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EP0199741B1 - Pinion motor - Google Patents

Pinion motor Download PDF

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Publication number
EP0199741B1
EP0199741B1 EP85904608A EP85904608A EP0199741B1 EP 0199741 B1 EP0199741 B1 EP 0199741B1 EP 85904608 A EP85904608 A EP 85904608A EP 85904608 A EP85904608 A EP 85904608A EP 0199741 B1 EP0199741 B1 EP 0199741B1
Authority
EP
European Patent Office
Prior art keywords
bearing elements
thickness
pinions
motor according
bearing bodies
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
Application number
EP85904608A
Other languages
German (de)
French (fr)
Other versions
EP0199741A1 (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 EP0199741A1 publication Critical patent/EP0199741A1/en
Application granted granted Critical
Publication of EP0199741B1 publication Critical patent/EP0199741B1/en
Expired 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.
  • the bearing bodies are of the same thickness, and there are usually liquid-pressurized pressure fields on both ends of the bearing bodies facing away from the gears, which bring the bearing bodies into sealing contact with the gear side surfaces.
  • mechanical forces arise which press the bearing bodies against the housing recess receiving them, specifically at a point on the low-pressure side.
  • These holding forces can be so great that they prevent any movement of the bearing body, i. H. the bearing bodies can be pressed too strongly or too weakly onto the gear side surfaces. This can affect the volumetric and mechanical efficiency and the starting behavior of the gear motor and even increase its wear.
  • the thicknesses of the bearing bodies are different, but sealing plates or additional pistons are used with these types.
  • the arrangement according to the invention with the characterizing features of the main claim has the advantage that it does not require additional components and that the holding forces mentioned are lower, since they are proportional to the thickness of the bearing body. This improves the mobility of the bearing bodies, which also improves volumetric and mechanical efficiency and reduces mechanical losses. A mobility of the bearing body is particularly necessary when the gears expand or contract due to temperature changes.
  • FIG. 1 shows a longitudinal section through a gear motor
  • FIG. 2 a schematic diagram
  • the gear motor has a housing 10, the interior 11 of which is closed on both sides by covers 12, 13.
  • the interior is formed by two intersecting holes, so that it has the cross-sectional shape of an eight; see FIG. 2, in the interior 11 there are two gear wheels 14, 15 which are connected to one another in external engagement.
  • the shafts 16, 17 of the gear wheels 14, 15 are mounted in bush-shaped bearing bodies 18, 19 and 20, 21, respectively.
  • These bearing bodies are arranged to be slightly movable in the interior 11 of the housing 10 in the axial and radial directions. It is essential that the thickness of the bearing bodies 19, 21 is significantly less than the thickness of the bearing bodies 18, 20 on the opposite side.
  • pressure fields 26, 27, which are delimited by a seal and are acted upon by hydraulic fluid, are formed in a known manner and bring the bearing bodies 19, 21 into sealing contact with the side faces of the gear wheels.
  • Two holes 23, 24 penetrate into the interior 11 at the level of the gearwheels from opposite sides of the housing, of which the hole 23 forms the high-pressure hole, the hole 24, the low-pressure hole.
  • a gap 25 leads from the high-pressure bore 23 along the bearing bodies 19, 21 to the flat rear side of the same and builds up the high-pressure field 26 there, while the remaining part of the bearing body surface forms a low-pressure field 27, which is formed by a gap 28 along the bearing bodies with the low-pressure bore 23 connected is.
  • the hydraulic forces create forces P1 and P2, which move the gears together with the bearing bodies in the direction of the low-pressure side and press them against the inner wall of the housing in areas B1 and B2.
  • the forces in pressure fields 26 and 27 support this, the holding forces P1 and P2 must not be too large, however, since they would then oppose any movement of the bearing bodies, so that they are pressed too little or too tightly against the gear side surfaces. This makes starting the gear motor difficult.
  • the size of the holding forces is proportional to the thickness of the bearing body. By reducing the thickness of the bearing bodies 19, 21 acted upon by the pressure fields, these holding forces are reduced in a desired manner and the mobility thereof is improved. This keeps volumetric and mechanical losses low. If pressure medium under high pressure is supplied to the gear motor via the bore 24, the gear wheels rotate and emit a torque on the shaft 30 emerging from the housing 10.
  • a sealing body is arranged at the shaft passage.

