EP0377617A1 - Gearwheel motor. - Google Patents

Gearwheel motor.

Info

Publication number
EP0377617A1
EP0377617A1 EP88907605A EP88907605A EP0377617A1 EP 0377617 A1 EP0377617 A1 EP 0377617A1 EP 88907605 A EP88907605 A EP 88907605A EP 88907605 A EP88907605 A EP 88907605A EP 0377617 A1 EP0377617 A1 EP 0377617A1
Authority
EP
European Patent Office
Prior art keywords
pressure
control valve
sealing plate
gear motor
gear
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.)
Granted
Application number
EP88907605A
Other languages
German (de)
French (fr)
Other versions
EP0377617B1 (en
Inventor
Hayno Rustige
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0377617A1 publication Critical patent/EP0377617A1/en
Application granted granted Critical
Publication of EP0377617B1 publication Critical patent/EP0377617B1/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
    • 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 motor according to the preamble of the main claim.
  • the disadvantage of such a known gear motor is that the pressure medium control between the pre-pressure field and the main pressure field does not function satisfactorily, so that the pressure build-up in the main pressure field does not take place properly.
  • the gear motor according to the invention with the characterizing features of the main claim has the advantage that the control of the pre and the main pressure field is unproblematic. This improves the functionality of 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. Description of the invention example
  • 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 toothed wheels 14, 15 mesh with one another in external engagement, the bright teeth 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. On its back side, two pressure fields are effective, 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 running close to the outer contour of the bearing body, which partially runs concentrically to the gear shaft and extends from the high pressure side HD to the low pressure side ND but does not extend up to this.
  • 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 groove train.
  • a second tool 29 which also extends from the high pressure side to the low pressure side, its ends 29A, 29B penetrating further to the low pressure side than the groove ends of the tool 27.
  • Usage 29 also has in its central area there is an indentation 29C which leads approximately to an imaginary straight line connecting the shaft centers.
  • a seal 30, which likewise consists of a rubber-elastic material, is suitably arranged in the groove 29.
  • 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 axis coincides with the high-pressure bore 32 extending low pressure bore 34 penetrates, which also starts from the outside of the housing.
  • the sealing plate 26 which is to be pressed against the gearwheel side surfaces 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 field 35 - and also lies below the surface of 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 opened strongly, the pressure Ps in the main pressure field is low, if the valve 41 is closed, the pressure Ps is high.
  • the friction force is negligible.
  • the valve 41 can be designed as a switching valve or as a proportional valve - both electromagnetically actuated. It can e.g. B. the pulse length can be modulated. 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 limiting 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 designated 50 - is no longer externally controlled here, i. H. z. B. by an electromagnet, but by the pressure in a line 49 branching from the delivery line 42 of the pump against the force of a spring 51. This also ensures a reliable start of the gear motor. 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.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Hydraulic Motors (AREA)
  • Electrically Driven Valve-Operating Means (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Abstract

Moteur turbinaire à engrenages comportant deux roues dentées (14, 15) à contact externe mutuel, sur les surfaces latérales desquelles une plaque d'étanchéité (26) est appliquée par deux champs de compression (A, B) approximativement concentriques. Les deux champs de compression ne communiquent pas l'un avec l'autre. On peut commander la pression d'un champ de compression (B) au moyen d'une soupape de régulation (41) à commande électromagnétique, modifiant ainsi la force de compression de la plaque d'étanchéité (26) sur les roues dentées. Lorsque l'on démarre le moteur turbinaire à engrenages, la force de compression doit être faible de sorte que la résistance de démarrage puisse également être faible. Lors de pressions élevées, la force de compression est augmentée par fermeture de la soupape, ce qui évite une fuite d'huile le long des roues dentées, à partir du côté à pression élevée jusqu'au côté à basse pression.Geared turbine engine comprising two toothed wheels (14, 15) with mutual external contact, on the side surfaces of which a sealing plate (26) is applied by two compression fields (A, B) approximately concentric. The two compression fields do not communicate with each other. The pressure of a compression field (B) can be controlled by means of an electromagnetically controlled regulating valve (41), thereby changing the compressive force of the sealing plate (26) on the sprockets. When starting the gear turbine engine, the compressive force should be low so that the starting resistance can also be low. At high pressures, the compressive force is increased by closing the valve, which prevents oil leakage along the gears from the high pressure side to the low pressure side.

