EP0377617B1 - Gearwheel motor - Google Patents

Gearwheel motor Download PDF

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Publication number
EP0377617B1
EP0377617B1 EP19880907605 EP88907605A EP0377617B1 EP 0377617 B1 EP0377617 B1 EP 0377617B1 EP 19880907605 EP19880907605 EP 19880907605 EP 88907605 A EP88907605 A EP 88907605A EP 0377617 B1 EP0377617 B1 EP 0377617B1
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EP
European Patent Office
Prior art keywords
pressure
sealing plate
gear motor
control valve
gears
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
EP19880907605
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German (de)
French (fr)
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EP0377617A1 (en
Inventor
Hayno Rustige
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP0377617A1 publication Critical patent/EP0377617A1/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 is based on a gear motor according to the preamble of claim 1.
  • a gear motor which has become known from US-A 3975174
  • the pressure fields are symmetrical to an imaginary straight line which runs through the two center points of the gear shaft.
  • the pressure of which can be controlled, so that the contact pressure of the sealing plate on the gear side surfaces can be controlled.
  • this improves the starting behavior of the gear motor.
  • the overall arrangement of the pressure fields is complex, especially since this known gear motor is reversible.
  • the gear motor according to the invention with the characterizing features of the main claim has the advantage that it can be controlled even better, especially because it is not reversible, especially in terms of its starting behavior. He also works particularly loss-free, since the throttle bore formed in the sealing plate significantly reduces outflow losses from the gear motor.
  • FIG. 1 shows a longitudinal section through a gear motor
  • FIG. 2 shows a section along II-II according to FIG. 1.
  • FIG. 3 shows a schematic diagram
  • FIG. 4 shows a modification of the exemplary embodiment according to FIG. 1.
  • FIG. 5 shows a schematic diagram.
  • the gear motor has a housing 10, the interior 11 of which has approximately the cross-sectional shape of an eight, which is closed on both sides by covers 12, 13.
  • two gears 14, 15 mesh with one another in external engagement, the shafts 16, 17 of which are mounted in spectacle-shaped bearing bodies 18, 19.
  • Bearing bodies of this type are generally known and are therefore not described further.
  • a passage 20 is formed in the cover 13, through which an extension 23 of the shaft 17 penetrates to the outside; it is sealed there by a sealing ring 24 and forms the output shaft.
  • a sealing plate 26 is arranged between the bearing body 18 and the adjacent side surfaces of the gear wheels 14, 15, which also has the contour of the housing interior and covers the entire surface of the gear wheels. Two pressure fields are effective on the back, as described below.
  • Figure 2 shows i.a. a plan view of the bearing body 18, namely from its end face facing the sealing plate 26.
  • a first use 27 which runs close to the outer contour of the bearing body, which runs partially concentrically to the gearwheel shafts and which extends from the high pressure side HD to the low pressure side ND, but does not extend up to the latter.
  • the Nutzug 27 ends in two groove ends 27A, 27B, which penetrate to the edge of the bearing body.
  • a seal 28 made of rubber-elastic material is arranged in this use.
  • a second usable part 29 which also extends from the high pressure side to the low pressure side, its ends 29A, 29B projecting further to the low pressure side than the groove ends of the usable part 27 29 also has in its central region there is an indentation 29C which leads approximately to an imaginary straight line connecting the shaft centers.
  • the high-pressure side HD is characterized by a recess 31, into which the high-pressure bore 32 penetrates from the outside of the housing, namely at the level of the gearwheels 14, 15.
  • the low-pressure side ND is characterized by a recess 33, in which an axially coextensive with the high-pressure bore 32 Low pressure bore 34 penetrates, which also extends from the exterior of the housing.
  • the sealing plate 26 which is to be pressed onto the side of the gearwheels only with a small force when starting.
  • This pressing force results from two pressure fields, namely a so-called pre-pressure field A and a main pressure field B.
  • the pre-pressure field A is delimited by the seal 28 and extends in the area radially outside of this seal - that is, between it and the housing wall - as well as in the area which lies below the surface of the seal 28 itself.
  • the main pressure field B is formed by an area which lies between the seal 28 and the seal 30 - in particular also by the rim 35 - and also lies below the surface above the seal 30.
  • the pre-pressure field A is acted upon from the recess 31 - ie the delivery pressure P of the pump 43 prevails in the pre-pressure field A - the main pressure field is acted upon by a lower pressure, which is determined in particular by the throttle bore 36.
  • the pressure in the main pressure field is a so-called control pressure Ps, which is determined by the valve 41.
  • the pressure in the main pressure field B is fed via the throttle bore 36 from the tooth chambers. If the valve 41 is open, the pressure Ps in the main pressure field is low, if the valve 41 is closed, the pressure Ps is high.
  • valve 41 When the gear motor is started up, the valve 41 is opened so that the pressure Ps in the main pressure field B is relatively low. Now the sealing plate 26 is pressed against the gears 14, 15 with a slight force. The gear motor can now start easily because the frictional force is low. With increasing speed, the valve 41 is gradually closed, so that the pressure in the main pressure field B increases and the sealing plate 26 presses with increasing force against the gear side surfaces. This has the advantage that the leakage losses below the sealing plate 26 between the low-pressure side and the high-pressure side along the side of the gearwheel are becoming ever smaller. When the valve 41 is completely closed, pressure medium can no longer flow out of the main pressure field A, so that the sealing plate 26 is now pressed against the gear side surfaces with a predetermined force. The frictional force is negligible.
  • the valve 41 can be designed as a switching valve or as a proportional valve - both electromagnetically actuated. For example, the pulse length can be modulated.
  • the sealing plate 26 is symbolically represented here as a pressure valve 26, since it in itself performs a relief function such as a pressure relief valve.
  • FIG. 4 and the schematically illustrated embodiment according to FIG. 5 relate to a modification of the above exemplary embodiment.
  • the switching valve - now labeled 50 - is no longer externally controlled, i.e. e.g. by an electromagnet, but rather by the pressure in a line 49 of the pump branching off from the delivery line 42 against the force of a spring 51. This also ensures that the gear motor starts reliably. An excessive load torque or a blocking immediately leads to the relief (lifting off) of the sealing plate 26 by the amount of the braking torque of the pressing plate. In this way, the maximum possible torque is taken from the gear motor.
  • the switching valve is expediently arranged in the cover 12 of the gear motor.

