EP0291703B1 - Gear machine (pump or motor) - Google Patents

Gear machine (pump or motor) Download PDF

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Publication number
EP0291703B1
EP0291703B1 EP19880106170 EP88106170A EP0291703B1 EP 0291703 B1 EP0291703 B1 EP 0291703B1 EP 19880106170 EP19880106170 EP 19880106170 EP 88106170 A EP88106170 A EP 88106170A EP 0291703 B1 EP0291703 B1 EP 0291703B1
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EP
European Patent Office
Prior art keywords
pressure
machine according
fields
sealing
seal
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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
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EP19880106170
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German (de)
French (fr)
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EP0291703A1 (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 of EP0291703A1 publication Critical patent/EP0291703A1/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 according to the preamble of the main claim.
  • a gear machine is described in DE-C 925 752.
  • two pressure fields acting on sealing plates are provided, one of which is acted upon by the high pressure side of the machine and the other by the low pressure side. These pressure fields are limited by suitable seals.
  • Such a gear machine is not yet optimally designed, since no intermediate pressures can be generated in the pressure fields.
  • the gear machine according to the invention with the characterizing features of the main claim has the advantage that the design of the pressure fields is perfected so that the hydraulic forces necessary for the current operation are always exerted on the sealing plate. This improves the life, noise and operating behavior of the gear machine. In particular, the internal housing forces are also reduced.
  • FIG. 1 An embodiment of the invention is shown in the following description and drawing.
  • the latter shows in Figure 1 a longitudinal section through a gear motor, in Figure 2 a section along II-II of Figure 1, in Figure 3 a section along III-III of Figure 2, in Figure 4 a detail.
  • the gear motor has a housing 10, the interior 11 of which is sealed on both sides by covers 12, 13. In the interior 11, two gears 14, 15 mesh with one another in external engagement, the shafts 16, 17 of which are mounted in bushings or glasses-shaped bearing bodies. That bearing body for the shaft journal 16 is designated by 18, that for the shaft journal 17 by 19.
  • the shaft journal 17 has an outwardly penetrating extension 23 which penetrates through a bore in the cover, in which a seal 24 is arranged.
  • a sealing plate 26 is arranged between the bearing body 18 and the gearwheel side surfaces. Hydraulically acted upon pressure fields are formed between this and the bearing bodies 18, which are delimited by a seal 27, as is shown in particular in FIGS. 2 and 3, which is arranged in corresponding grooves of the bearing body 18.
  • the seal 27 is formed in two parts, namely from a support body 27A made of a somewhat harder plastic than the sealing body 27B, which consists of a rubber-elastic material.
  • the supporting body 27A has the shape of a U in cross section, into which the lower part of the sealing body 27B is pressed.
  • the seal 27 is arranged in a corresponding groove 28, which is located in the end face of the bearing body 18.
  • the shape of the seal 27 or the groove 28 is again referred to in FIGS. 2 and 3, the sealing body 27B being shown in FIG. 2, since the support body 27A is underneath.