Description

Zahnradmotor Gear motor
Stand der TechnikState of the art
Die Erfindung geht aus von einem Zahnradmotor nach der Gattung des Hauptanspruchs. Bei einem derartigen bekannten Zahnradmotor ergibt sich der Nachteil, daß die Druckmittelsteuerung zwischen Vordruck- feld und Hauptdruckfeld nicht befriedigend funktioniert, so daß der Druckaufbau im Hauptdruckfeld nicht einwandfrei erfolgt.The invention relates to a gear motor according to the preamble of the main claim. The disadvantage of such a known gear motor is that the pressure medium control between the pre-pressure field and the main pressure field does not function satisfactorily, so that the pressure build-up in the main pressure field does not take place properly.
Vorteile der ErfindungAdvantages of the invention
Der erfindungsgemäße Zahnradmotor mit den kennzeichnenden Merkmalen des Hauptanspruchs hat demgegenüber den Vorteil, daß die Steuerung des Vor- und des Hauptdruckfelds unproblematisch ist. Damit wird die Funktionsfähigkeit des Zahnradmotors verbessert.The gear motor according to the invention with the characterizing features of the main claim has the advantage that the control of the pre and the main pressure field is unproblematic. This improves the functionality of the gear motor.
Zeichnungdrawing
Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung darge¬ stellt 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. Beschreibung des ErfindungsbeispielesAn 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, and FIG. 5 shows a schematic diagram. Description 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 Hellen 16, 17 in brillenförmigen Lagerkörpern 18, 19 gelagert sind. Derartige Lagerkörper sind allge¬ mein 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 toothed wheels 14, 15 mesh with one another in external engagement, the bright teeth 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 Bückseite sind zwei Druckfelder wirk¬ sam, 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. On its back side, two pressure fields are effective, 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 ver¬ laufender erster Nutzug 27 ausgebildet, welcher teilweise konzen¬ trisch zu den Zahnradwellen verläuft, und sich von der Hochdruck¬ seite 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 Nut¬ zug 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 running close to the outer contour of the bearing body, which partially runs concentrically to the gear shaft and extends from the high pressure side HD to the low pressure side ND but does not extend up to this. 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 groove train.
Ebenfalls konzentrisch zu den Zahnradwellen, aber radial innerhalb des Nutzugs 27 ist ein zweiter Nutzug 29 ausgebildet, der sich eben¬ falls von der Hochdruckseite zur Niederdruckseite hin erstreckt, wobei seine Enden 29A, 29B noch weiter zur Niederdruckseite vor¬ dringen 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 Nut¬ zug 29 ist passend eine Dichtung 30 angeordnet, die ebenfalls aus einem gummielastischen Werkstoff besteht.Also concentric with the gearwheel shafts, but radially inside the tool 27 is a second tool 29, which also extends from the high pressure side to the low pressure side, its ends 29A, 29B penetrating further to the low pressure side than the groove ends of the tool 27. Usage 29 also has in its central area there is an indentation 29C which leads approximately to an imaginary straight line connecting the shaft centers. A seal 30, which likewise consists of a rubber-elastic material, is suitably arranged in the groove 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 Niederdruck¬ seite 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 axis coincides with the high-pressure bore 32 extending low pressure bore 34 penetrates, which also starts from the outside 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 FIG. 2, there is an intermediate space between the cables 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 An¬ laufen nur einen geringen Reibungswiders and 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 Hauptdruckfeld B ist gebildet durch einen Bereich, der zwischen der Dichtung 28 und der Dichtung 30 liegt - insbesondere auch durch das Feld 35 - und außerdem unter der Fläche der Dichtung 30 liegt. Das Vordruckfeld 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 Drossel¬ bohrung 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 against the gearwheel side surfaces 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 field 35 - and also lies below the surface of 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 opened strongly, 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 Zahnradseitenfl chen drückt. Das hat den Vorteil, daß nun die Leckverluste unterhalb der Dichtplatte 26 zwischen der Niederdruck¬ seite 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 Zahnradseiten¬ flächen 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. 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 Druckbegrenzungs- ventil ausübt.When the gear motor is started up, the valve 41 is strongly 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 surfaces with increasing force against the Zahnradseitenfl. 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, no more pressure medium can 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 friction force is negligible. The valve 41 can be designed as a switching valve or as a proportional valve - both electromagnetically actuated. It can e.g. B. the pulse length can be modulated. 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 limiting valve.
Die Figur 4 und die schematisch dargestellte Ausführung nach Figur 5 betreffen eine Abwandlung obigen Ausführungsbeispiels. Das Schalt¬ ventil - jetzt bezeichnet mit 50 - ist hier nicht mehr fremdge¬ steuert, 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 designated 50 - is no longer externally controlled here, i. H. z. B. by an electromagnet, but by the pressure in a line 49 branching from the delivery line 42 of the pump against the force of a spring 51. This also ensures a reliable start of the gear motor. 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

