP0293585A1 EP0293585A1 (en) 1988-12-07
EP0293585B1 true EP0293585B1 (en) 1991-06-12

Family

ID=6328748

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19880106171 Expired - Lifetime EP0293585B1 (en) 1987-05-30 1988-04-19 Reversible gear machine (pump or motor)

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EP (1) EP0293585B1 (en)
DE (1) DE3863235D1 (en)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3902139A1 (en) * 1989-01-25 1990-07-26 Bosch Gmbh Robert HYDROSTATIC DRIVE
GB2233712A (en) * 1989-07-13 1991-01-16 Dowty Hydraulic Units Ltd Rotary positive displacement hydraulic machines
DE3925269A1 (en) * 1989-07-31 1991-02-07 Vickers Systems Gmbh AXIAL SEAL
IT1241224B (en) * 1990-05-11 1993-12-29 Maspe Srl CALCULATING MACHINE FOR FLUID STATE FOOD PRODUCTS
EP0563661A1 (en) * 1992-03-19 1993-10-06 J.M. Voith GmbH Internal gear pump with radially movable sealing elements for radial compensation
DE10104621B4 (en) * 2001-02-02 2014-07-24 Robert Bosch Gmbh Axial field sealing of a gear machine
GR1009196B (en) * 2016-08-31 2018-01-11 Αθανασιος Νικολαου Κοτουπας New-type gear system

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3174435A (en) * 1962-08-16 1965-03-23 Clark Equipment Co Pump or motor
US3499390A (en) * 1968-04-11 1970-03-10 Parker Hannifin Corp Rotary pump
DE2403319A1 (en) * 1974-01-24 1975-07-31 Bosch Gmbh Robert GEAR MACHINE
DE3217753A1 (en) * 1982-05-12 1983-11-17 Robert Bosch Gmbh, 7000 Stuttgart REVERSIBLE GEAR MACHINE (PUMP OR MOTOR)

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Publication number Publication date
DE3863235D1 (en) 1991-07-18
EP0293585A1 (en) 1988-12-07

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