  • the seal has the shape of a pair of glasses and consists of two concentric arcs 30, 31 which are connected to one another by webs 32 to 34 which lie in the same imaginary straight line, namely in a straight line which the two bores receiving the gear shaft connects.
  • the seal also has circular recesses 36, 37 through which the shaft journals of the gearwheels penetrate.
  • the outer circumference of the seal 27 extends to the inner wall of the housing.
  • the shape of the seal results in two double-arch-shaped recesses 38, 39 which are opposite each other in mirror image, with a bore 40, 41 penetrating each of these, which run through the bearing bodies 18, 19.
  • channels 42, 43 which are formed in the cover and have the connection to a line 44 which are connected to a pressure medium source 46 via a proportional control valve 45.
  • a proportional control valve 45 Via this latter device, either the recess 38 or 39 can be pressurized or relieved, depending on the direction of rotation of the hydraulic motor; this creates the pressure fields mentioned at the beginning.
  • Two bores 50, 51 penetrate into the interior 11 from opposite sides and extend in the same axis and serve to supply or discharge the pressure medium.
  • the gear machine is operated as a motor and, for example, pressure medium under high pressure flows through the bore 50, the pressure fields 38 and 31 are relieved via the control valve 45 and the corresponding channels, so that the sealing plate 26 only has a very slight excess force on the gear side surfaces is pressed so that the frictional force remains low.
  • the gear motor can now start easily. If it has reached its rotational speed, pressure medium under pressure is fed into the field 38 by appropriate adjustment of the valve 45 (switch position I), so that the sealing plate 26 is now pressed more strongly onto the gear side surfaces is, whereby the leakage losses along the gear side surfaces are significantly reduced.
  • the field 39 is then relieved of pressure via the bore 41 (valve in position III). If the hydraulic motor is reversed, ie if pressure medium under high pressure is supplied via the bore 51, then both fields 38, 31 are relieved, but after the motor has started up fully, pressure medium under high pressure is again applied.
  • a circumferential groove 52 with a small cross-section extends around the bearing body at a short distance from the seal 27, via which pressure medium leaking through the seal is collected.
  • the type of seal and the groove 52 prevent the pressure medium from leaking from the high-pressure side along the bearing body in the direction of the cover, so that the internal load on the housing is thereby substantially reduced. If this were not the case, pressure medium could leak from the high-pressure side along the bearing body towards the cover and exert a relatively large force on the housing, which has very negative consequences.
  • sealing plates 26 and also corresponding seals can be arranged on both sides of the gears and in the bearing bodies 19, 20. Such an arrangement is probably more expensive, but brings with it a further improvement in function.
  • the exact cross-sectional shape of the sealing body 27B can best be seen in FIG. 3. This shape results in flow channels 27C, 27D at the bottom of the groove, which has proven to be very expedient, since this acts on the seal from behind and presses the support body 27A particularly well against the sealing plate.
  • the gear machine can of course also be operated as a pump.
  • the action on the pressure fields 38, 39 can then be simplified considerably in that their action is carried out simply through bores penetrating the sealing plate. Pump 46, control valve 45 and the corresponding channels are omitted.

