WO1986002128A1 - Pinion motor - Google Patents

Pinion motor Download PDF

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Publication number
WO1986002128A1
WO1986002128A1 PCT/DE1985/000336 DE8500336W WO8602128A1 WO 1986002128 A1 WO1986002128 A1 WO 1986002128A1 DE 8500336 W DE8500336 W DE 8500336W WO 8602128 A1 WO8602128 A1 WO 8602128A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing bodies
thickness
bearing
pinions
motor according
Prior art date
Application number
PCT/DE1985/000336
Other languages
German (de)
French (fr)
Inventor
Hayno Rustige
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
Priority to DE8585904608T priority Critical patent/DE3569787D1/en
Publication of WO1986002128A1 publication Critical patent/WO1986002128A1/en

Links

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 bearing bodies are of the same thickness, and there are usually on both end faces of the bearing bodies facing away from the gears, fluid-pressurized e pressure fields which bring the bearing bodies into sealing contact with the gear side surfaces .
  • mechanical forces are created which press the bearing bodies against the housing recess receiving them at a location on the low-pressure side.
  • These holding forces can be so great that they prevent any movement of the bearing body, i.e. 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 arrangement according to the invention with the characterizing features of the main claim has the advantage that the holding forces mentioned are lower, since they are proportional to the thickness of the bearing body, the mobility of the bearing body is better, which also the volumetric and mechanical efficiency better and the mechanical losses become smaller, mobility of the bearing body is particularly necessary if the gearwheels 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, 1 3.
  • the interior is formed by two intersecting bores, so that it has the cross-sectional shape of an eight, see FIG. 2, in the interior 11 there are two gears 1 4, 15, which are in external engagement with each other, the shafts 16, 17 of the gears 14, 1 5 s ind in book-shaped bearing bodies 1 8, 1 9 b between. 20, 21 stored.
  • These bearing bodies are in axial as in arranged radially slightly movable in the interior 11 of the housing 10, it is essential that the thickness of the bearing body 19, 21 is significantly less than the thickness of the bearing body 18, 20 on the opposite side e.
  • pressure fields 26, 27 which are limited by a seal and are acted upon by hydraulic fluid are formed in a known manner, which pressurize the bearing bodies 19, 21 in sealing contact with the gear side surfaces bring.
  • 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 thereof 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 against the gear side surfaces too little or too tightly. 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 become in it desirably reduced and improved mobility thereof. This keeps volumetric and mechanical losses low. If the gear motor is fed via the bore 24 under the high pressure medium, the gear wheels rotate and emit a torque on the shaft 30 emerging from the housing 10.
  • a sealing body 31 is arranged at the shaft passage.

Landscapes

  • 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

ZahnradmotorGear motor
Stand der TechnikState of the art
Die Erfindung betrifft einen Zahnradmotor nach der Gattung des Hauptanspruchs, Bei derartigen bekannten Zahnradmotoren sind die Lagerkörper gleich dick ausgebildet, und meist befinden sich auf beiden den Zahnrädern abgewandten Stirnseiten dieser Lagerkörper flüs s igkeitsbeaufschlagt e 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 Anlaufverhalt en des Zahnradmotors beeinträchtigen und sogar dessen Verschleiß vergrößern. Vorteile der ErfindungThe invention relates to a gear motor according to the preamble of the main claim, In such known gear motors, the bearing bodies are of the same thickness, and there are usually on both end faces of the bearing bodies facing away from the gears, fluid-pressurized e pressure fields 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 are created which press the bearing bodies against the housing recess receiving them at a location on the low-pressure side. These holding forces can be so great that they prevent any movement of the bearing body, i.e. 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. Advantages of the invention
Die erfindungsgemäße Anordnung mit den kennzeichnenden Merkmalen des Hauptanspruchs hat demgegenüber den Vorteil, daß 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 the holding forces mentioned are lower, since they are proportional to the thickness of the bearing body, the mobility of the bearing body is better, which also the volumetric and mechanical efficiency better and the mechanical losses become smaller, mobility of the bearing body is particularly necessary if the gearwheels 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 make it possible to develop the features specified in the main claim,
Zeichnungdrawing
Ein Aus fuhrungsbeispiel der Erfindung ist in der Zeichnung dargestellt. Diese zeigt in Figur 1 einen Längsschnitt durch einen Zahnradmotor, in Figur 2 eine Prinzipskizze,From an exemplary 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, 1 3 verschlossen ist, Der Innenraum ist durch zwei sich überschneidende Bohrungen gebildet, so daß er die Querschnittsform einer Acht hatj siehe hierzu Figur 2, Im Innenraum 11 befinden sich zwei Zahnräder 1 4 , 15, die im Außeneingriff miteinander in Verbindung stehen, Die Wellen 16, 17 der Zahnräder 14, 1 5 s ind in buch s enförmi gen Lagerkörpern 1 8 , 1 9 b zw . 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 Seit e . Auf der den Zahnrädern 1 4 , 1 5 abgewandt en Se it e 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 Lagerkörperflache 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, 1 3. The interior is formed by two intersecting bores, so that it has the cross-sectional shape of an eight, see FIG. 2, in the interior 11 there are two gears 1 4, 15, which are in external engagement with each other, the shafts 16, 17 of the gears 14, 1 5 s ind in book-shaped bearing bodies 1 8, 1 9 b between. 20, 21 stored. These bearing bodies are in axial as in arranged radially slightly movable in the interior 11 of the housing 10, it is essential that the thickness of the bearing body 19, 21 is significantly less than the thickness of the bearing body 18, 20 on the opposite side e. On the gear wheels 1 4, 1 5 facing away from the bearing bodies 19, 21, pressure fields 26, 27 which are limited by a seal and are acted upon by hydraulic fluid are formed in a known manner, which pressurize the bearing bodies 19, 21 in sealing contact with the gear side surfaces bring. 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 thereof 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 er wünschter Weise verringert und die Beweglichkeit derselben verbessert. Dadurch werden volumetrische und mechanische Verluste gering gehalten. Wird dem Zahnradmotor über die Bohrung 24 unt er Hochdruck s t ehende s Druckmitt el zuge führt, so rotieren die Zahnräder und geben an der aus dem Gehäuse 10 austretenden Welle 30 ein Drehmoment ab, Am Wellendurchgang ist ein Dichtkörper 31 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 against the gear side surfaces too little or too tightly. 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 become in it desirably reduced and improved mobility thereof. This keeps volumetric and mechanical losses low. If the gear motor is fed via the bore 24 under the high pressure medium, the gear wheels rotate and emit a torque on the shaft 30 emerging from the housing 10. A sealing body 31 is arranged at the shaft passage.

