EP2059672A2 - Pompes et moteurs à engrenages télescopiques à longue durée de vie - Google Patents

Pompes et moteurs à engrenages télescopiques à longue durée de vie

Info

Publication number
EP2059672A2
EP2059672A2 EP07814743A EP07814743A EP2059672A2 EP 2059672 A2 EP2059672 A2 EP 2059672A2 EP 07814743 A EP07814743 A EP 07814743A EP 07814743 A EP07814743 A EP 07814743A EP 2059672 A2 EP2059672 A2 EP 2059672A2
Authority
EP
European Patent Office
Prior art keywords
motor
wear
gear
pump
telescoping pump
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Withdrawn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
EP07814743A
Other languages
German (de)
English (en)
Other versions
EP2059672A4 (fr
Inventor
James A. Ii. O'brien
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.)
Limo Reid Inc
Original Assignee
Hybra-Drive Systems LLC
Hybra Drive Systems LLC
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 Hybra-Drive Systems LLC, Hybra Drive Systems LLC filed Critical Hybra-Drive Systems LLC
Publication of EP2059672A2 publication Critical patent/EP2059672A2/fr
Publication of EP2059672A4 publication Critical patent/EP2059672A4/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Withdrawn legal-status Critical Current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
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
    • 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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/185—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by varying the useful pumping length of the cooperating members in the axial direction
    • 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
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/101—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with a crescent-shaped filler element, located between the inner and outer intermeshing members