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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 bekannte Zahnradmaschine ist in der DE-C 925 752 beschrieben. Bei dieser bekannten Zahnradmaschine sind zwei auf Dichtplatten einwirkende Druckfelder vorgesehen, von denen das eine von der Hochdruckseite der Maschine beaufschlagt ist, das andere von der Niederdruckseite. Diese Druckfelder sind durch passende Dichtungen begrenzt. Eine derartige Zahnradmaschine ist noch nicht optimal ausgelegt, da keine Zwischendrücke in den Druckfeldern erzeugt werden können.The invention relates to a gear machine according to the preamble of the main claim. Such a known gear machine is described in DE-C 925 752. In this known gear machine, two pressure fields acting on sealing plates are provided, one of which is acted upon by the high pressure side of the machine and the other by the low pressure side. These pressure fields are limited by suitable seals. Such a gear machine is not yet optimally designed, since no intermediate pressures can be generated in the pressure fields.

Aus der US-A 3 174 435 ist weiterhin eine Zahnradmaschine bekanntgeworden, bei der an den Seitenflächen der Zahnräder Dichtplatten anliegen, die unter Flüssigkeitskraft stehen, welche in Druckfeldern gebildet ist. Diese Druckfelder, die alle gegeneinander durch Stege abgegrenzt sind, erstrecken sich entlang des Außenumfangs der Zahnräder und sind vom jeweiligen Druck der darunterliegenden Zahnkammern beaufschlagt. Auf diese Weise erhält man eine von der Niederdruck- zur Hochdruckseite sich stetig aufbauende Anpreßkraft auf die Dichtplatte. Die Konstruktion für die Schaffung der Dichtfelder ist verhältnismäßig aufwendig, da zwei Platten und eine entsprechende Dichtung verwendet werden müssen, außerdem sind die Druckfelder keiner individuellen Drucksteuerung unterziehbar.From US-A 3 174 435 a gear machine has also become known, in which sealing plates bear on the side surfaces of the gear wheels, which are under liquid force, which is formed in pressure fields. These pressure fields, which are all delimited from one another by webs, extend along the outer circumference of the toothed wheels and are acted upon by the respective pressure of the tooth chambers below. In this way one obtains a contact pressure which builds up continuously from the low pressure to the high pressure side on the sealing plate. The construction for the creation of the sealing fields is relatively complex, since two plates and a corresponding seal have to be used, and the pressure fields cannot be subjected to individual pressure control.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Zahnradmaschine mit den kennzeichnenden Merkmalen des Hauptanspruchs hat den Vorteil, daß die Auslegung der Druckfelder vervollkommnet ist, so daß auf die Dichtplatte stets die für den momentanen Betrieb notwendigen hydraulischen Kräfte ausgeübt werden. Dadurch werden die Lebensdauer, die Geräuschbildung und das Betriebsverhalten der Zahnradmaschine verbessert. Insbesondere werden auch die inneren Gehäusekräfte reduziert.The gear machine according to the invention with the characterizing features of the main claim has the advantage that the design of the pressure fields is perfected so that the hydraulic forces necessary for the current operation are always exerted on the sealing plate. This improves the life, noise and operating behavior of the gear machine. In particular, the internal housing forces are also reduced.

