US20120156080A1 - Hydraulic Toothed Wheel Machine - Google Patents

Hydraulic Toothed Wheel Machine Download PDF

Info

Publication number
US20120156080A1
US20120156080A1 US13/256,072 US201013256072A US2012156080A1 US 20120156080 A1 US20120156080 A1 US 20120156080A1 US 201013256072 A US201013256072 A US 201013256072A US 2012156080 A1 US2012156080 A1 US 2012156080A1
Authority
US
United States
Prior art keywords
toothed wheel
pressure
wheel machine
axial
toothed
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.)
Abandoned
Application number
US13/256,072
Other languages
English (en)
Inventor
Marc Laetzel
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
Assigned to ROBERT BOSCH GMBH reassignment ROBERT BOSCH GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: TETZLAFF, SEBASTIAN, GRIESE, KLAUS, SCHWUCHOW, DIETMAR, LAETZEL, MARC, WILHELM, MICHAEL, BREDENFELD, GUIDO, CERNY, STEFAN
Publication of US20120156080A1 publication Critical patent/US20120156080A1/en
Abandoned legal-status Critical Current

Links

Images

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 toothed wheel machine in accordance with the preamble of patent claim 1 .
  • EP 1 291 526 A2 shows a toothed wheel machine having a housing in which two intermeshing toothed wheels supported in bearing bushes or bearing bodies are arranged, the housing being closed at the ends by a first and a second housing cover respectively.
  • the toothed wheels are each supported in a sliding manner axially by two axial surfaces between the bearing bodies and radially by respective bearing shafts accommodated in the bearing bodies.
  • hydraulic and mechanical forces act on the toothed wheels along the same toothed wheel longitudinal axis in each case.
  • a counter-force is applied to the toothed wheels and to the first bearing body.
  • This counter-force is larger than the hydraulic and mechanical forces, with the result that the first bearing body is pressed against the toothed wheels, the toothed wheels are pressed against the second bearing body, and the second bearing body is pressed against the second housing cover. All the resultant forces on the bearing bodies and the toothed wheels thus act in the direction of the second housing cover.
  • the counter-force on the toothed wheels is applied via pistons acting on the bearing shafts.
  • the pistons are accommodated in a sliding manner, approximately coaxially with respect to the toothed wheel longitudinal axis, in an intermediate cover arranged between the first housing cover and the housing and rest by means of a first piston end face against a shaft end face of the bearing shafts which faces in the direction of the first housing cover and are each subjected to pressure by way of a second piston end face.
  • the counter-force is applied to the first bearing body by way of a pressure field formed between the bearing body and the intermediate cover.
  • a toothed wheel machine has a housing for accommodating two intermeshing toothed wheels. These are supported in a sliding manner axially by axial surfaces between bearing bodies accommodated in the housing and radially by respective bearing shafts accommodated in the bearing bodies.
  • an axial force component of a force resulting from hydraulic and mechanical forces arising during operation acts on each toothed wheel in the same axial direction.
  • At least one pressure field is provided between at least one axial surface of a toothed wheel, said axial surface lying in the direction of action of the axial force component, and the bearing bodies adjoining the at least one axial surface.
  • This solution has the advantage that a counter-force acting against the axial force component can be applied to the toothed wheels by means of the pressure field, without additional components. Moreover, the pressure field reduces the axial force component acting as a contact pressure force on the toothed wheels, thereby reducing the sliding friction between the toothed wheels and the bearing bodies lying in the direction of action of the axial force component and minimizing wear.
  • the toothed wheels are preferably helically toothed.
  • a pressure field is provided between each of those axial surfaces of the toothed wheels which lie in the direction of action of the axial force component and those sliding surfaces of the bearing body which lie opposite the axial surfaces.
  • the pressure fields can simply be designed as pressure pockets.
  • the sliding surface of the bearing body lying in the direction of action of the axial force component preferably has introduced into it a first pressure groove, running concentrically around a first bearing eye, and a second pressure groove, spanning a partial circle around a second bearing eye, and different effective areas of the pressure grooves are thereby obtained.
  • the pressure grooves are in pressure-medium communication with the high pressure of the toothed wheel machine via connection grooves. This enables the pressure force acting in the pressure grooves to be linked to the operating conditions of the toothed wheel machine.
  • the pressure pockets are introduced into those axial surfaces of the toothed wheels which lie in the direction of action of the axial force component.