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

Abstract

The pinion motor has two pinions which engage on their external sides (14, 15) the shafts of the pinions being supported on both sides in bearings (18 to 21). The bearing elements (19, 21) on one side of the pinions are designed with a lesser thickness than those on the other side. They are pressed against the lateral surfaces of the pinions by pressure regions (26, 27). The application forces of the thinner bearing elements (19, 21) against the inner wall (11) of the housing (10) must not be too large, since otherwise the starting-up behaviour of the pinion motor is impaired. These application forces are, inter alia, proportioned to the thickness of the bearing elements; the bearing elements on which the pressure regions are provided are not so thick.

Description

Stand der TechnikState of the art

Die Erfindung betrifft einen Zahnradmotor. Bei derartigen bekannten Zahnradmotoren sind die Lagerkörper gleich dick ausgebildet, und meist befinden sich auf beiden den Zahnrädern abgewandten Stirnseiten dieser Lagerkörper flüssigkeitsbeaufschlagte Druckfelder, welche die Lagerkörper in dichtende Berührung mit den Zahnradseitenflächen bringen. Dabei entstehen im Zusammenwirken mit den an den Zahnrädern wirkenden Druckkräften mechanische Kräfte, welche die Lagerkörper gegen die sie aufnehmende Gehäuseausnehmung drücken, und zwar an einer Stelle, die auf der Niederdruckseite liegt. Diese Haltekräfte können so groß sein, daß sie jede Bewegung der Lagerkörper verhindern, d. h. die Lagerkörper können zu stark oder zu schwach an die Zahnradseitenflächen angepreßt sein. Das kann den volumetrischen und mechanischen Wirkungsgrad und das Anlaufverhalten des Zahnradmotors beeinträchtigen und sogar dessen Verschleiß vergrößern. Bei Zahnradmotoren nach der Gattung des Hauptanspruchs, d. h. nach der FR-A-1 442211 oder auch nach der GB-A-1 140 651, sind zwar die Dicken der Lagerkörper unterschiedlich aber bei diesen Bauarten werden Dichtplatten oder zusätzliche Kolben verwendet.The invention relates to a gear motor. In such known gear motors, the bearing bodies are of the same thickness, and there are usually liquid-pressurized pressure fields on both ends of the bearing bodies facing away from the gears, which bring the bearing bodies into sealing contact with the gear side surfaces. In cooperation with the pressure forces acting on the gearwheels, mechanical forces arise which press the bearing bodies against the housing recess receiving them, specifically at a point on the low-pressure side. These holding forces can be so great that they prevent any movement of the bearing body, i. H. the bearing bodies can be pressed too strongly or too weakly onto the gear side surfaces. This can affect the volumetric and mechanical efficiency and the starting behavior of the gear motor and even increase its wear. For gear motors according to the type of the main claim, i. H. According to FR-A-1 442211 or GB-A-1 140 651, the thicknesses of the bearing bodies are different, but sealing plates or additional pistons are used with these types.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Anordnung mit den kennzeichnenden Merkmalen des Hauptanspruchs hat demgegenüber den Vorteil, daß sie ohne zusätzliche Bauteile auskommt und daß trotzdem die genannten Haltekräfte geringer sind, da sie proportional der Dicke der Lagerkörper sind. Die Beweglichkeit der Lagerkörper wird dadurch besser, wodurch auch der volumetrische und mechanische Wirkungsgrad besser und die mechanischen Verluste geringer werden. Eine Beweglichkeit der Lagerkörper ist besonders dann erforderlich, wenn sich die Zahnräder durch Temperaturänderungen ausdehnen bzw. zusammenziehen.The arrangement according to the invention with the characterizing features of the main claim has the advantage that it does not require additional components and that the holding forces mentioned are lower, since they are proportional to the thickness of the bearing body. This improves the mobility of the bearing bodies, which also improves volumetric and mechanical efficiency and reduces mechanical losses. A mobility of the bearing body is particularly necessary when the gears expand or contract due to temperature changes.

Durch die in den Unteransprüchen aufgeführten Maßnahmen sind Weiterbildungen der im Hauptanspruch angegebenen Merkmale möglich.The measures listed in the subclaims allow further developments of the features specified in the main claim.