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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)
  • Electrically Driven Valve-Operating Means (AREA)

Abstract

A gearwheel motor has two mutually engaged externally toothed wheels (14, 15) against the side surfaces of which is pressed a sealing plate (26) by means of two approximately concentric compression fields (A, B). The two compression fields do not communicate with each other. The pressure of one compression field (B) can be controlled by means of an electro-magnetically driven control valve (41), thus changing the compression force of the sealing plate (26) on the toothed wheels. When the gearwheel motor is started, the compression force must be low, so that the starting resistance may also be low. Under high pressures, the compression force is increased by closing the valve, avoiding oil leakage along the toothed wheels from the high pressure to the low pressure side.

Description

ZahnradmotorGear motor Stand der TechnikState of the art

Die Erfindung geht aus von einem Zahnradmotor nach der Gattung des Anspruchs 1. Bei einem derartigen, aus der US-A 3975174 bekanntgewordenen Zahnradmotor liegen die Druckfelder symmetrisch zu einer gedachten Geraden, welche durch die beiden Mittelpunkte der Zahnradwellen verläuft. Im Zentrum dieser Druckfelder befindet sich ein kleines Zusatzdruckfeld, dessen Druck steuerbar ist, so daß die Anpreßkraft der Dichtplatte an die Zahnradseitenflächen gesteuert werden kann. Damit wird vor allem das Anlaufverhalten des Zahnradmotors verbessert. Die Gesamtanordnung der Druckfelder ist jedoch aufwendig, vor allem deshalb, da dieser bekannte Zahnradmotor reversierbar ist.The invention is based on a gear motor according to the preamble of claim 1. In such a gear motor, which has become known from US-A 3975174, the pressure fields are symmetrical to an imaginary straight line which runs through the two center points of the gear shaft. In the center of these pressure fields there is a small additional pressure field, the pressure of which can be controlled, so that the contact pressure of the sealing plate on the gear side surfaces can be controlled. Above all, this improves the starting behavior of the gear motor. However, the overall arrangement of the pressure fields is complex, especially since this known gear motor is reversible.

