EP0091347A1 - Mehrfache Zahnradpumpe - Google Patents

Mehrfache Zahnradpumpe Download PDF

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Publication number
EP0091347A1
EP0091347A1 EP83400618A EP83400618A EP0091347A1 EP 0091347 A1 EP0091347 A1 EP 0091347A1 EP 83400618 A EP83400618 A EP 83400618A EP 83400618 A EP83400618 A EP 83400618A EP 0091347 A1 EP0091347 A1 EP 0091347A1
Authority
EP
European Patent Office
Prior art keywords
pump
orifice
casing
working fluid
return
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
EP83400618A
Other languages
English (en)
French (fr)
Other versions
EP0091347B1 (de
Inventor
Jean-Claude Muller
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.)
DBA SA
Original Assignee
DBA SA
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 DBA SA filed Critical DBA SA
Publication of EP0091347A1 publication Critical patent/EP0091347A1/de
Application granted granted Critical
Publication of EP0091347B1 publication Critical patent/EP0091347B1/de
Expired 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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/02—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for several machines or pumps connected in series or in parallel
    • 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
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • F04C11/001—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle
    • 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
    • F04C2/18—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 similar tooth forms

Definitions

  • the present invention relates to multiple gear pumps comprising a first pump part supplying equipment with a large flow of working fluid, and at least a second pump part supplying at least one other equipment with a low flow of working fluid , in particular, although not exclusively, for agricultural vehicles.
  • a multiple gear pump 100 comprising a first pump or front pump 1 supplying equipment 3, such as lifting installations, with a large working fluid flow, and at least a second pump or rear pump 2 supplying a servomechanism, such as a power steering 4, with a small flow of working fluid.
  • the first and second pumps 1 and 2 of the driven pinion type meshing with a idler pinion, are rotated by a shaft 5 capable of being coupled to a drive motor M.
  • the first and second pumps 1 and 2 deliver working fluid under pressure through two separate outlet ports 6 and 7, respectively.
  • the multiple pump comprises an orifice 8 for admitting the working fluid from a tank or a reservoir 90, the casing of the pump being provided with first and second passages 9 and 10, respectively, of the working fluid in from the tank 90 to the first and second pumps 1 and 2. Due mainly to the locations of the various equipment in the machine or the vehicle using the double gear pump, the high-speed return 11 takes place directly at the tank 90 , while the return at a lower flow rate from the particular equipment, such as the power steering 4, takes place directly in the pump via a return orifice 12 and a fluid return passage 13 downstream of the orifice admission 8.
  • the return passage 13 communicates with the second supply passage 10 of the second pump 2, immediately upstream of the latter.
  • This arrangement has the drawback that the second pump or rear pump 2 operates in fact in a closed circuit, from which it follows a rapid heating of the working fluid passing through this second pump and the associated equipment, with the related problems.
  • the object of the present invention is precisely to present a multiple gear pump of the general type described above making it possible to avoid the operation of the second pump in a closed circuit, thereby limiting the overheating. working fluid flowing through the latter, at the cost of a simple arrangement of low manufacturing cost.
  • the gear pump of the type comprising a casing, a first and at least a second gear pump, arranged in the casing and each comprising a driven pinion and a idler pinion, means for connecting the driven pinions to a drive member, a working fluid intake port in the casing, first and second working fluid supply passages between the intake port and the first and second pumps, respectively, first and second working fluid outlet ports connected to the first and second pumps, respectively, at least one working fluid return port in the housing, and at least one fluid return passage work establishing communication between the return port and the intake port, is characterized in that the return path opens into the first working fluid supply passage to the first pump.
  • Another object of the present invention is to provide a gear pump of the type defined above allowing, without obstructing the manufacturing costs, to simply carry out the return path by using the latter in addition to recirculate any leaks of working fluid. at the bearings of the driven and idler gears of the first and second pumps.
  • the idler gears of the first and second pumps have hollow axes, the return passage of working fluid passing through these hollow axes.
  • the pump also comprises recirculation passages connecting the ends of the bearings of the pinions driven to the return passage.
  • a double gear pump 100 has the same general layout as the pump of Figure 1 except, however, that, in accordance with the present invention, the return passage 13 this time no longer communicates with the second passage 10 for supplying the working fluid to the second pump 2, but is extended, within the body of the pump, by an axial passage 13 ′ which opens into the first passage 9 supplying the working fluid to the first pump 1.
  • the return from the equipment 4 is carried out this time immediately upstream of the first pump 1 in the working fluid circulation path 9 and 6 at high speed from this first pump, the second pump 2 receiving the working fluid at low pressure directly from the supply pipe coming from the tank 90, which thus eliminates the problems of heating of the working fluid in the loop of the second pump.
  • the extension part 13 ′ of the return passage 13 can be provided, like the second supply passage, 10 in the body of the pump housing.
  • the gear pump comprises idler pinions with hollow axes, the return passage 13 'passing through these hollow axes, as will be understood from the following description given with reference with Figures 3 to 6.
  • first and second pumps 1 and 2 respectively comprising a driven pinion 101 and 102 and a idler pinion 111 and 112.
  • the driven pinions 101 and 102 are coaxial and driven by a shaft 50 in two parts coupled by a sleeve, intermediate 51.
  • the two idler gears 111 and 112 are coaxial.
  • Each pump 1 and 2 is arranged in a housing part provided with bearing elements for the pinions, the two housing parts being joined with the interposition of an intermediate part and kept assembled between two end flanges 14 and 15, l drive shaft 50 projecting externally from the flange: 14 for its connection to the drive motor M.
  • the inlet 8 and the first outlet 6 of the first pump 1 are arranged opposite in the opposite side walls of the housing part of the first pump , axially the second inlet passage 10 extending / through the casing part intermediate between the casing parts of the first and second. pumps up to the latter, the second outlet orifice 7 of the second pump 2 being formed in the end flange 15 adjacent to the latter.
  • the axes of the idler gears 111 and 112 are each formed with a through bore 113 and 114, respectively, establishing a continuous passage, via an internal chamber 115 in the part of the intermediate housing separating the two pumps between an idler end chamber 116 formed in the inner face of the end flange 15 and an idler gear end chamber 117 similarly formed in the inner face of the opposite end flange 14.
  • chambers 118 and 119 at the end of the axes of the driven pinions collecting the leaks at the bearings of the driven pinions.
  • the chamber 118 communicates with the chamber 116 by an internal passage 120 formed in the flange 15.
  • the chamber 119 communicates with the chamber 117 by an internal passage 121 formed in the end flange 14.
  • the passages 120 and 121 thus allow recovery of internal leaks in the return passage 13 '.
  • a passage 122 formed in the end flange 15, communicates the return orifice 12, also formed in this flange 15, with the chamber 116 of the shaft end idler gear of the second pump to constitute the first part 13 of the path of return of working fluid in the pump.
  • a passage 123 formed in the end flange 14, connects the chamber 117 of the idler pin end end with a housing 124 communicating with the first supply passage 9 of the working fluid to the first pump l, immediately downstream of the intake orifice 8, thus completing the return path 13, 13 'in the pump body from the return orifice 12, the passage 122, the bores 114 and 113 of the pinions. two pumps, and the passage 123 in the flange 14.
  • this arrangement ensures the uniformity of temperature of the working fluid circuit as well as the return to suction of internal leaks from the pump.
  • the pump assembly can comprise more than two adjacent pumps with mutually aligned pinions, the internal leaks from the bearings of the driven pinions being recovered in chambers such as 115 formed in the intermediate casing parts between two adjacent pumps via formed conduits. in these intermediate parts.
  • the passages formed in the end flanges consist of holes using closure plugs, they can be produced by lost wax molding.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
EP19830400618 1982-03-30 1983-03-24 Mehrfache Zahnradpumpe Expired EP0091347B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8205409 1982-03-30
FR8205409A FR2524575B1 (fr) 1982-03-30 1982-03-30 Pompe multiple a engrenages

