EP0334040A1 - Gear machine (pump or motor) - Google Patents

Gear machine (pump or motor) Download PDF

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Publication number
EP0334040A1
EP0334040A1 EP19890103043 EP89103043A EP0334040A1 EP 0334040 A1 EP0334040 A1 EP 0334040A1 EP 19890103043 EP19890103043 EP 19890103043 EP 89103043 A EP89103043 A EP 89103043A EP 0334040 A1 EP0334040 A1 EP 0334040A1
Authority
EP
European Patent Office
Prior art keywords
gear
teeth
pump
motor
gear wheel
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
EP19890103043
Other languages
German (de)
French (fr)
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EP0334040B1 (en
Inventor
Gerhard Dipl.-Ing. Nonnenmacher
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
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0334040A1 publication Critical patent/EP0334040A1/en
Application granted granted Critical
Publication of EP0334040B1 publication Critical patent/EP0334040B1/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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C2/20—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with dissimilar tooth forms

Definitions

  • the invention relates to a gear machine according to the preamble of the main claim.
  • gear machines with the same number of teeth of the meshing gears, the torque arises alternately on the two gears due to the fluid pressure.
  • the distribution of the torque on the gears can be read directly from the line of engagement. While the torque of the driving gearwheel acts directly on its shaft, the torque of the driven gearwheel must first be converted to the driving gearwheel via the toothing, with mechanical losses inevitably occurring.
  • the gear machine according to the invention with the characterizing features of the main claim has the advantage that the hydraulic torque is divided between the two gears in such a way that the greatest possible proportion is generated directly on the driving gear. This improves the hydraulic-mechanical efficiency.
  • the gear machine has a driving gear 10 and a driven gear 11 in a known manner.
  • the driven gear 11 has two teeth more than the driving gear 10.
  • the pitch point W shifts from the center, and the engagement on the driven gear 11 moves in the direction of the tip circle, the torque of which is reduced , and on the driving wheel 10 in the direction of the root circle F, whereby its torque becomes larger. Thanks to the more direct flow of the throughput, the hydraulic-mechanical efficiency is improved.
  • the driving gear 10 is corrected for plus, the driven gear 11 for minus for this purpose.
  • the gears remain gearable even with different numbers of teeth.
  • the requirement for an identical tip diameter for both wheels limits the geometrical possibilities of involute teeth. Teeth on the grinding wheel and undercut tendency on the driven wheel form the limits.

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

Abstract

The gear machine (pump or motor) has two gear wheels with the same external diameter and the same root circle diameter, which intermesh with one another in external engagement and the driven gear wheel (11) of which has a larger number of teeth than the driving gear wheel (10). This is achieved by the one gear wheel having a negative correction and the other gear wheel having a positive correction, or by using suitable tooth system geometries which are not of involute design. <IMAGE>

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Zahnradmaschine nach der Gattung des Hauptanspruchs. Bei bekannten Zahnradmaschinen mit gleicher Zähnezahl der kämmenden Zahnräder entsteht das Drehmoment infolge des Flüssigkeitsdrucks wechselweise an den beiden Zahnrädern. Dieses ist für das jeweilige Zahnrad um so höher, je weiter der abdichtende Eingriff von seinem Kopfkreis entfernt ist. Die Aufteilung des Dreh­moments auf die Zahnräder kann so direkt aus der Eingriffslinie abgelesen werden. Während das Drehmoment des treibenden Zahnrads direkt an seiner Welle wirksam wird, muß das Drehmoment des getrie­benen Zahnrads erst noch über die Verzahnung auf das treibende Zahn­rad umgesetzt werden, wobei zwangsläufig mechanische Verluste ent­stehen.The invention relates to a gear machine according to the preamble of the main claim. In known gear machines with the same number of teeth of the meshing gears, the torque arises alternately on the two gears due to the fluid pressure. The higher the sealing engagement is from its tip circle, the higher for the respective gear. The distribution of the torque on the gears can be read directly from the line of engagement. While the torque of the driving gearwheel acts directly on its shaft, the torque of the driven gearwheel must first be converted to the driving gearwheel via the toothing, with mechanical losses inevitably occurring.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Zahnradmaschine mit den kennzeichnenden Merk­malen des Hauptanspruchs hat demgegenüber den Vorteil, daß das hydraulische Moment so auf die beiden Zahnräder aufgeteilt wird, daß ein möglichst hoher Anteil direkt am treibenden Zahnrad entsteht. Dadurch wird der hydraulisch-mechanische Wirkungsgrad verbessert.The gear machine according to the invention with the characterizing features of the main claim has the advantage that the hydraulic torque is divided between the two gears in such a way that the greatest possible proportion is generated directly on the driving gear. This improves the hydraulic-mechanical efficiency.