Vorteile der ErfindungAdvantages of the invention

Der erfindungsgemäße Zahnradmotor mit den kennzeichnenden Merkmalen des Hauptanspruchs hat demgegenüber den Vorteil, daß er, insbesondere weil nicht reversierbar, vor allem in seinem Anlaufverhalten noch besser steuerbar ist. Auch arbeitet er besonders verlustfrei, da die in der Dichtplatte ausgebildete Drosselbohrung Abflußverluste aus dem Zahnradmotor wesentlich verringert.The gear motor according to the invention with the characterizing features of the main claim has the advantage that it can be controlled even better, especially because it is not reversible, especially in terms of its starting behavior. He also works particularly loss-free, since the throttle bore formed in the sealing plate significantly reduces outflow losses from the gear motor.

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 II-II nach Figur 1. Figur 3 eine Prinzipskizze, Figur 4 eine Abwandlung des Ausführungsbeispiels nach Figur 1. Figur 5 eine Prinzipskizze.An embodiment of the invention is shown in the drawing and explained in more detail in the following description. FIG. 1 shows a longitudinal section through a gear motor, FIG. 2 shows a section along II-II according to FIG. 1. FIG. 3 shows a schematic diagram, FIG. 4 shows a modification of the exemplary embodiment according to FIG. 1. FIG. 5 shows a schematic diagram.

Beschreibung des ErfindungsbeispielesDescription of the invention example

Der Zahnradmotor weist ein Gehäuse 10 auf, dessen Innenraum 11 etwa die Querschnittsform einer Acht hat, das beidseitig durch Deckel 12, 13 verschlossen ist. Im Innenraum kämmen zwei Zahnräder 14, 15 im Außeneingriff miteinander, deren Wellen 16, 17 in brillenförmigen Lagerkörpern 18, 19 gelagert sind. Derartige Lagerkörper sind allgemein bekannt und deshalb nicht weiter beschrieben. Im Deckel 13 ist ein Durchgang 20 ausgebildet, durch welche eine Verlängerung 23 der Welle 17 nach außen dringt; sie ist dort durch einen Dichtring 24 abgedichtet und bildet die Abtriebswelle.The gear motor has a housing 10, the interior 11 of which has approximately the cross-sectional shape of an eight, which is closed on both sides by covers 12, 13. In the interior, two gears 14, 15 mesh with one another in external engagement, the shafts 16, 17 of which are mounted in spectacle-shaped bearing bodies 18, 19. Bearing bodies of this type are generally known and are therefore not described further. A passage 20 is formed in the cover 13, through which an extension 23 of the shaft 17 penetrates to the outside; it is sealed there by a sealing ring 24 and forms the output shaft.

Zwischen dem Lagerkörper 18 und den benachbarten Seitenflächen der Zahnräder 14, 15 ist eine Dichtplatte 26 angeordnet, die ebenfalls die Kontur des Gehäuseinnenraums hat und die gesamte Fläche der Zahnräder überdeckt. An ihrer Rückseite sind zwei Druckfelder wirksam, wie sie nachfolgend beschrieben sind.A sealing plate 26 is arranged between the bearing body 18 and the adjacent side surfaces of the gear wheels 14, 15, which also has the contour of the housing interior and covers the entire surface of the gear wheels. Two pressure fields are effective on the back, as described below.

