EP2406496A2 - Machine hydraulique à engrenage - Google Patents

Machine hydraulique à engrenage

Info

Publication number
EP2406496A2
EP2406496A2 EP10705827A EP10705827A EP2406496A2 EP 2406496 A2 EP2406496 A2 EP 2406496A2 EP 10705827 A EP10705827 A EP 10705827A EP 10705827 A EP10705827 A EP 10705827A EP 2406496 A2 EP2406496 A2 EP 2406496A2
Authority
EP
European Patent Office
Prior art keywords
pressure
gears
gear machine
bearing
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.)
Withdrawn
Application number
EP10705827A
Other languages
German (de)
English (en)
Inventor
Marc LÄTZEL
Michael Wilhelm
Dietmar Schwuchow
Guido Bredenfeld
Stefan Cerny
Sebastian Tetzlaff
Klaus Griese
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 EP2406496A2 publication Critical patent/EP2406496A2/fr
Withdrawn legal-status Critical Current

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
    • 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
    • F04C2/16—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 helical teeth, e.g. chevron-shaped, screw type
    • 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
    • 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
    • F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
    • 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
    • F04C15/0088—Lubrication
    • 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
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • F04C2240/54—Hydrostatic or hydrodynamic bearing assemblies specially adapted for rotary positive displacement pumps or compressors