Zeichnungdrawing

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

Beschreibung des AusführungsbeispielsDescription of the embodiment

Der Zahnradmotor weist ein Gehäuse 10 auf, dessen Innenraum 11 beidseitig durch Deckel 12, 13 dicht verschlossen ist. Im Innenraum 11 kämmen zwei Zahnräder 14, 15 im Außeneingriff miteinander, deren Wellen 16, 17 in Buchsen oder brillenförmigen Lagerkörpern gelagert sind. Derjenige Lagerkörper für den Wellenzapfen 16 ist mit 18 bezeichnet, derjenige für den Wellenzapfen 17 mit 19. Der Wellenzapfen 17 hat einen nach außen dringenden Fortsatz 23, der durch eine Bohrung im Deckel dringt, in welcher eine Dichtung 24 angeordnet ist. Zwischen dem Lagerkörper 18 und den Zahnradseitenflächen ist eine Dichtplatte 26 angeordnet. Zwischen dieser und dem Lagerkörpern 18 sind hydraulisch beaufschlagte Druckfelder ausgebildet, die _ wie insbesondere in den Figuren 2 und 3 dargestellt ist _ durch eine Dichtung 27 begrenzt sind, die in entsprechenden Nuten des Lagerkörpers 18 angeordnet ist. Die Dichtung 27 ist zweiteilig ausgebildet, nämlich aus einem Stützkörper 27A aus einem etwas härteren Kunststoff als der Dichtkörper 27B, der aus einem gummielastischen Werkstoff besteht. Der Stützkörper 27A hat im Querschnitt die Form eines U, in welches der untere Teil des Dichtkörpers 27B eingedrückt ist. Die Dichtung 27 ist in einer entsprechenden Nut 28 angeordnet, welche sich in der Stirnseite des Lagerkörpers 18 befindet. Auf die Form der Dichtung 27 bzw. der Nut 28 wird wiederum auf die Figuren 2 und 3 verwiesen, wobei in Figur 2 der Dichtkörper 27B zu sehen ist, da der Stützkörper 27A darunterliegt. Die Dichtung hat von oben gesehen die Form einer Doppelbrille und besteht aus zwei konzentrischen Kreisbögen 30, 31, die durch Stege 32 bis 34 miteinander verbunden sind, welche in derselben gedachten Geraden liegen, und zwar in einer Geraden, welche die beiden die Zahnradwellen aufnehmenden Bohrungen verbindet. Dort hat die Dichtung auch kreisförmige Ausnehmungen 36, 37, durch welche die Wellenzapfen der Zahnräder hindurchdringen. Der Außenumfang der Dichtung 27 reicht bis an die Innenwand des Gehäuses. Wie aus Figur 2 zu erkennen ist, ergeben sich durch die Form der Dichtung zwei einander spiegelbildlich gegenüberliegende, doppelbogenförmige Aussparungen 38, 39, wobei in jede von diesen eine Bohrung 40, 41 eindringt, welche durch die Lagerkörper 18, 19 verlaufen. Sie stehen mit Kanälen 42, 43 in Verbindung, die im Deckel ausgebildet sind und die Anschluß haben zu einer Leitung 44, die über ein Proportional-Steuerventil 45 mit einer Druckmittelquelle 46 in Verbindung stehen. Über diese letztgenannte Einrichtung kann entweder die Aussparung 38 oder 39 mit Druck beaufschlagt bzw. entlastet werden, und zwar abhängig von der Drehrichtung des Hydromotors; hierdurch entstehen die eingangs erwähnten Druckfelder. In den Innenraum 11 dringen von entgegengesetzten Seiten und achsgleich verlaufend zwei Bohrungen 50, 51 ein, die zum Zuführen oder Abführen des Druckmittels dienen.The gear motor has a housing 10, the interior 11 of which is sealed on both sides by covers 12, 13. In the interior 11, two gears 14, 15 mesh with one another in external engagement, the shafts 16, 17 of which are mounted in bushings or glasses-shaped bearing bodies. That bearing body for the shaft journal 16 is designated by 18, that for the shaft journal 17 by 19. The shaft journal 17 has an outwardly penetrating extension 23 which penetrates through a bore in the cover, in which a seal 24 is arranged. A sealing plate 26 is arranged between the bearing body 18 and the gearwheel side surfaces. Hydraulically acted upon pressure fields are formed between this and the bearing bodies 18, which are delimited by a seal 27, as is shown in particular in FIGS. 2 and 3, which is arranged in corresponding grooves of the bearing body 18. The seal 27 is formed in two parts, namely from a support body 27A made of a somewhat harder plastic than the sealing body 27B, which consists of a rubber-elastic material. The supporting body 27A has the shape of a U in cross section, into which the lower part of the sealing body 27B is pressed. The seal 27 is arranged in a corresponding groove 28, which is located in the end face of the bearing body 18. The shape of the seal 27 or the groove 28 is again referred to in FIGS. 2 and 3, the sealing body 27B being shown in FIG. 2, since the support body 27A is underneath. Seen from above, the seal has the shape of a pair of glasses and consists of two concentric arcs 30, 31 which are connected to one another by webs 32 to 34 which lie in the same imaginary straight line, namely in a straight line which the two bores receiving the gear shaft connects. There the seal also has circular recesses 36, 37 through which the shaft journals of the gearwheels penetrate. The outer circumference of the seal 27 extends to the inner wall of the housing. As can be seen from FIG. 2, the shape of the seal results in two double-arch-shaped recesses 38, 39 which are opposite each other in mirror image, with a bore 40, 41 penetrating each of these, which run through the bearing bodies 18, 19. They are connected to channels 42, 43 which are formed in the cover and have the connection to a line 44 which are connected to a pressure medium source 46 via a proportional control valve 45. Via this latter device, either the recess 38 or 39 can be pressurized or relieved, depending on the direction of rotation of the hydraulic motor; this creates the pressure fields mentioned at the beginning. Two bores 50, 51 penetrate into the interior 11 from opposite sides and extend in the same axis and serve to supply or discharge the pressure medium.