Die Figur 2 zeigt u.a. eine Draufsicht auf den Lagerkörper 18, und zwar von seiner der Dichtplatte 26 zugewandten Stirnseite her. In dieser Stirnseite ist ein nahe der Außenkontur des Lagerkörpers verlaufender erster Nutzug 27 ausgebildet, welcher teilweise konzentrisch zu den Zahnradwellen verläuft, und sich von der Hochdruckseite HD zur Niederdruckseite ND hinzieht, jedoch nicht bis zu dieser verläuft. Der Nutzug 27 endet jeweils in zwei Nutenden 27A, 27B, die bis an den Rand des Lagerkörpers vordringen. In diesem Nutzug ist eine Dichtung 28 aus gummielastischem Werkstoff angeordnet.Figure 2 shows i.a. a plan view of the bearing body 18, namely from its end face facing the sealing plate 26. In this end face is formed a first use 27, which runs close to the outer contour of the bearing body, which runs partially concentrically to the gearwheel shafts and which extends from the high pressure side HD to the low pressure side ND, but does not extend up to the latter. The Nutzug 27 ends in two groove ends 27A, 27B, which penetrate to the edge of the bearing body. A seal 28 made of rubber-elastic material is arranged in this use.

Ebenfalls konzentrisch zu den Zahnradwellen, aber radial innerhalb des Nutzugs 27 ist ein zweiter Nutzug 29 ausgebildet, der sich ebenfalls von der Hochdruckseite zur Niederdruckseite hin erstreckt, wobei seine Enden 29A, 29B noch weiter zur Niederdruckseite vordringen als die Nutenden des Nutzuges 27. Der Nutzug 29 hat außerdem in seinem mittleren Bereich eine Einbuchtung 29C, die etwa bis zu einer die Wellenmitten verbindenden gedachten Geraden führt. Im Nutzug 29 ist passend eine Dichtung 30 angeordnet, die ebenfalls aus einem gummielastischen Werkstoff besteht.Also concentric to the gear shaft, but radially inside the usable part 27 is a second usable part 29, which also extends from the high pressure side to the low pressure side, its ends 29A, 29B projecting further to the low pressure side than the groove ends of the usable part 27 29 also has in its central region there is an indentation 29C which leads approximately to an imaginary straight line connecting the shaft centers. A seal 30, which also consists of a rubber-elastic material, is suitably arranged in the utilization 29.

Die Hochdruckseite HD ist gekennzeichnet durch eine Ausnehmung 31, in welche die Hochdruckbohrung 32 vom Äußeren des Gehäuses ausgehend eindringt, und zwar in Höhe der Zahnräder 14, 15. Die Niederdruckseite ND ist gekennzeichnet durch eine Ausnehmung 33, in welche eine achsgleich zur Hochdruckbohrung 32 verlaufende Niederdruckbohrung 34 eindringt, die ebenfalls vom Äußeren des Gehäuses ausgeht.The high-pressure side HD is characterized by a recess 31, into which the high-pressure bore 32 penetrates from the outside of the housing, namely at the level of the gearwheels 14, 15. The low-pressure side ND is characterized by a recess 33, in which an axially coextensive with the high-pressure bore 32 Low pressure bore 34 penetrates, which also extends from the exterior of the housing.

Wie aus Figur 2 ersichtlich ist. besteht zwischen den Nutzügen 27, 29 ein Zwischenraum, welcher im Bereich 29C ein etwas vergrößertes Feld 35 bildet, das über eine in der Dichtplatte 26 ausgebildete, durchgehende Drosselbohrung 36 mit den Zahnradkammern verbunden ist. Achsgleich zur Drosselbohrung 36 verläuft im Lagerkörper 18 eine Bohrung 37, die mit einer im Deckel 12 ausgebildeten durchgehenden Bohrung 38 Verbindung hat, an welche eine Leitung 39 angeschlossen ist. In dieser Leitung, die zu einem Behälter 40 führt, ist ein elektromagnetisch betätigbares Ventil 41 angeordnet. Dieses kann ein Schaltventil oder ein proportional arbeitendes Elekromagnetventil sein. An die Hochdruckbohrung 32 ist eine Leitung 42 angeschlossen, die zu einer Pumpe 43 führt, welche Druckmittel aus dem Behälter 40 ansaugt und dieses dem Zahnradmotor zuführt.As can be seen from Figure 2. there is an intermediate space between the useful lines 27, 29, which forms a somewhat enlarged field 35 in the region 29C, which is connected to the gearwheel chambers via a continuous throttle bore 36 formed in the sealing plate 26. Coaxial with the throttle bore 36 is a bore 37 in the bearing body 18, which has a connection to a through bore 38 formed in the cover 12, to which a line 39 is connected. In this line, which leads to a container 40, an electromagnetically actuated valve 41 is arranged. This can be a switching valve or a proportional solenoid valve. A line 42 is connected to the high-pressure bore 32 and leads to a pump 43 which sucks pressure medium from the container 40 and supplies it to the gear motor.