Ansprüche Expectations
1. Zahnradmotor mit zwei im Außeneingriff kämmenden Zahnrädern, wobei auf mindestens einer Seite der Zahnräder eine der Kontur des Innenraums (11) des Gehäuses angepaßte Dichtplatte (26) angeordnet ist, die durch in zwei Druckfeldern wirkenden Flüssigkeitsdruck gegen die Zahnradseitenflächen gedrückt wird und die Druckfelder durch auf der den Zahnrädern abgewandten Seite angeordnete Dich¬ tungen abgegrenzt sind, wobei die Druckfelder als zwei zueinander mindestens über einen Teilbereich zu den Wellenbohrungen (27, 28) im wesentlichen konzentrische Druckfelder (A, B) ausgebildet sind, und zwar einem radial außenliegenden Vordruckfeld (A) und einem radial innenliegenden Hauptdruckfeld (B), dessen Druck mittels eines Steuerventils (41, 50) steuerbar ist, das eine Verbindung zum Rück¬ lauf steuert, dadurch gekennzeichnet, daß der Zwischenraum (35) zwischen den Dichtungen (28, 30) einerseits durch eine die Dicht¬ platte (26) durchdringende Drosselbohrung (36) mit dem Zahnkammern verbunden ist, andererseits über eine Druckmittelverbindung (37, 38, 39) mit dem Steuerventil (41).1. Gear motor with two meshing external gears, wherein on at least one side of the gears one of the contours of the interior (11) of the housing adapted sealing plate (26) is arranged, which is pressed by liquid pressure acting in two pressure fields against the gear side surfaces and the pressure fields are delimited by seals arranged on the side facing away from the gearwheels, the pressure fields being formed as two pressure fields (A, B) which are essentially concentric with one another at least over a partial area with respect to the shaft bores (27, 28), namely a radially outer pre-pressure field (A) and a radially inner main pressure field (B), the pressure of which can be controlled by means of a control valve (41, 50) which controls a connection to the return flow, characterized in that the intermediate space (35) between the seals (28, 30 ) on the one hand through a throttle bore (36) penetrating the sealing plate (26) with the tooth box is connected, on the other hand via a pressure medium connection (37, 38, 39) to the control valve (41).
2. Zahnradmotor nach Anspruch 1, dadurch gekennzeichnet, daß das Steuerventil (41) als Schaltventil ausgebildet ist. 2. Gear motor according to claim 1, characterized in that the control valve (41) is designed as a switching valve.
3. Zahnradmotor nach Anspruch 1 und/oder 2, dadurch gekennzeichnet, daß das Steuerventil (41, 50) entgegen der Kraft einer Feder vom Druck in der Förderleitung in Durchflußrichtung einstellbar ist.3. Gear motor according to claim 1 and / or 2, characterized in that the control valve (41, 50) is adjustable against the force of a spring by the pressure in the delivery line in the flow direction.
4. Zahnrad otor nach Anspruch 1 und/oder 2, dadurch gekennzeichnet, daß das Steuerventil (50) willkürlich durch einen Elektromagneten einstellbar ist. 4. gear otor according to claim 1 and / or 2, characterized in that the control valve (50) is arbitrarily adjustable 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 true EP0377617A1 (en) 1990-07-18
EP0377617B1 EP0377617B1 (en) 1991-09-18

Family

ID=25952038

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)

Families Citing this family (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
CN103939334B (en) * 2013-01-17 2017-06-06 常州雷利电机科技有限公司 Gear pump
DE102014208021A1 (en) * 2014-04-29 2015-10-29 Robert Bosch Gmbh Gear machine with eccentricity on the gears
US10544867B2 (en) * 2017-10-30 2020-01-28 Saudi Arabian Oil Company Spectacle blinds swinging device
US11060559B2 (en) * 2018-06-11 2021-07-13 Eaton Intelligent Power Limited Bi-metallic journal bearing with additive manufactured sleeve

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3175468A (en) * 1962-04-05 1965-03-30 Cessna Aircraft Co Fluid motor with delayed pressure loading
DE1553133A1 (en) * 1966-12-23 1970-07-30 Maag Zahnraeder & Maschinen Ag High pressure gear pump
DE2349304C3 (en) * 1973-10-01 1981-07-16 Robert Bosch Gmbh, 7000 Stuttgart Gear motor operated with hydraulic fluid
JPS5543220A (en) * 1978-09-19 1980-03-27 Kayaba Ind Co Ltd Terminal structure of seal to demarcate gear pump or high pressure area and low pressure area in motor
DE2846547A1 (en) * 1978-10-26 1980-04-30 Pierburg Luftfahrtgeraete SELF-SEALING GEAR PUMP
DE2855567A1 (en) * 1978-12-22 1980-06-26 Duesterloh Gmbh Rotary seal strip for gear pump or motor - has spring loaded oil-pressurised seal elements set via throttle with pressure limited by valve
DE3605246C2 (en) * 1986-02-19 1993-11-25 Bosch Gmbh Robert Gear machine (pump or motor)

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO8902515A1 *

Also Published As

Publication number Publication date
WO1989002515A1 (en) 1989-03-23
JPH03500194A (en) 1991-01-17
DE8806388U1 (en) 1989-01-12
DE3865019D1 (en) 1991-10-24
US5052905A (en) 1991-10-01
EP0377617B1 (en) 1991-09-18

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