Zeichnungdrawing

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt. Diese zeigt in Figur 1 einen Längsschnitt durch einen Zahnradmotor, in Figur 2 eine Prinzipskizze,An embodiment of the invention is shown in the drawing. 1 shows a longitudinal section through a gear motor, in FIG. 2 a schematic diagram,

Beschreibung des ErfindungsbeispielsDescription of the invention example

Der Zahnradmotor hat ein Gehäuse 10, dessen Innenraum 11 beidseitig durch Deckel 12, 13 verschlossen ist. Der Innenraum ist durch zwei sich überschneidende Bohrungen gebildet, so daß er die Querschnittsform einer Acht hat ; siehe hierzu Figur 2, Im Innenraum 11 befinden sich zwei Zahnräder 14, 15, die im Außeneingriff miteinander in Verbindung stehen, Die Wellen 16, 17 der Zahnräder 14, 15 sind in buchsenförmigen Lagerkörpern 18, 19 bzw. 20, 21 gelagert. Diese Lagerkörper sind in axialer wie in radialer Richtung geringfügig beweglich im Innenraum 11 des Gehäuses 10 angeordnet, Wesentlich ist, daß die Dicke der Lagerkörper 19, 21 wesentlich geringer ist als die Dicke der Lagerkörper 18, 20 auf der entgegengesetzten Seite. Auf der den Zahnrädern 14, 15 abgewandten Seite der Lagerkörper 19, 21 sind in bekannter Weise durch eine Dichtung 22 begrenzte, mit Hydraulikflüssigkeit beaufschlagte Druckfelder 26, 27 ausgebildet, welche die Lagerkörper 19, 21 in dichtende Berührung mit den Zahnradseitenflächen bringen. In den Innenraum 11 dringen in Höhe der Zahnräder von entgegengesetzten Seiten des Gehäuses zwei Bohrungen 23, 24 ein, von denen die Bohrung 23 die Hochdruckbohrung, die Bohrung 24, die Niederdruckbohrung bildet. Von der Hochdruckbohrung 23 führt ein Spalt 25 entlang der Lagerkörper 19, 21 an die flache Rückseite derselben und baut dort das Hochdruckfeld 26 auf, während der restliche Teil der Lagerkörperfläche ein Niederdruckfeld 27 bildet, das durch einen Spalt 28 entlang der Lagerkörper mit der Niederdruckbohrung 23 verbunden ist.The gear motor has a housing 10, the interior 11 of which is closed on both sides by covers 12, 13. The interior is formed by two intersecting holes, so that it has the cross-sectional shape of an eight; see FIG. 2, in the interior 11 there are two gear wheels 14, 15 which are connected to one another in external engagement. The shafts 16, 17 of the gear wheels 14, 15 are mounted in bush-shaped bearing bodies 18, 19 and 20, 21, respectively. These bearing bodies are arranged to be slightly movable in the interior 11 of the housing 10 in the axial and radial directions. It is essential that the thickness of the bearing bodies 19, 21 is significantly less than the thickness of the bearing bodies 18, 20 on the opposite side. On the side of the bearing bodies 19, 21 facing away from the gears 14, 15, pressure fields 26, 27, which are delimited by a seal and are acted upon by hydraulic fluid, are formed in a known manner and bring the bearing bodies 19, 21 into sealing contact with the side faces of the gear wheels. Two holes 23, 24 penetrate into the interior 11 at the level of the gearwheels from opposite sides of the housing, of which the hole 23 forms the high-pressure hole, the hole 24, the low-pressure hole. A gap 25 leads from the high-pressure bore 23 along the bearing bodies 19, 21 to the flat rear side of the same and builds up the high-pressure field 26 there, while the remaining part of the bearing body surface forms a low-pressure field 27, which is formed by a gap 28 along the bearing bodies with the low-pressure bore 23 connected is.