Wesentlich beim Betrieb des Zahnradmotors ist, daß dieser beim Anlaufen nur einen geringen Reibungswiderstand zu überwinden hat. Dies bezieht sich insbesondere auf die Dichtplatte 26, die beim Anlauf nur mit geringer Kraft an die Zahnradseitenflächen gedrückt werden soll. Diese Andrückkraft resultiert aus zwei Druckfeldern, nämlich einem sogenannten Vordruckfeld A und einem Hauptdruckfeld B. Das Vordruckfeld A ist begrenzt durch die Dichtung 28 und erstreckt sich im Bereich radial außerhalb dieser Dichtung ― also zwischen dieser und der Gehäusewand ― sowie im Bereich, welcher unter der Fläche der Dichtung 28 selbst liegt. Das Hauptdruckfelb B ist gebildet durch einen Bereich, der zwischen der Dichtung 28 und der Dichtung 30 liegt ― insbesondere auch durch das Felb 35 ― und außerdem unter der Fläche ber Dichtung 30 liegt. Das Vordruckfelb A ist beaufschlagt von der Ausnehmung 31 her ― d.h. im Vordruckfeld A herrscht der Förderdruck P der Pumpe 43 ― das Hauptdruckfeld ist von einem niedrigeren Druck beaufschlagt, der insbesondere durch die Drosselbohrung 36 mitbestimmt ist. Der Druck im Hauptdruckfeld ist ein sogenannter Steuerdruck Ps, der bestimmt wird durch das Ventil 41. Gespeist wird der Druck im Hauptdruckfeld B über die Drosselbohrung 36 von den Zahnkammern her. Wenn das Ventil 41 stark geöffnet ist, ist der Druck Ps im Hauptdruckfeld gering, wenn das Ventil 41 geschlossen ist, ist der Druck Ps groß.It is essential in the operation of the gear motor that it has to overcome only a slight frictional resistance when starting. This relates in particular to the sealing plate 26, which is to be pressed onto the side of the gearwheels only with a small force when starting. This pressing force results from two pressure fields, namely a so-called pre-pressure field A and a main pressure field B. The pre-pressure field A is delimited by the seal 28 and extends in the area radially outside of this seal - that is, between it and the housing wall - as well as in the area which lies below the surface of the seal 28 itself. The main pressure field B is formed by an area which lies between the seal 28 and the seal 30 - in particular also by the rim 35 - and also lies below the surface above the seal 30. The pre-pressure field A is acted upon from the recess 31 - ie the delivery pressure P of the pump 43 prevails in the pre-pressure field A - the main pressure field is acted upon by a lower pressure, which is determined in particular by the throttle bore 36. The pressure in the main pressure field is a so-called control pressure Ps, which is determined by the valve 41. The pressure in the main pressure field B is fed via the throttle bore 36 from the tooth chambers. If the valve 41 is open, the pressure Ps in the main pressure field is low, if the valve 41 is closed, the pressure Ps is high.