Wird die Zahnradmaschine als Motor betrieben und fließt beispielsweise durch die Bohrung 50 unter Hochdruck stehendes Druckmittel zu, so werden über das Steuerventil 45 und die entsprechenden Kanäle die Druckfelder 38 und 31 entlastet, so daß die Dichtplatte 26 nur mit einer ganz geringen Überschußkraft an die Zahnradseitenflächen angedrückt wird, so daß die Reibkraft gering bleibt. Der Zahnradmotor kann nun leicht anlaufen. Hat er seine Drehzahl erreicht, dann wird durch entsprechende Einstellung des Ventils 45 (Schaltstellung I) in das Feld 38 unter Druck stehendes Druckmittel zugeführt, so daß nun die Dichtplatte 26 stärker an die Zahnradseitenflächen angedrückt wird, wodurch die Leckverluste entlang der Zahnradseitenflächen wesentlich verringert werden. Das Feld 39 ist dann über die Bohrung 41 vom Druck entlastet (Ventil in Stellung III). Wird der Hydromotor reversiert, d. h. wird über die Bohrung 51 unter Hochdruck stehendes Druckmittel zugeführt, so sind nun beide Felder 38, 31 entlastet, nach dem vollen Anlaufen des Motors jedoch ebenfalls wieder mit unter Hochdruck stehendem Druckmittel beaufschlagt.If the gear machine is operated as a motor and, for example, pressure medium under high pressure flows through the bore 50, the pressure fields 38 and 31 are relieved via the control valve 45 and the corresponding channels, so that the sealing plate 26 only has a very slight excess force on the gear side surfaces is pressed so that the frictional force remains low. The gear motor can now start easily. If it has reached its rotational speed, pressure medium under pressure is fed into the field 38 by appropriate adjustment of the valve 45 (switch position I), so that the sealing plate 26 is now pressed more strongly onto the gear side surfaces is, whereby the leakage losses along the gear side surfaces are significantly reduced. The field 39 is then relieved of pressure via the bore 41 (valve in position III). If the hydraulic motor is reversed, ie if pressure medium under high pressure is supplied via the bore 51, then both fields 38, 31 are relieved, but after the motor has started up fully, pressure medium under high pressure is again applied.

Es ist noch zu erwähnen, daß sich um die Lagerkörper herum in geringem Abstand zur Dichtung 27 eine Umfangsnut 52 mit kleinem Querschnitt erstreckt, über welche entlang der Dichtung durchleckendes Druckmittel aufgefangen wird. Durch die Art der Dichtung und durch die Nut 52 wird verhindert, das Druckmittel von der Hochdruckseite entlang der Lagerkörper in Richtung Deckel durchlecken kann, so daß die Innenbelastung des Gehäuses dadurch wesentlich verringert wird. Wäre dies nicht der Fall, so könnte Druckmittel von der Hochdruckseite entlang der Lagerkörper in Richtung Deckel hindurchlecken und eine relativ große Kraft auf das Gehäuse ausüben, was sehr negative Folgen hat.It should also be mentioned that a circumferential groove 52 with a small cross-section extends around the bearing body at a short distance from the seal 27, via which pressure medium leaking through the seal is collected. The type of seal and the groove 52 prevent the pressure medium from leaking from the high-pressure side along the bearing body in the direction of the cover, so that the internal load on the housing is thereby substantially reduced. If this were not the case, pressure medium could leak from the high-pressure side along the bearing body towards the cover and exert a relatively large force on the housing, which has very negative consequences.

Selbstverständlich können auf beiden Seiten der Zahnräder Dichtplatten 26 und auch in den Lagerkörpern 19, 20 entsprechende Dichtungen angeordnet werden. Eine solche Anordnung ist wohl teurer, bringt aber eine weitere Verbesserung der Funktion mit sich. Die genaue Querschnittsform des Dichtkörpers 27B ist am besten der Figur 3 zu entnehmen. Durch diese Form ergeben sich Durchflußkanäle 27C, 27D am Nutgrund, was sich als sehr zweckmäßig erwiesen hat, da hierdurch die Dichtung von hinten her beaufschlagt wird und den Stützkörper 27A besonders gut an die Dichtplatte drückt.Of course, sealing plates 26 and also corresponding seals can be arranged on both sides of the gears and in the bearing bodies 19, 20. Such an arrangement is probably more expensive, but brings with it a further improvement in function. The exact cross-sectional shape of the sealing body 27B can best be seen in FIG. 3. This shape results in flow channels 27C, 27D at the bottom of the groove, which has proven to be very expedient, since this acts on the seal from behind and presses the support body 27A particularly well against the sealing plate.