Definitions

  • the power plant section 11 of the system 10 includes a plurality of accessory drives including, but not limited to, a motor generator 22, an air conditioning compressor 24, and a heat pump 26.
  • the motor generator 22 is connected to a power maintenance module 28, which is in turn connected to a battery pack 30.
  • the heat pump 26 is in communication with a heater core 32 and both the heat pump 26 and the heater core 32 are in fluid communication with a cooling water source 34 for the engine 12.
  • the air conditioning compressor 24 is in communication with a heat exchanger 36.
  • the accessory drives 22, 24, and 26 are preferably run by respective electric or hydraulic motors. Alternatively, the accessory drives 22, 24, and 26 are selectively mechanically clutched to the engine 12.
  • An accumulator 38 is in fluid communication with the high pressure conduit 20 on the outlet of the pump/motor 16. The accumulator 38 serves as a reservoir for high pressure hydraulic fluid and maintains high pressure in the system 10, such as by being charged with a high pressure gas or the like (not shown), as will be appreciated by those skilled in the art.
  • conduits 50 and 52 are connected to a brake override device
  • a conduit 92 is in fluid communication with an inlet of the check valve 84 and an outlet of the check valve 86.
  • the conduit 92 is also in fluid communication with the high pressure outlet conduit 56.
  • a conduit 94 is in fluid communication with an inlet of the check valve 86 and an inlet of the check valve 88.
  • the conduit 94 is also in fluid communication with the low pressure source of hydraulic fluid 18.
  • a conduit 96 is in fluid communication with an outlet of the check valve 88 and an inlet of the check valve 90.
  • the conduit 96 is also in fluid communication with the low pressure outlet conduit 56.
  • a conduit 98 is in fluid communication with an outlet of the check valve 84 and an outlet of the check valve 90.
  • the conduit 98 is also in fluid communication with the high pressure conduit 20.
  • An external gear 124 that is substantially circular in cross section is adapted to be placed atop the upper surface 113 of the base portion 111 wherein a curved outer surface of the gear 124 is adjacent the respective curved inner surfaces of the outer flanges 116 and 118.
  • the external gear 124 includes a plurality of teeth 126 formed on an inner surface thereof. When placed on the upper surface 113, the gear 124 is fixed axially between the outer flanges 118 and the inner flange 120.
  • the downwardly extending flange 144 cooperates with the upwardly extending inner flange 120 to divide the interior of the external gear into an inlet chamber and discharge chamber of the motor 100 and the upper end cap 106 is attached to the base portion 104 to enclose the housing 102.
  • the flanges 120 and 144 extend radially between the teeth 126 and the teeth 130 to form the inlet chamber on one side of the flanges and the discharge chamber on the other side of the flanges.
  • an external source of pressure such as hydraulic fluid from an external hydraulic pump, compressed air from an air compressor or the like, provides a volume flow to the ports 107 to spin the gears 124 and 128 and produce an output torque on the shaft 134.
  • the internal gear 128 will move along the axis of the shaft 134 in order to vary the output horsepower of the motor 100.
  • the motor 100 may be advantageously utilized to control output rpm under widely changing output loads including, but not limited to automotive vehicles, turrets, large machinery, earth movers, large well drills, ships, farm equipment, or the like.
  • the pump 100 When the unit 100 is configured as a pump and a prime mover, such as the engine 12 of Figs. Ia-Ie, rotates the shaft 134 at a lower speed or with a lower torque, the pump 100 will react to the reduced input speed or input torque by varying its output based on the internal pressures in the pump housing 102. In this condition, the output port 107 will create a higher back pressure in the discharge chamber, and the internal gear 128 will move along the axis of the shaft 134 to a point along the axis where the gear 128 is at or near equilibrium to continue operation.
  • a prime mover such as the engine 12 of Figs. Ia-Ie
  • the shafts 222 and 224 extend in opposite axial directions and the shaft 224 is greater in length than the shaft 222.
  • a first seal sleeve 226 having internal teeth receives the first gear 214 and a second seal sleeve 228 having internal teeth receives an end of the second gear 218.
  • a second thrust plate 242 is attached to an upper surface 205 of the first end cap 204 by a plurality of fasteners 244, such as high strength bolts or the like.
  • the plate 242 includes an aperture for receiving a free end of the shaft 224 and a larger aperture for receiving and locating the first seal sleeve 226 adjacent the upper surface of the first end cap 204.
  • the free end of the shaft 224 extends through the aperture in the plate 242, threadably engages a pair of nuts 246 at the step and is rotatably supported by a bearing 248, such as a ball bearing, a roller bearing or the like.
  • the pump 200 will react to the reduced input speed or input torque by varying its output based on the internal pressures in the pump housing 202.
  • the output port 252 or 254 will create a higher back pressure in the recess 212, and the second gear 218 will move along the axis of the shaft 224 to a point along the axis where the gear 218 is at or near equilibrium to continue operation.
  • the pump 200 therefore, can vary from a maximum output or displacement where the gear 218 is substantially adjacent the fitting 230 to a minimum displacement where the gear 218 is substantially adjacent the lower thrust plate 242.
  • High pressure hydraulic fluid will then flow from the motors 76a-76d, through the lower ports 78a-78d, through the conduit 96, and, if the pressure in the conduit 96 is greater than the conduit 98, through the check valve 90 and into the conduit 98, where the high pressure hydraulic fluid flows to the conduit 20 and recharges the accumulator 38.
  • the hydraulic hybrid powertrain system 10 in accordance with the present invention advantageously providing an uncomplicated and straightforward control methodology and a very responsive control means for the system 10 by virtue of the fact that output torque response from the motors 76a-76d, once their displacement is increased, is very quick.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Abstract

L'invention concerne une pompe à engrenages télescopiques comprenant un écrou, une rondelle Belleville, une plaque d'usure, un boîtier d'étanchéité, un ressort étanche, un engrenage droit comprenant un lobe d'usure, une bague d'étanchéité et un chemin de drainage de carter, un arbre, une couronne comprenant un lobe d'usure, une bague d'étanchéité, ainsi qu'un chemin de drainage de carter, un joint d'étanchéité, un ensemble écrou comprenant une rondelle Belleville et un écrou, et une plaque de pression. L'ensemble assure une pression à un fluide afin de maintenir une étanchéité dans un ensemble pompe/moteur télescopique au cours du fonctionnement. Le lobe d'usure réduit l'usure tout en maintenant une pression du fluide.
EP07814743.6A 2006-09-08 2007-09-07 Pompes et moteurs à engrenages télescopiques à longue durée de vie Withdrawn EP2059672A4 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US82498106P 2006-09-08 2006-09-08
PCT/US2007/077852 WO2008031012A2 (fr) 2006-09-08 2007-09-07 Pompes et moteurs à engrenages télescopiques à longue durée de vie