Publications (2)

Publication Number Publication Date
EP0091347A1 true EP0091347A1 (de) 1983-10-12
EP0091347B1 EP0091347B1 (de) 1985-06-19

Family

ID=9272547

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19830400618 Expired EP0091347B1 (de) 1982-03-30 1983-03-24 Mehrfache Zahnradpumpe

Country Status (3)

Country Link
EP (1) EP0091347B1 (de)
DE (1) DE3360299D1 (de)
FR (1) FR2524575B1 (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0787260A4 (de) * 1994-03-22 1997-08-06
US5842848A (en) * 1997-01-03 1998-12-01 Knowles; Frederick W. Compact high-volume gear pump
EP2634430A1 (de) 2012-02-28 2013-09-04 Maag Pump Systems AG Getriebepumpenanordnung

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2830290B1 (fr) * 2001-10-01 2004-01-02 Coutier Moulage Gen Ind Pompe double a engrenages, et installation utilisant une telle pompe
JP5361074B2 (ja) * 2009-11-20 2013-12-04 ジヤトコ株式会社 ヘリカルギヤポンプ

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB572967A (en) * 1942-04-15 1945-10-31 Pump Engineering Service Corp Improvements in gear-wheel pumps
FR916746A (fr) * 1941-08-19 1946-12-13 Plessey Co Ltd Perfectionnements aux pompes hydrauliques, compresseurs à plusieurs étages et appareils analogues
GB665808A (en) * 1949-11-26 1952-01-30 Snecma Installation for the distribution of fluid under pressure
US2965036A (en) * 1957-07-08 1960-12-20 Louis S Wood Automatic dual pump single-multiple stage low-high pressure fluid supply means
US3292551A (en) * 1965-04-26 1966-12-20 Clark Equipment Co Gear pump or motor
FR1536833A (fr) * 1967-09-15 1968-08-16 Hobourn Eaton Mfg Co Ltd Pompe pour l'alimentation d'un système utilisant un fluide

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR916746A (fr) * 1941-08-19 1946-12-13 Plessey Co Ltd Perfectionnements aux pompes hydrauliques, compresseurs à plusieurs étages et appareils analogues
GB572967A (en) * 1942-04-15 1945-10-31 Pump Engineering Service Corp Improvements in gear-wheel pumps
GB665808A (en) * 1949-11-26 1952-01-30 Snecma Installation for the distribution of fluid under pressure
US2965036A (en) * 1957-07-08 1960-12-20 Louis S Wood Automatic dual pump single-multiple stage low-high pressure fluid supply means
US3292551A (en) * 1965-04-26 1966-12-20 Clark Equipment Co Gear pump or motor
FR1536833A (fr) * 1967-09-15 1968-08-16 Hobourn Eaton Mfg Co Ltd Pompe pour l'alimentation d'un système utilisant un fluide

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0787260A4 (de) * 1994-03-22 1997-08-06
US5842848A (en) * 1997-01-03 1998-12-01 Knowles; Frederick W. Compact high-volume gear pump
EP2634430A1 (de) 2012-02-28 2013-09-04 Maag Pump Systems AG Getriebepumpenanordnung

Also Published As

Publication number Publication date
DE3360299D1 (en) 1985-07-25
EP0091347B1 (de) 1985-06-19
FR2524575A1 (fr) 1983-10-07
FR2524575B1 (fr) 1986-02-28

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