Die Zahnradmaschine kann natürlich auch als Pumpe betrieben werden. Die Beaufschlagung der Druckfelder 38, 39 kann dann insofern wesentlich vereinfacht werden, als deren Beaufschlagung einfach über die Dichtplatte durchdringende Bohrungen erfolgt. Dabei entfallen Pumpe 46, Steuerventil 45 und die entsprechenden Kanäle.The gear machine can of course also be operated as a pump. The action on the pressure fields 38, 39 can then be simplified considerably in that their action is carried out simply through bores penetrating the sealing plate. Pump 46, control valve 45 and the corresponding channels are omitted.

Claims (7)

1. Gear machine (pump or motor) having externally engaging gearwheels (14, 15) whose shafts (16, 17) are supported in bushes or "spectacle-frame" bearing bodies (18, 19) located in the casing (10) and having a sealing plate (26) completely covering the gearwheel side surfaces arranged at least on one side between the bearing bodies and the gearwheel side surfaces, pressure fields (38, 39) bounded by a seal (27) acting on said sealing plate (26) and, in consequence, bringing it into sealing contact with the gearwheel side surfaces, the pressure fields being able to be subjected to controlled or uncontrolled pressure via holes (40, 41), characterised in that the seal (27) consists of two concentrically extending, approximately "spectacle-frame" shaped relatively narrow rings (30, 31) which are connected by webs (32 to 34) which extend along a hypothetical straight line L which connects the centres of the two gearwheel shafts, in that the outer rings (30) extend as far as the external contour of the sealing plate and in that the holes (40 or 41) each emerge in one of the two fields (38, 39) located between the rings.
2. Machine according to Claim 1, characterised in that one of the fields (38, 39) is always subjected to a higher pressure than the other field.
3. Machine according to Claim 1 and/or 2, characterised in that one field is subjected to high pressure and the other field is unpressurised.
4. Machine according to Claim 1 and/or 2, characterised in that the pressure in the field with the higher pressure is subjected to a pressure controlled by a proportional pressure control valve.
5. Machine according to one of Claims 1 to 4, characterised in that the seal is located in a groove (28) formed in one of the bearing bodies and consists of a sealing body (27B) of elastomeric material located in the groove, which sealing body is inserted in a support body (27A) of a harder material, which is in direct contact with the sealing plate (26).
6. Machine according to one of Claims 1 to 4, characterised in that the bearing bodies are designed as bearing bushes or as "spectacle-frame" bearings.
7. Machine according to one of Claims 1 to 6, characterised in that sealing plates (26) with pressure fields acting on them in a corresponding manner are located on both sides of the gearwheel side surfaces.
EP19880106170 1987-05-20 1988-04-19 Gear machine (pump or motor) Expired - Lifetime EP0291703B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE8707256U DE8707256U1 (en) 1987-05-20 1987-05-20 Gear machine (pump or motor)
DE8707256U 1987-05-20

Publications (2)

Publication Number Publication Date
EP0291703A1 EP0291703A1 (en) 1988-11-23
EP0291703B1 true EP0291703B1 (en) 1991-05-15

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EP19880106170 Expired - Lifetime EP0291703B1 (en) 1987-05-20 1988-04-19 Gear machine (pump or motor)

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DE (2) DE8707256U1 (en)

Families Citing this family (3)

* 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
DE4322240C2 (en) * 1993-07-03 1997-01-09 Eckerle Rexroth Gmbh Co Kg Hydraulic internal gear machine (pump or motor)
JPH0949491A (en) * 1995-08-07 1997-02-18 Shimadzu Corp Gear pump or motor

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE925752C (en) * 1950-06-16 1955-03-28 Borg Warner High pressure fluid gear pump
US3174435A (en) * 1962-08-16 1965-03-23 Clark Equipment Co Pump or motor
DE1528943C3 (en) * 1962-08-30 1973-11-08 Borg-Warner Corp., Chicago, Ill. (V.St.A.) External mesh gear pump or motor
FR1359861A (en) * 1963-03-20 1964-04-30 Hydro Meca Method and device for hydrostatic compensation of rotary hydraulic energy transformers
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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DE8707256U1 (en) 1988-09-22
DE3862805D1 (en) 1991-06-20
EP0291703A1 (en) 1988-11-23

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