Publications (2)

Publication Number Publication Date
EP2059672A2 true EP2059672A2 (fr) 2009-05-20
EP2059672A4 EP2059672A4 (fr) 2014-05-14

Family

ID=39158083

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07814743.6A Withdrawn EP2059672A4 (fr) 2006-09-08 2007-09-07 Pompes et moteurs à engrenages télescopiques à longue durée de vie

Country Status (5)

Country Link
EP (1) EP2059672A4 (fr)
JP (1) JP2010502895A (fr)
CN (1) CN101535633B (fr)
BR (1) BRPI0716188A2 (fr)
WO (1) WO2008031012A2 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102410212B (zh) * 2011-12-06 2015-01-21 张意立 一种宝塔形弹簧补偿内外齿轮泵
CZ304353B6 (cs) * 2012-11-13 2014-03-19 Enetrans S.R.O. Zubové čerpadlo nebo motor
CN105317545A (zh) * 2014-07-13 2016-02-10 徐建宁 双连杆液压发动机
SG11202000958UA (en) * 2017-08-21 2020-02-27 Macnaught Pty Ltd Reel braking system
CN107726669A (zh) * 2017-11-18 2018-02-23 山东阿尔普尔节能装备有限公司 一种变频补焓超低温空气源热泵
DE102017223675B4 (de) * 2017-12-22 2023-01-26 Eckerle Technologies GmbH Fluidfördereinrichtung
DE102018133680A1 (de) * 2018-12-28 2020-07-02 Schwäbische Hüttenwerke Automotive GmbH Rotationspumpe mit axialer Kompensation, Auslassdichtung für eine Pumpe sowie vormontierte Pumpeneinheit

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1853430A (en) * 1930-02-20 1932-04-12 Viking Pump Company Rotary pump
JPS5776284A (en) * 1980-10-28 1982-05-13 Canon Inc Gear pump
JPS59175618U (ja) * 1983-05-12 1984-11-24 日産自動車株式会社 内燃機関用オイルポンプ
JPS61223282A (ja) * 1985-03-26 1986-10-03 Honda Motor Co Ltd オイルポンプ装置
JPS6276294U (fr) * 1985-10-31 1987-05-15
JPH01159479A (ja) * 1987-12-14 1989-06-22 Mazda Motor Corp 自動車用ポンプ構造
US4940394A (en) * 1988-10-18 1990-07-10 Baker Hughes, Inc. Adjustable wearplates rotary pump
JPH0419375A (ja) * 1990-05-11 1992-01-23 Mitsubishi Materials Corp 内接型オイルモータ及び内接型オイルポンプ
JPH11247766A (ja) * 1998-02-27 1999-09-14 Mikuni Adec Corp トロコイドポンプ
JP2002195147A (ja) * 2000-12-25 2002-07-10 Eaton Hydraulics Co Ltd 油圧モータ
FR2835300B1 (fr) * 2002-01-29 2004-02-27 Valeo Volant flexible pour embrayage, en particulier pour vehicule automobile
CN2549210Y (zh) * 2002-05-20 2003-05-07 杭州萧山云祥工程机械厂 双轴向密封补偿式高压齿轮泵
WO2005100780A2 (fr) * 2004-04-09 2005-10-27 Hybra-Drive Systems, Llc Pompe/moteur a capacite variable

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
No further relevant documents disclosed *
See also references of WO2008031012A2 *

Also Published As

Publication number Publication date
BRPI0716188A2 (pt) 2013-11-12
JP2010502895A (ja) 2010-01-28
CN101535633A (zh) 2009-09-16
WO2008031012A3 (fr) 2008-09-04
EP2059672A4 (fr) 2014-05-14
WO2008031012A2 (fr) 2008-03-13
CN101535633B (zh) 2013-05-29

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