Beim Anfahren des Zahnradmotors ist das Ventil 41 stark geöffnet, so daß der Druck Ps im Hauptdruckfeld B relativ gering ist. Nun wird die Dichtplatte 26 noch mit einer geringen Kraft gegen die Zahnräder 14, 15 gedrückt. Der Zahnradmotor kann nun leicht anlaufen, weil die Reibungskraft gering ist. Bei zunehmender Drehzahl wird das Ventil 41 nach und nach geschlossen, so daß der Druck im Hauptdruckfeld B ansteigt und die Dichtplatte 26 mit zunehmender Kraft gegen die Zahnradseitenflächen drückt. Das hat den Vorteil, daß nun die Leckverluste unterhalb der Dichtplatte 26 zwischen der Niederdruckseite und der Hochdruckseite entlang der Zahnradseitenfläche immer geringer werden. Wenn das Ventil 41 ganz geschlossen ist, kann kein Druckmittel mehr aus dem Hauptdruckfeld A abfließen, so daß nun die Dichtplatte 26 mit einer vorbestimmten Kraft an die Zahnradseitenflächen gedrückt wird. Die Reibkraft ist dabei vernachlässigbar. Das Ventil 41 kann als Schaltventil oder als Proportionalventil ― beide elektromagnetisch betätigt ― ausgebildet sein. Es kann z.B. die Pulslänge moduliert werden.When the gear motor is started up, the valve 41 is opened so that the pressure Ps in the main pressure field B is relatively low. Now the sealing plate 26 is pressed against the gears 14, 15 with a slight force. The gear motor can now start easily because the frictional force is low. With increasing speed, the valve 41 is gradually closed, so that the pressure in the main pressure field B increases and the sealing plate 26 presses with increasing force against the gear side surfaces. This has the advantage that the leakage losses below the sealing plate 26 between the low-pressure side and the high-pressure side along the side of the gearwheel are becoming ever smaller. When the valve 41 is completely closed, pressure medium can no longer flow out of the main pressure field A, so that the sealing plate 26 is now pressed against the gear side surfaces with a predetermined force. The frictional force is negligible. The valve 41 can be designed as a switching valve or as a proportional valve - both electromagnetically actuated. For example, the pulse length can be modulated.

Dieser gesamte Vorgang ist schematisch in Figur 3 zu erkennen. Die Dichtplatte 26 ist hier symbolisch als Druckventil 26 dargesellt, da sie an sich ja eine Entlastungsfunktion wie ein Druckbegrenzungsventil ausübt.This entire process can be seen schematically in FIG. 3. The sealing plate 26 is symbolically represented here as a pressure valve 26, since it in itself performs a relief function such as a pressure relief valve.

Die Figur 4 und die schematisch dargestellte Ausführung nach Figur 5 betreffen eine Abwandlung obigen Ausführungsbeispiels. Das Schaltventil ― jetzt bezeichnet mit 50 ― ist hier nicht mehr fremdgesteuert, d.h. z.B. von einem Elektromagneten, sondern vom Druck in einer von der Förderleitung 42 abzweigenden Leitung 49 der Pumpe entgegen der Kraft einer Feder 51. Auch hierdurch wird ein sicherer Anlauf des Zahnradmotors erreicht. Ein überhöhtes Lastmoment oder ein Blockieren führt sofort zum Entlasten (Abheben) der Dichtplatte 26 um den Betrag des Bremsmomentes der andrückenden Platte. Dem Zahnradmotor wird auf diese Weise das maximal mögliche Drehmoment entnommen. Zweckmäßigerweise wird das Schaltventil im Deckel 12 des Zahnradmotors angeordnet.FIG. 4 and the schematically illustrated embodiment according to FIG. 5 relate to a modification of the above exemplary embodiment. The switching valve - now labeled 50 - is no longer externally controlled, i.e. e.g. by an electromagnet, but rather by the pressure in a line 49 of the pump branching off from the delivery line 42 against the force of a spring 51. This also ensures that the gear motor starts reliably. An excessive load torque or a blocking immediately leads to the relief (lifting off) of the sealing plate 26 by the amount of the braking torque of the pressing plate. In this way, the maximum possible torque is taken from the gear motor. The switching valve is expediently arranged in the cover 12 of the gear motor.