  • the pressure pockets are formed around and along a portion of the circumference of the respective bearing shafts of the toothed wheels and, as a result, the leakage gap that forms is small too.
  • the pressure pockets are formed so as to run around the respective bearing shafts of the toothed wheels.
  • At least one pressure pocket is preferably enlarged by tooth pocket sections introduced into the tooth end faces of the teeth of the toothed wheel.
  • the pressure pockets can be supplied with pressure oil via the adjoining bearing body, the pressure pockets being in pressure-medium communication with the high pressure of the toothed wheel machine, for example.
  • FIG. 1 shows a simplified illustration of a toothed wheel machine in a longitudinal section
  • FIG. 2 shows a simplified illustration of an assembly of bearing bodies and toothed wheels of the toothed wheel machine from FIG. 1 , in a side view;
  • FIG. 3 shows a simplified illustration of bearing bodies and toothed wheels of the toothed wheel machine according to a first illustrative embodiment in a longitudinal section;
  • FIG. 4 shows a plan view of the bearing body from FIG. 3 ;
  • FIG. 5 shows a plan view of the toothed wheels of the toothed wheel machine according to a second illustrative embodiment.
  • FIG. 1 shows a hydraulic machine, embodied as a toothed wheel machine 1 , according to one illustrative embodiment in a longitudinal section.
  • This machine has a machine housing 2 , which is closed by means of two housing covers 4 and 6 .
  • Housing cover 6 of the toothed wheel machine 1 which is on the right in FIG. 1 , is penetrated by a first bearing shaft 8 , on which a first toothed wheel 10 is arranged within the machine housing 2 .
  • the first toothed wheel 10 is in engagement with a second toothed wheel 12 by way of helical toothing 14 , toothed wheel 12 being arranged on a second bearing shaft 16 for conjoint rotation therewith.
  • the first and second bearing shafts 8 and 16 are each guided in two plain bearings 18 , 20 and 22 , 24 respectively.
  • the plain bearings 20 , 24 on the right in FIG. 1 are accommodated in a bearing body 26
  • the plain bearings 18 , 22 on the left in FIG. 1 are accommodated in a bearing body 28 .
  • the toothed wheels 10 and 12 are each supported in a sliding manner in the axial direction by respective first axial surfaces 30 and 32 on the second bearing body 26 (on the right in FIG. 1 ) and by respective second axial surfaces 34 and 36 on the bearing body 28 on the left.
  • sliding surfaces between the toothed wheels 10 , 12 and the bearing bodies 26 , 28 can be provided with an antifriction coating, such as MoS 2 , graphite or PTFE.
  • an antifriction coating such as MoS 2 , graphite or PTFE.
  • Respective end faces 38 and 40 of the bearing bodies 26 and 28 face the housing covers 6 and 4 .
  • the housing covers 4 , 6 are aligned on the machine housing 2 by means of centering pins 42 .
  • a housing seal 44 is arranged between the housing covers 4 and 6 and the machine housing 2 .
  • Respective axial field seals 46 are furthermore inserted into the end faces 38 and 40 of the bearing bodies 26 and 28 to separate a high-pressure zone from a low-pressure zone of the toothed wheel machine 1 .
  • a shaft seal ring 48 seals off the first bearing shaft 8 where it passes through the housing cover 6 on the right in FIG. 1 .
  • FIG. 2 shows a simplified illustration, in side view, of the assembly of toothed wheels 10 and 12 and bearing bodies 26 and 28 in order to illustrate the hydraulic forces that arise during operation and the mechanical forces that essentially act due to the helical toothing in the toothed wheel machine 1 from FIG. 1 .
  • a force component of a hydraulic force acts in the same axial direction on both toothed wheels 10 , 12 , toward the left in FIG. 2 .
  • a driving toothed wheel which is the upper toothed wheel 10 in FIG. 2
  • a driven toothed wheel which is the lower toothed wheel 12 in FIG.
  • the toothed wheels 10 and 12 subjected to axial force components 47 , 49 are each supported by axial surfaces 34 and 36 , respectively, on the bearing body 28 on the left in FIG. 2 .
  • the right-hand bearing body 26 is not subject to the axial force components acting on the toothed wheels 10 , 12 .
  • a counter-force is applied to the toothed wheels, this being indicated by dashed arrows in FIG. 2 .
  • FIG. 3 shows a simplified illustration of the bearing bodies 26 , 28 and the toothed wheels 10 , 12 according to a first illustrative embodiment of the toothed wheel machine 1 from FIG. 1 in a longitudinal section.
  • a pressure field is provided between those axial surfaces 34 , 36 of the toothed wheels 10 , 12 which lie in the direction of action of the axial force components 47 , and those sliding surfaces 50 , 52 of the bearing body 28 which lie opposite the axial surfaces 34 , 36 .
  • the bearing bodies 26 , 28 can be of two-part construction, as illustrated in FIG. 3 .
  • the pressure field is delimited by pressure grooves 54 and 56 , respectively, introduced into the sliding surfaces 50 and 52 and by the respective axial surfaces 34 and 36 .