Durch die hydraulischen Kräfte entstehen Kräfte P1 und P2, welche die Zahnräder samt den Lagerkörpern in Richtung zur Niederdruckseite verschieben und dort im Bereich B1 und B2 an die Gehäuse-Innenwand drücken, Unterstützend hierbei wirken die Kräfte in den Druckfeldern 26 und 27, Die Haltekräfte P1 und P2 dürfen jedoch nicht zu groß sein, da sie dann jeder Bewegung der Lagerkörper entgegenstehen würden, so daß diese zuwenig oder auch zu fest an die Zahnradseitenflächen angepreßt werden. Dadurch wird das Anlaufen des Zahnradmotors erschwert. Die Größe der Haltekräfte ist proportional der Dicke der Lagerkörper. Durch eine Verringerung der Dicke der von den Druckfeldern beaufschlagten Lagerkörper 19, 21 werden diese Haltekräfte in erwünschter Weise verringert und die Beweglichkeit derselben verbessert. Dadurch werden volumetrische und mechanische Verluste gering gehalten. Wird dem Zahnradmotor über die Bohrung 24 unter Hochdruck stehendes Druckmittel zugeführt, so rotieren die Zahnräder und geben an der aus dem Gehäuse 10 austretenden Welle 30 ein Drehmoment ab, Am Wellendurchgang ist ein Dichtkörper angeordnet.The hydraulic forces create forces P1 and P2, which move the gears together with the bearing bodies in the direction of the low-pressure side and press them against the inner wall of the housing in areas B1 and B2. The forces in pressure fields 26 and 27 support this, the holding forces P1 and P2 must not be too large, however, since they would then oppose any movement of the bearing bodies, so that they are pressed too little or too tightly against the gear side surfaces. This makes starting the gear motor difficult. The size of the holding forces is proportional to the thickness of the bearing body. By reducing the thickness of the bearing bodies 19, 21 acted upon by the pressure fields, these holding forces are reduced in a desired manner and the mobility thereof is improved. This keeps volumetric and mechanical losses low. If pressure medium under high pressure is supplied to the gear motor via the bore 24, the gear wheels rotate and emit a torque on the shaft 30 emerging from the housing 10. A sealing body is arranged at the shaft passage.

Claims (5)

1. Pinion motor having two externally meshing pinions (14, 15), the shafts (16, 17) of which are mounted in bearing elements (18 to 21) arranged on both sides of the pinions, which bearing elements are located with slight axial and radial mobility in the interior space (11) of a housing (10), the thickness of the bearing elements (19, 21) on one side of the pinions being substantially less than the thickness of the other bearing elements and -pressed fluidtightly against the pinion side surfaces by fluid-stressed pressure regions (26, 27), characterized in that the bearing elements fill the interior space totally except for the play at least in the axial direction and that the pressure regions (26, 27) are constructed only on the bearing elements of lesser thickness.
2. Motor according to Claim 1, characterized in that the bearing elements are constructed as bushings.
3. Motor according to Claim 1, characterized in that the bearing elements are plates of somewhat spectacle-shaped construction.
4. Motor according to one of Claims 1 to 3, characterized in that the bearing elements of lesser thickness are approximately half as thick as the others.
5. Motor according to one of Claims 1 to 3, characterized in that the thickness of the bearing elements of lesser thickness corresponds to approximately 0.5 to 0.8 times the diameter of the shafts.
EP85904608A 1984-10-04 1985-09-26 Pinion motor Expired EP0199741B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3436375 1984-10-04
DE19843436375 DE3436375A1 (en) 1984-10-04 1984-10-04 GEAR MOTOR

Publications (2)

Publication Number Publication Date
EP0199741A1 EP0199741A1 (en) 1986-11-05
EP0199741B1 true EP0199741B1 (en) 1989-04-26

Family

ID=6247059

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85904608A Expired EP0199741B1 (en) 1984-10-04 1985-09-26 Pinion motor

Country Status (4)

Country Link
EP (1) EP0199741B1 (en)
JP (1) JPS62500314A (en)
DE (2) DE3436375A1 (en)
WO (1) WO1986002128A1 (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES2232221B1 (en) * 2002-02-07 2006-07-16 Pedro Roquet, S.A. PERFECTION OF OLEOHIDRAULIC MOTORS.

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3055307A (en) * 1959-10-23 1962-09-25 Thompson Ramo Wooldridge Inc Pressure yoke for pumps
GB1148651A (en) * 1965-04-24 1969-04-16 Armstrong Patents Co Ltd Improvements in and relating to gear pumps
FR1442211A (en) * 1965-08-09 1966-06-10 Bosch Gmbh Robert Delivery machine, in particular pump or hydraulic motor
US3474736A (en) * 1967-12-27 1969-10-28 Koehring Co Pressure loaded gear pump

Also Published As

Publication number Publication date
JPS62500314A (en) 1987-02-05
DE3436375A1 (en) 1986-04-10
WO1986002128A1 (en) 1986-04-10
DE3569787D1 (en) 1989-06-01
EP0199741A1 (en) 1986-11-05

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