Claims

Ansprüche Expectations
1. Zahnradnotor mit zwei im Außeneingriff kämmenden Zahnrädern ( 1 4 , 15), deren Wellen (16, 17) in beidseits der Zahnräder angeordneten Lagerkörpern (18 bis 21) gelagert sind, die sich geringfügig axial und radialverschiebbar in einem Innenraum (11) eines Gehäuses (10) befinden und durch flüs sigkeit sbeaufschlagt e Druckfelder (26, 27) dichtend gegen, die Zahnradseitenflächen gedrückt werden, dadurch gekennzeichnet, daß die Dicke der Lagerkörper (19, 21) auf einer Seite der Zahnräder wesentlich geringer ist als die Dicke der anderen Lagerkörper und daß die Druckfelder (26, 27) nur an den weniger dicken Lagerkörpern ausgebildet sind,1. Gear motor with two meshing external gears (1 4, 15), the shafts (16, 17) of which are mounted in bearing bodies (18 to 21) arranged on both sides of the gears, which are slightly axially and radially displaceable in an interior (11) of one Housing (10) are located and pressurized by liquid s e pressurized fields (26, 27) against, the gear side surfaces are pressed, characterized in that the thickness of the bearing body (19, 21) on one side of the gears is substantially less than the thickness of the other bearing body and that the pressure fields (26, 27) are formed only on the less thick bearing bodies,
2. Motor nach Anspruch 1, dadurch gekennzeichnet, daß die Lagerkörper als Buchsen ausgebildet sind.2. Motor according to claim 1, characterized in that the bearing bodies are designed as bushings.
3. Motor nach Anspruch 1, dadurch gekennzeichnet, daß die Lagerkörper etwa brillenförmig ausgebildete Platten sind. 3. Motor according to claim 1, characterized in that the bearing bodies are approximately glasses-shaped plates.
4. Motor nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß die weniger dicken Lagerkörper etwa halb so dick sind wie die anderen.4. Motor according to one of claims 1 to 3, characterized in that the less thick bearing bodies are approximately half as thick as the others.
5. Motor nach einem der Ansprüche 1 bis 3. dadurch gekennzeichnet, daß die Dicke der weniger dicken Lagerkörper das etwa 0,5 bis 0,8fache des Durchmessers der Wellen entspricht. 5. Motor according to one of claims 1 to 3, characterized in that the thickness of the less thick bearing body corresponds to about 0.5 to 0.8 times the diameter of the shafts.
PCT/DE1985/000336 1984-10-04 1985-09-26 Pinion motor WO1986002128A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE8585904608T DE3569787D1 (en) 1984-10-04 1985-09-26 Pinion motor

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19843436375 DE3436375A1 (en) 1984-10-04 1984-10-04 GEAR MOTOR
DEP3436375.0 1984-10-04

Publications (1)

Publication Number Publication Date
WO1986002128A1 true WO1986002128A1 (en) 1986-04-10

Family

ID=6247059

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE1985/000336 WO1986002128A1 (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.

Citations (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
FR1442211A (en) * 1965-08-09 1966-06-10 Bosch Gmbh Robert Delivery machine, in particular pump or hydraulic motor
GB1148651A (en) * 1965-04-24 1969-04-16 Armstrong Patents Co Ltd Improvements in and relating to gear pumps
DE1809156A1 (en) * 1967-12-27 1969-07-24 Hydraulic Unit Specialities Co Gear pump

Patent Citations (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
DE1809156A1 (en) * 1967-12-27 1969-07-24 Hydraulic Unit Specialities Co Gear pump

Also Published As

Publication number Publication date
EP0199741B1 (en) 1989-04-26
EP0199741A1 (en) 1986-11-05
DE3436375A1 (en) 1986-04-10
DE3569787D1 (en) 1989-06-01
JPS62500314A (en) 1987-02-05

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