  • Pressure forces 58 , 60 acting on bearing body 28 and the toothed wheels 10 , 12 by virtue of the pressure field are illustrated in simplified form by double arrows in FIG. 3 , with bearing body 28 having been moved to the left to enable the pressure forces 58 , 60 to be illustrated more clearly.
  • the design of the pressure grooves 54 , 56 can be seen in the following figure, FIG. 4 .
  • FIG. 4 discloses the sliding surfaces 50 , 52 of the spectacle-shaped bearing body 28 from FIG. 3 in a plan view.
  • the first pressure groove 54 is introduced into the sliding surface so as to run around a bearing eye 62 at the top in FIG. 4 .
  • the second pressure groove 56 is formed substantially in the high pressure zone of the toothed wheel machine 1 from FIG. 1 , spanning a partial circle around a lower bearing eye 64 .
  • the pressure grooves 54 , 56 are in pressure-medium communication with the high pressure of the toothed wheel machine 1 via radial grooves 66 .
  • the pressure forces 58 , 60 are applied to the toothed wheels 10 , 12 and bearing body 28 by means of the respective pressure grooves 54 and 56 introduced into the sliding surfaces 50 and 52 in FIGS. 3 and 4 .
  • the pressure forces 58 , 60 counteract the axial force components 47 , 49 , thereby reducing the sliding friction and wear between the toothed wheels 10 , 12 and bearing body 28 .
  • the size of the pressure grooves 54 , 56 is designed in such a way that the axial force components 47 , 49 applied to the toothed wheels 10 , 12 are thus substantially compensated for by the pressure forces 58 , 60 , and the toothed wheels 10 , 12 are thus supported approximately hydrostatically.
  • the axial force component 47 at the top in FIG. 3 is larger than the lower axial force component 49 , for which reason the upper pressure groove 54 from FIG. 4 is designed with a larger area than the lower pressure groove 56 .
  • FIG. 5 shows a plan view of the axial surfaces 34 , 36 of the toothed wheels 10 , 12 in accordance with a second illustrative embodiment of the toothed wheel machine 1 from FIG. 1 .
  • the pressure field is not delimited by pressure grooves 54 , 56 introduced into bearing body 28 as in FIG. 3 but by respective pressure pockets 68 and 70 introduced into the axial surfaces 34 and 36 of the toothed wheels 10 and 12 .
  • the pressure pocket 70 in toothed wheel 12 is designed as an annular groove which is introduced around the axial surface 36 between tooth end faces 72 of teeth 74 of toothed wheel 12 and an outer circumferential surface of bearing shaft 16 .
  • the pressure pocket 68 in toothed wheel 10 In addition to an annular groove corresponding to pressure pocket 70 , the pressure pocket 68 in toothed wheel 10 , said pocket being at the top in FIG. 5 , has tooth pocket sections 76 introduced into the tooth end faces 72 , pressure pocket 68 thus being introduced into the axial surface 34 over a large area. Pressure pocket 68 is then delimited radially by a wall 78 running around the periphery of toothed wheel 10 .
  • the pressure pockets 68 , 70 are in pressure-medium communication with the high pressure of the toothed wheel machine 1 from FIG. 1 via connection grooves in the adjoining bearing body 28 (see FIG. 1 ), for example.
  • the pressure forces 58 , 60 from FIG. 3 are introduced in the area of action on bearing body 28 of the toothed wheels 10 , 12 subjected to axial force components 47 , 49 . Since the pressure pocket 68 at the top in FIG. 4 has a larger axial pressure application area than the lower pressure pocket 70 , the pressure force acting on the upper toothed wheel 10 is greater.
  • the pressure pockets 68 , 70 from FIG. 4 could be introduced into the toothed wheels 10 , 12 in such a way that they do not run around but merely span a partial circle and have a larger radial width. This would be a way, for example, of simplifying manufacture and reducing the size of a leakage gap, which would result in smaller hydraulic losses.
  • the toothed wheel machine can be used as a gear pump or motor.
  • the disclosure is of a toothed wheel machine having a housing for accommodating two intermeshing toothed wheels. These are supported in a sliding manner axially by axial surfaces between bearing bodies accommodated in the housing and radially by respective bearing shafts accommodated in the bearing bodies. Hydraulic and mechanical forces arise during the operation of the toothed wheel machine, and an axial force component of these forces acts in the same axial direction on each toothed wheel. To counteract this axial force component, a pressure field is provided between at least one axial surface of a toothed wheel, said axial surface lying in the direction of action of the axial force component, and the bearing body adjoining the at least one axial surface.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Hydraulic Motors (AREA)
  • Gear Transmission (AREA)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)
US13/256,072 2009-03-12 2010-02-25 Hydraulic Toothed Wheel Machine Abandoned US20120156080A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102009012916A DE102009012916A1 (de) 2009-03-12 2009-03-12 Hydraulische Zahnradmaschine
DE102009012916.2 2009-03-12
PCT/EP2010/001164 WO2010102723A2 (de) 2009-03-12 2010-02-25 Hydraulische zahnradmaschine