Definitions

  • the invention relates to a hydraulic gear machine according to the preamble of patent claim 1.
  • a gear machine is shown with a housing in which two intermeshing and mounted in bearing bushes or bearing bodies gears are arranged, wherein the housing is closed with a first and second housing cover each end face.
  • the gears are mounted slidably axially each with two axial surfaces between the bearing bodies and radially in each case via a bearing shaft received in the bearing bodies.
  • hydraulic and mechanical forces act on the gears in the same gear longitudinal axis in each case.
  • the counterforce on the gears is applied via attacking on the bearing shafts piston.
  • the pistons are slidably received approximately coaxially to the toothed wheel longitudinal axis in a between the first housing cover and the housing arranged intermediate cover and abut with a first piston end face on a pointing in the direction of the first housing cover shaft end face of the bearing shafts and are acted upon via a second piston end face in each case with pressure.
  • the counterforce is applied to the first bearing body via a pressure field formed between the bearing body and the intermediate cover.
  • a disadvantage of this solution is that the entire package of bearing bodies and gears is pressed onto the second housing cover of the gear machine, whereby the second housing cover and the housing are loaded very high and uneven. By compressing the gears and the bearing body occurs a fairly high wear between the axial surfaces of the gears and the bearing bodies.
  • the application of the counterforce on the bearing shafts and the bearing body requires a high device complexity with a variety of components.
  • the object of the present invention is to provide a hydraulic gear machine, which is constructed device-simple and with a small number of components and has a low wear.
  • a gear machine has a housing for receiving two meshing gears. These are mounted slidably axially with axial surfaces between housed in the housing bearing bodies and radially, each with a bearing shaft accommodated in the bearing bodies.
  • a gear acts in the operation of the gear machine an axial force component of a force resulting from the operation of hydraulic and mechanical forces resulting force in a same axial direction.
  • At least one pressure field is provided between at least one axial surface of a gear lying in the effective direction of the axial force component and the bearing bodies adjoining the at least one axial surface.
  • This solution has the advantage that a force acting against the Axialkraftkomponente counterforce can be applied to the gears without additional components by the pressure field. Furthermore, the force acting as a contact force Axialkraftkomponente the gears is reduced by the pressure field, whereby the sliding friction between the gears and lying in the effective direction of the Axialkraftkomponente bearing bodies reduced and wear is minimized.
  • the gears are helically toothed.
  • a pressure field is provided in each case between the axial surfaces of the toothed wheels lying in the direction of action of the axial force component and the sliding surfaces of the bearing body which lie opposite the axial surfaces.
  • the pressure fields can simply be designed as pressure pockets.
  • a first pressure groove is concentrically encircling a first bearing eye and a second pressure groove a circle inserted around a second bearing eye in the sliding surface of the bearing in the direction of the Axialkraftkomponente bearing body, whereby different effective surfaces of the pressure grooves are realized.
  • the pressure grooves via connecting grooves with the high pressure of the gear machine in pressure medium connection.
  • the pressure force acting in the pressure grooves can be coupled to the operating conditions of the gear machine.
  • the pressure pockets are introduced in the direction of action of Axialkraftkomponente lying axial surfaces of the gears.
  • the pressure pockets are easily manufactured along a peripheral portion formed around the respective bearing shaft of the gears, whereby a small leakage gap occurs.
  • the pressure pockets are formed circumferentially around the respective bearing shaft of the gears.
  • At least one pressure pocket is widened by tooth pocket portions introduced into the tooth end faces of the teeth of the toothed wheel.
  • the pressure oil supply of the pressure pockets can be done via the adjacent bearing body, the pressure pockets are for example at high pressure of the gear machine in fluid communication.
  • Figure 1 in a longitudinal section a simplified representation of a gear machine
  • Figure 2 is a side view of a simplified representation of a package of bearing bodies and gears of the gear machine of Figure 1;
  • FIG. 3 is a longitudinal sectional view of a simplified representation of bearing bodies and gears of the gear machine according to a first embodiment
  • Figure 4 is a plan view of the bearing body of Figure 3.
  • Figure 5 is a plan view of the gears of the gear machine according to a second embodiment. Description of the embodiments
  • FIG. 1 shows a longitudinal section of a designed as a gear machine 1 hydraulic working machine according to an embodiment is shown.
  • This has a machine housing 2, which is closed by means of two housing cover 4 and 6.
  • the right in Figure 1 housing cover 6 of the gear machine 1 is penetrated by a first bearing shaft 8, on softer a first gear 10 is disposed within the machine housing 2.
  • the first gear 10 is connected to a second gear 12 via a helical gear 14 into engagement, wherein the gear 12 is rotatably mounted on a second bearing shaft 16.
  • the first and second bearing shaft 8 and 16 are each guided in two plain bearings 18, 20 and 22, 24.
  • the right in Figure 1 sliding bearings 20, 24 are received in a bearing body 26 and the left in Figure 1 slide bearings 18, 22 in a bearing body 28.
  • the gears 10 and 12 are mounted in the axial direction in each case via a first axial surface 30 and 32 respectively on the second right in Figure 1 bearing body 26 and a respective second axial surface 34 and 36 on the left bearing body 28 slidably. Sliding surfaces between the gears 10, 12 and the bearing bodies 26, 28 may be provided with a sliding coating, such as M0S 2 , graphite or PTFE to reduce friction.
  • the bearing bodies 26 and 28 each have an end face 38 or 40 towards the housing covers 6 and 4, respectively.
  • the housing cover 4, 6 are aligned by centering bolts 42 on the machine housing 2. Between the housing covers 4 and 6 and the machine housing 2, a housing seal 44 is arranged. Furthermore, an axial field seal 46 is respectively introduced into the end faces 38 and 40 of the bearing bodies 26 and 28 for the separation of a high-pressure region of the gearwheel machine 1. A shaft sealing ring 48 seals the passage of the first bearing shaft 8 through the housing cover 6 on the right in FIG.
  • FIG. Figure 2 shows a side view of a simplified representation of the package of gears 10 and 12 and bearing bodies 26 and 28 to explain the occurring in the gear machine 1 of Figure 1 hydraulic and acting substantially by the helical gear 14 mechanical forces.
  • a force component of a hydraulic force acts on both gears 10, 12 in the same axial direction in the figure 2 to the left.
  • a driving gear which in FIG. 2 is the upper gear 10
  • a driven gear which is the lower gear 12 in FIG. 2
  • the hydraulic and mechanical force components result in a corresponding axial force component 47, 49 on both toothed wheels 10, 12 in the same direction (to the left in FIG. 2), but with a different amount.
  • FIG. 3 shows in a longitudinal sectional view a simplified illustration of the bearing bodies 26, 28 and the toothed wheels 10, 12 according to a first exemplary embodiment of the gear machine 1 from FIG.
  • a pressure field between the lying in the effective direction of the Axialkraftkomponenten 47, 49 axial surfaces 34 and 36 of the respective gears 10 and 12 and the axial surfaces 34 and 36 opposite sliding surfaces 50 and 52 of the bearing body 28 provided.
  • the bearing bodies 26, 28 can be constructed in two parts as in FIG. The pressure field is limited by respective pressure grooves 54 and 56 introduced into the sliding surfaces 50 and 52 and the respective axial surfaces 34 and 36, respectively.
  • Figure 4 discloses in a plan view, the sliding surfaces 50, 52 of the spectacle-shaped bearing body 28 of Figure 3.
  • the first pressure groove 54 is circumferentially about an upper in Figure 4 bearing eye 62 is inserted into the sliding surface.
  • the second pressure groove 56 is formed around a lower circle around a lower bearing eye 64 substantially in the high pressure region of the gear machine 1 of FIG.
  • the pressure grooves 54, 56 are via radial grooves 66 to the high pressure of the gear machine 1 in fluid communication.
  • FIG. 5 shows a plan view of the axial surfaces 34, 36 of the gears 10, 12 according to a second embodiment of the gear machine 1 of Figure 1.
  • the pressure field is not as shown in Figure 3 in the bearing body 28 introduced pressure grooves 54, 56, but bounded by in each case in the axial surfaces 34 and 36 of the gears 10 and 12 introduced pressure pockets 68 and 70, respectively.
  • the lower in the figure 5 pressure pocket 70 of the gear 12 is formed as an annular groove which is circumferentially introduced into the axial surface 36 between toothed end faces 72 of teeth 74 of the gear 12 and an outer circumferential surface of the bearing shaft 16.
  • pressure pocket 68 of the gear 10 has in addition to a pressure pocket 70 corresponding annular groove in the toothed end faces 72 introduced Zahntaschenabismee 76, whereby the Pressure pocket 68 is thus introduced over a large area in the axial surface 34.
  • the pressure pocket 68 is then radially bounded by a wall 78 running around the circumference of the toothed wheel 10.
  • the pressure pockets 68, 70 are in pressure fluid communication with the high pressure of the gear machine 1 from FIG. 1, for example via connecting grooves in the adjacent bearing body 28 (see FIG. 1).
  • the pressure pockets 68, 70 of FIG. 4 are not incorporated in the gears 10, 12 but encircling only a partial circle and having a larger radial width.
  • the production could be simplified and a leakage gap can be reduced, which would lead to lower hydraulic losses.
  • Axialspalt- and Axialkraftkompensation are independent of the type of bearing elements used and is therefore applicable to all, suitable for the axial sealing of gear machines components. The same applies to the type of gearing and its parameters. Such Axialspalt- and Axialkraftkompensation can be used both in external and internal gear machines.
  • the gear machine can be used as a gear pump or motor.
  • a gear machine with a housing for receiving two intermeshing gears. These are axially received with axial surfaces between housing bearing bodies and radially slidably mounted in each case with a bearing shaft received in the bearing bodies.
  • an axial force component of these forces acts on the gears in a same axial direction.
  • This axial force component is a pressure field between at least one lying in the effective direction of the Axialkraftkomponente axial surface of a gear and the adjacent to the at least one axial surface bearing body.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Gear Transmission (AREA)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)
  • Hydraulic Motors (AREA)

Abstract

Machine à engrenage qui comporte un carter dans lequel sont logées deux roues dentées qui s'engrènent. Ces roues sont montées glissantes axialement grâce à des surfaces axiales entre des corps de palier logés dans le carter et radialement grâce à un arbre de palier logé dans les corps de palier. Le fonctionnement de la machine à engrenage provoque des forces hydrauliques et mécaniques, une composante axiale de ces forces agissant sur chacune des deux roues dans un même sens axial. Pour contrer cette composante de force axiale, un champ de pression est situé entre au moins une surface axiale d'une des roues dentées, s'étendant dans la direction d'action de la composante de force axiale, et le corps de palier adjacent à la surface axiale.
EP10705827A 2009-03-12 2010-02-25 Machine hydraulique à engrenage Withdrawn EP2406496A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009012916A DE102009012916A1 (de) 2009-03-12 2009-03-12 Hydraulische Zahnradmaschine
PCT/EP2010/001164 WO2010102723A2 (fr) 2009-03-12 2010-02-25 Machine hydraulique à engrenage

Publications (1)

Publication Number Publication Date
EP2406496A2 true EP2406496A2 (fr) 2012-01-18

Family

ID=42557931

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10705827A Withdrawn EP2406496A2 (fr) 2009-03-12 2010-02-25 Machine hydraulique à engrenage

Country Status (7)

Country Link
US (1) US20120156080A1 (fr)
EP (1) EP2406496A2 (fr)
JP (1) JP5502909B2 (fr)
CN (1) CN102362073A (fr)
BR (1) BRPI1011690A2 (fr)
DE (1) DE102009012916A1 (fr)
WO (1) WO2010102723A2 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11773845B2 (en) 2019-03-08 2023-10-03 Shimadzu Corporation Helical gear pump and helical gear motor