Dies gilt insbesondere für Betriebszustände, in denen mechanische Verluste vorherrschen, beispielsweise für den Anlaufvorgang von Zahnradmotoren.This applies in particular to operating states in which mechanical losses predominate, for example for the starting process of gear motors.

Zeichnungdrawing

Ein Ausführungsbeispiel der Erfindung ist in schematischer Dar­stellung in der Zeichnung wiedergegeben.An embodiment of the invention is shown in a schematic representation in the drawing.

Beschreibung der ErfindungDescription of the invention

Die Zahnradmaschine weist in bekannter Weise ein treibendes Zahnrad 10 und ein getriebenes Zahnrad 11 auf. Trotz unverändertem Achs­abstand und gleichem Kopfkreisdurchmesser K hat das getriebene Zahn­rad 11 zwei Zähne mehr als das treibende Zahnrad 10. Durch diesen Unterschied verschiebt sich der Wälzpunkt W aus der Mitte, und der Eingriff am getriebenen Zahnrad 11 wandert in Richtung Kopfkreis, wobei dessen Drehmoment kleiner wird, und am treibenden Rad 10 in Richtung Fußkreis F, wodurch dessen Drehmoment größer wird. Dank dem direkteren Fluß der durchgesetzten Leistung erhält man einen ver­besserten hydraulisch-mechanischen Wirkungsgrad.The gear machine has a driving gear 10 and a driven gear 11 in a known manner. Despite the unchanged center distance and the same tip circle diameter K, the driven gear 11 has two teeth more than the driving gear 10. As a result of this difference, the pitch point W shifts from the center, and the engagement on the driven gear 11 moves in the direction of the tip circle, the torque of which is reduced , and on the driving wheel 10 in the direction of the root circle F, whereby its torque becomes larger. Thanks to the more direct flow of the throughput, the hydraulic-mechanical efficiency is improved.

Bei Evolventenverzahnungen wird zu diesem Zweck das treibende Zahn­rad 10 nach plus, das getriebene Zahnrad 11 nach minus korrigiert. Dabei bleiben die Zahnräder auch bei unterschiedlicher Zähnezahl abwälzfähig. Durch die Forderung nach identischem Kopfkreisdurch­messer beider Räder sind die geometrischen Möglichkeiten der Evol­ventenverzahnung beschränkt. Spitz werdende Zähne am teibenden Rad und Unterschnittneigung am getriebenen Rad bilden die Grenzen.For involute gears, the driving gear 10 is corrected for plus, the driven gear 11 for minus for this purpose. The gears remain gearable even with different numbers of teeth. The requirement for an identical tip diameter for both wheels limits the geometrical possibilities of involute teeth. Teeth on the grinding wheel and undercut tendency on the driven wheel form the limits.

Besonders vorteilhaft ist die Kombination mit der Verwendung einer geeigneten, nichtevolventischen Verzahnung. Man erhält dadurch mehr Möglichkeiten für die Gestaltung der Zahnform. Zweckmäßig ist bei­ spielsweise als Eingriffslinie die Kombination zweier logarith­mischer Spiralen um die Radmittelpunkte. Mit einer solchen Ver­zahnung lassen sich Zähnezahldifferenzen von mindestens zwei bei üblichem Kopfkreisdurchmesser darstellen.The combination with the use of a suitable, non-volatile toothing is particularly advantageous. This gives you more options for the design of the tooth shape. It is useful for for example, as a line of engagement, the combination of two logarithmic spirals around the wheel centers. With such a toothing, differences in the number of teeth of at least two with the usual tip diameter can be represented.

Claims (4)

1. Zahnradmaschine (Pumpe oder Motor) mit im Außeneingriff kämmenden Zahnrädern (10, 11) mit gleichem Außendurchmesser und ungeführ gleichem Fußkreisdurchmesser, dadurch gekennzeichnet, daß das getriebene Zahnrad (11) trotz unverändertem Achsabstand eine größere Anzahl von Zähnen hat als das treibende Zahnrad (10), das eine Plus­korrektur aufweist.1. Gear machine (pump or motor) with meshing external gears (10, 11) with the same outer diameter and roughly the same root diameter, characterized in that the driven gear (11) has a larger number of teeth than the driving gear (despite the unchanged center distance) 10), which has a plus correction. 2. Maschine nach Anspruch 1, dadurch gekennzeichnet, daß bei evol­ventenverzahnten Zahnrädern die unterschiedliche Zähnezahl durch Minuskorrektur des getriebenen Rades und durch Pluskorrektur des treibenden Rades verwirklicht wird.2. Machine according to claim 1, characterized in that in involute toothed gears the different number of teeth is realized by minus correction of the driven wheel and by plus correction of the driving wheel. 3. Maschine nach Anspruch 1, dadurch gekennzeichnet, daß die Ein­griffslinie (E) nichtevolventisch ist.3. Machine according to claim 1, characterized in that the line of engagement (E) is non-volatile. 4. Maschine nach Anspruch 1 und/oder 3, dadurch gekennzeichnet, daß die Eingriffslinie (E) aus logarithmischen oder archimedischen Spiralen um die Radmittelpunkte zusammengesetzt ist.4. Machine according to claim 1 and / or 3, characterized in that the line of engagement (E) is composed of logarithmic or Archimedean spirals around the wheel centers.
EP89103043A 1988-03-23 1989-02-22 Gear machine (pump or motor) Expired - Lifetime EP0334040B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3809721A DE3809721C1 (en) 1988-03-23 1988-03-23
DE3809721 1988-03-23

Publications (2)

Publication Number Publication Date
EP0334040A1 true EP0334040A1 (en) 1989-09-27
EP0334040B1 EP0334040B1 (en) 1992-08-26

Family

ID=6350448

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89103043A Expired - Lifetime EP0334040B1 (en) 1988-03-23 1989-02-22 Gear machine (pump or motor)

Country Status (2)

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EP (1) EP0334040B1 (en)
DE (2) DE3809721C1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2211893B (en) * 1987-11-04 1992-01-02 Bosch Gmbh Robert Hydraulic gear machine (pump or motor)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4242217C2 (en) * 1992-12-15 1995-07-20 Bosch Gmbh Robert Gear machine (pump or motor)
DE4320489C2 (en) * 1993-06-21 2001-06-28 Bosch Gmbh Robert Gear machine (pump or motor)
US10989190B2 (en) 2015-12-04 2021-04-27 Audi Ag External gear pump

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH376776A (en) * 1960-03-14 1964-04-15 Wiggermann Georg Gear displacement machine
US3303792A (en) * 1964-04-20 1967-02-14 Roper Ind Inc Gear pump with trapping reliefs
DE2242269B2 (en) * 1971-08-28 1980-06-12 Shimadzu Seisakusho Ltd., Kyoto (Japan) Gear pump or motor
DE3246685A1 (en) * 1981-12-22 1983-06-30 Sullair Technology AB, 11653 Stockholm ROTORS FOR A SCREW ROTOR MACHINE
EP0149446A2 (en) * 1983-12-14 1985-07-24 Boge Kompressoren Otto Boge GmbH &amp; Co. KG Rotary piston compressor

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2421891A1 (en) * 1974-05-07 1975-11-20 Bosch Gmbh Robert GEAR MOTOR

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH376776A (en) * 1960-03-14 1964-04-15 Wiggermann Georg Gear displacement machine
US3303792A (en) * 1964-04-20 1967-02-14 Roper Ind Inc Gear pump with trapping reliefs
DE2242269B2 (en) * 1971-08-28 1980-06-12 Shimadzu Seisakusho Ltd., Kyoto (Japan) Gear pump or motor
DE3246685A1 (en) * 1981-12-22 1983-06-30 Sullair Technology AB, 11653 Stockholm ROTORS FOR A SCREW ROTOR MACHINE
EP0149446A2 (en) * 1983-12-14 1985-07-24 Boge Kompressoren Otto Boge GmbH &amp; Co. KG Rotary piston compressor

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2211893B (en) * 1987-11-04 1992-01-02 Bosch Gmbh Robert Hydraulic gear machine (pump or motor)

Also Published As

Publication number Publication date
EP0334040B1 (en) 1992-08-26
DE58902105D1 (en) 1992-10-01
DE3809721C1 (en) 1989-06-01

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