Publications (1)

Publication Number Publication Date
US20120156080A1 true US20120156080A1 (en) 2012-06-21

Family

ID=42557931

Family Applications (1)

Application Number Title Priority Date Filing Date
US13/256,072 Abandoned US20120156080A1 (en) 2009-03-12 2010-02-25 Hydraulic Toothed Wheel Machine

Country Status (7)

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

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9366250B1 (en) * 2013-06-27 2016-06-14 Sumitomo Precision Products Co., Ltd. Hydraulic device
CN114026327A (zh) * 2018-12-20 2022-02-08 奥迪股份公司 用于机动车的动力设备
EP3936725A4 (de) * 2019-03-08 2022-03-23 Shimadzu Corporation Schraubenradpumpe oder -motor
US11448212B2 (en) 2018-09-13 2022-09-20 Casappa S.P.A. Geared volumetric machine
US20230033416A1 (en) * 2021-07-27 2023-02-02 Eaton Intelligent Power Limited Controlling pressure on a journal bearing

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
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

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1706829A (en) * 1928-05-28 1929-03-26 Joseph Mercadante Pump
US2997960A (en) * 1957-12-20 1961-08-29 Kimijima Takehiko Gear pump
US4343602A (en) * 1976-07-13 1982-08-10 Akzo, N.V. Gear wheel pump with reduced power requirement
US6902382B2 (en) * 2003-09-11 2005-06-07 Matthew Peter Christensen Gear motor start up control

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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)
FR2564931B1 (fr) * 1984-05-22 1986-12-05 Malfit Jean Generateur recepteur hydraulique a haute pression pour la transmission de puissance
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
WO2004057193A1 (de) * 2002-12-19 2004-07-08 Haldex Hydraulics Gmbh Zahnradmaschine mit axialen seitenplatten
KR101012465B1 (ko) * 2006-02-20 2011-02-08 시마즈멕템가부시기가이샤 기어펌프
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 (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1706829A (en) * 1928-05-28 1929-03-26 Joseph Mercadante Pump
US2997960A (en) * 1957-12-20 1961-08-29 Kimijima Takehiko Gear pump
US4343602A (en) * 1976-07-13 1982-08-10 Akzo, N.V. Gear wheel pump with reduced power requirement
US6902382B2 (en) * 2003-09-11 2005-06-07 Matthew Peter Christensen Gear motor start up control