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2837827B1 (fr) * 2013-06-27 2016-06-01 Sumitomo Precision Products Co., Ltd. Dispositif hydraulique
JP5783305B2 (ja) * 2013-09-18 2015-09-24 ダイキン工業株式会社 ギヤ流体装置
CN105298835A (zh) * 2015-11-17 2016-02-03 天津百利机械装备集团有限公司中央研究院 一种动静压承载圆弧齿轮油泵
DE102016225869A1 (de) * 2016-12-21 2018-06-21 Robert Bosch Gmbh Außenzahnradpumpe für ein Abwärmerückgewinnungssystem
WO2020053720A1 (fr) * 2018-09-13 2020-03-19 Casappa S.P.A. Machine volumétrique à engrenages
CN109322821B (zh) * 2018-10-09 2023-07-04 宿迁学院 一种用于消除齿轮泵径向力的组合结构
DE102018222516A1 (de) * 2018-12-20 2020-06-25 Audi Ag Antriebseinrichtung für ein Kraftfahrzeug
FR3125849B1 (fr) * 2021-07-27 2024-11-15 Eaton Intelligent Power Ltd Commande de pression sur un palier lisse
IT202300014397A1 (it) * 2023-07-10 2025-01-10 Marzocchi Pompe S P A Macchina idraulica reversibile ad ingranaggio a dentatura elicoidale con sistema idraulico bilaterale per il bilanciamento di forze assiali.
US20250180016A1 (en) * 2023-11-30 2025-06-05 Eaton Intelligent Power Limited Bearing for Pump

Citations (2)

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FR2564931A1 (fr) * 1984-05-22 1985-11-29 Malfit Jean Generateur recepteur hydraulique a haute pression pour la transmission de puissance
EP1988290A1 (fr) * 2006-02-20 2008-11-05 Shimadzu Mectem, Inc. Pompe à engrenages

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US1706829A (en) * 1928-05-28 1929-03-26 Joseph Mercadante Pump
US2997960A (en) * 1957-12-20 1961-08-29 Kimijima Takehiko Gear pump
DE2315630A1 (de) * 1973-03-29 1974-10-17 Bosch Gmbh Robert Zahnradmaschine
DE2610827A1 (de) * 1976-03-15 1977-09-29 Bosch Gmbh Robert Zahnradmaschine (pumpe oder motor)
AT355916B (de) * 1976-07-13 1980-03-25 Akzo Nv Zahnradpumpe mit verminderter leistungsaufnahme zum foerdern viskoser fluessigkeiten
FR2698413B1 (fr) * 1992-11-26 1995-01-27 Jean Malfit Générateur-récepteur hydraulique pour la transmission de puissance comportant un équilibrage hydraulique perfectionné.
JPH1182323A (ja) * 1997-09-11 1999-03-26 Hitachi Ltd 燃料ポンプ
ITBO20010540A1 (it) 2001-09-07 2003-03-07 Mario Antonio Morselli Perfezionamenti in una pompa volumetrica rotativa
JP3897568B2 (ja) * 2001-11-02 2007-03-28 株式会社ジェイテクト ギヤポンプ及びこれを用いたパワーステアリング装置
EP1576290B1 (fr) * 2002-12-19 2013-02-20 Concentric Hof GmbH Machine a roues dentees comprenant des plaques laterales axiales
US6902382B2 (en) * 2003-09-11 2005-06-07 Matthew Peter Christensen Gear motor start up control
CN201180643Y (zh) * 2008-02-29 2009-01-14 徐州科源液压有限公司 具有压力补偿功能的高压齿轮泵

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2564931A1 (fr) * 1984-05-22 1985-11-29 Malfit Jean Generateur recepteur hydraulique a haute pression pour la transmission de puissance
EP1988290A1 (fr) * 2006-02-20 2008-11-05 Shimadzu Mectem, Inc. Pompe à engrenages

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11773845B2 (en) 2019-03-08 2023-10-03 Shimadzu Corporation Helical gear pump and helical gear motor

Also Published As

Publication number Publication date
JP5502909B2 (ja) 2014-05-28
WO2010102723A2 (fr) 2010-09-16
DE102009012916A1 (de) 2010-09-16
BRPI1011690A2 (pt) 2016-03-22
WO2010102723A3 (fr) 2011-09-22
JP2012519799A (ja) 2012-08-30
US20120156080A1 (en) 2012-06-21
CN102362073A (zh) 2012-02-22

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