Claims (4)

1. Gear motor having two gears arranged in a housing (10, 13) and meshing externally, a sealing plate (26) adapted to the contour of the inner space (11) of the housing being arranged on at least one end face of the gears, which sealing plate (26) is pressed against the side faces of the gears by fluid pressure acting in two pressure zones, and the pressure zones are defined by two seals arranged on the side remote from the gears, the pressure zones being designed as two pressure zones (A, B), essentially concentric to one another at least over a partial area relative to the gear axes (16, 17), and in fact a radially outer admission-pressure zone (A) and a radially inner main-pressure zone (B) whose pressure can be controlled by means of a control valve (41, 50) which controls a connection to the return and is connected via a pressure-medium connection (37, 38, 39) to the main-pressure zone (B), characterised in that the main-pressure zone (B) is arranged in the intermediate space (35) between the two seals (28, 30), and in that it is connected to the gear chambers via a restrictor bore (36) passing through the sealing plate (26).
2. Gear motor according to Claim 1, characterised in that the control valve (41) is designed as a pilot valve.
3. Gear motor according to Claim 1 and/or 2, characterised in that the control valve (41, 50) can be adjusted in flow direction against the force of a spring by the pressure in the feed line.
4. Gear motor according to Claim 1 and/or 2, characterised in that the control valve (50) can be adjusted at random by an electromagnet.
EP19880907605 1987-09-10 1988-09-02 Gearwheel motor Expired - Lifetime EP0377617B1 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE8712245 1987-09-10
DE8712245U 1987-09-10
DE8806388U 1988-05-14
DE8806388U DE8806388U1 (en) 1987-09-10 1988-05-14 Gear motor

Publications (2)

Publication Number Publication Date
EP0377617A1 EP0377617A1 (en) 1990-07-18
EP0377617B1 true EP0377617B1 (en) 1991-09-18

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP19880907605 Expired - Lifetime EP0377617B1 (en) 1987-09-10 1988-09-02 Gearwheel motor

Country Status (5)

Country Link
US (1) US5052905A (en)
EP (1) EP0377617B1 (en)
JP (1) JPH03500194A (en)
DE (2) DE8806388U1 (en)
WO (1) WO1989002515A1 (en)

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DE3816537A1 (en) * 1988-05-14 1989-11-23 Bosch Gmbh Robert GEAR PUMP
DE3902139A1 (en) * 1989-01-25 1990-07-26 Bosch Gmbh Robert HYDROSTATIC DRIVE
DE3919939C2 (en) * 1989-06-19 1998-07-30 Bosch Gmbh Robert Hydrostatic drive
DE3923518A1 (en) * 1989-07-15 1991-01-17 Bosch Gmbh Robert Gear pump with externally meshing gears - incorporates control pipe for load sensing pressure
DE3924482A1 (en) * 1989-07-25 1991-02-07 Bosch Gmbh Robert GEAR PUMP
DE3931186C2 (en) * 1989-09-19 1999-12-16 Bosch Gmbh Robert Gear motor
DE3938135A1 (en) * 1989-11-16 1991-05-23 Bosch Gmbh Robert GEAR PUMP
DE4124466C2 (en) * 1991-07-24 1999-04-01 Bosch Gmbh Robert Gear machine (pump or motor)
JP4333422B2 (en) * 2003-06-02 2009-09-16 株式会社島津製作所 Gear pump or motor
US20070201989A1 (en) * 2005-10-14 2007-08-30 Parker-Hannifin Low ripple gear pump/motor
US8998496B2 (en) * 2012-03-30 2015-04-07 Imo Industries, Inc. Gear pump with asymmetrical dual bearing
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Also Published As

Publication number Publication date
JPH03500194A (en) 1991-01-17
DE8806388U1 (en) 1989-01-12
US5052905A (en) 1991-10-01
EP0377617A1 (en) 1990-07-18
WO1989002515A1 (en) 1989-03-23
DE3865019D1 (en) 1991-10-24

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