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
English Language Machine Translation of WO 2004/057193 *

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9366250B1 (en) * 2013-06-27 2016-06-14 Sumitomo Precision Products Co., Ltd. Hydraulic device
US11448212B2 (en) 2018-09-13 2022-09-20 Casappa S.P.A. Geared volumetric machine
CN114026327A (zh) * 2018-12-20 2022-02-08 奥迪股份公司 用于机动车的动力设备
EP3936725A4 (de) * 2019-03-08 2022-03-23 Shimadzu Corporation Schraubenradpumpe oder -motor
US20220112894A1 (en) * 2019-03-08 2022-04-14 Shimadzu Corporation Helical gear pump and helical gear motor
US11773845B2 (en) * 2019-03-08 2023-10-03 Shimadzu Corporation Helical gear pump and helical gear motor
US20230033416A1 (en) * 2021-07-27 2023-02-02 Eaton Intelligent Power Limited Controlling pressure on a journal bearing
US11905949B2 (en) * 2021-07-27 2024-02-20 Eaton Intelligent Power Limited Controlling pressure on a journal bearing

Also Published As

Publication number Publication date
BRPI1011690A2 (pt) 2016-03-22
DE102009012916A1 (de) 2010-09-16
JP2012519799A (ja) 2012-08-30
JP5502909B2 (ja) 2014-05-28
WO2010102723A3 (de) 2011-09-22
WO2010102723A2 (de) 2010-09-16
CN102362073A (zh) 2012-02-22
EP2406496A2 (de) 2012-01-18

Similar Documents

Publication Publication Date Title
US8979518B2 (en) Hydraulic toothed wheel machine
US20120156080A1 (en) Hydraulic Toothed Wheel Machine
CN101723006A (zh) 双轴套履带链卡盘
US9371910B2 (en) Piston for a radial piston machine
JP5006838B2 (ja) 減速装置
US20100196186A1 (en) Gear pump
CN102748432A (zh) 一种减速机
JP2000205142A (ja) 液圧式容積形機械、特に容積形ポンプ
EP1291526B2 (de) Zahnradförderpumpe
EP3460229B1 (de) Intern gekrümmter hydraulikmotor mit geringer drehzahl und hohem drehmoment mit drehmomentabgabe mittels rotation des gehäuses
US6887055B2 (en) Positive-displacement rotary pump
DE202013104531U1 (de) Hydraulikpumpe und Elektromotor mit abgedichteter Direktverbindung
JP6526371B1 (ja) 内接ギヤポンプ
US6716011B2 (en) Hydraulic pump utilizing floating shafts
CN106838035A (zh) 带抗扭的制动器件的径向活塞机
US20080159898A1 (en) Vane Pump
CN210396989U (zh) 一种定量径向配油泵
CN102338024A (zh) 内曲线径向柱塞式液压马达
CN104334880B (zh) 具有填充件的内齿轮泵
EP4073384A1 (de) Verbesserte hülsenanordnung und verdrängerpumpe, die diese hülsenanordnung umfasst
WO2018096941A1 (ja) トロイダル無段変速機
US6524087B1 (en) Hydrostatic planetary rotation machine having an orbiting rotary valve
RU2477388C2 (ru) Шестеренный насос
RU2262619C2 (ru) Шестеренная гидромашина
US20060042459A1 (en) High efficiency hydraulic machine with radial cylinders

Legal Events

Date Code Title Description
AS Assignment

Owner name: ROBERT BOSCH GMBH, GERMANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:LAETZEL, MARC;WILHELM, MICHAEL;SCHWUCHOW, DIETMAR;AND OTHERS;SIGNING DATES FROM 20111027 TO 20111222;REEL/FRAME:027811/0364

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION