EP0342346B1 - Pompe à engrenages - Google Patents

Pompe à engrenages Download PDF

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Publication number
EP0342346B1
EP0342346B1 EP89106034A EP89106034A EP0342346B1 EP 0342346 B1 EP0342346 B1 EP 0342346B1 EP 89106034 A EP89106034 A EP 89106034A EP 89106034 A EP89106034 A EP 89106034A EP 0342346 B1 EP0342346 B1 EP 0342346B1
Authority
EP
European Patent Office
Prior art keywords
pressure
gearwheels
gear pump
sealing plate
disposed
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.)
Expired - Lifetime
Application number
EP89106034A
Other languages
German (de)
English (en)
Other versions
EP0342346A3 (en
EP0342346A2 (fr
Inventor
Hayno Dipl.-Ing. Rustige
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 EP0342346A2 publication Critical patent/EP0342346A2/fr
Publication of EP0342346A3 publication Critical patent/EP0342346A3/de
Application granted granted Critical
Publication of EP0342346B1 publication Critical patent/EP0342346B1/fr
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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C14/26—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
    • F04C14/265—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels being obtained by displacing a lateral sealing face
    • 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

Definitions

  • the invention relates to a gear pump according to the preamble of the main claim.
  • a gear pump See GB-A-2048385
  • the sealing plate is brought into sealing contact with the gear side surfaces by means of graduated hydraulic loading of pressure fields, in order to thereby keep the leakage loss between the high pressure and low pressure sides low. It is often disadvantageous that the delivery rate increases with increasing speed.
  • the gear pump according to the invention with the characterizing features of the main claim has the advantage that the sealing plate has, in addition to the sealing function, that of a current regulator, which is effective from a certain delivery volume of the gear pump by targeted leakage oil flow from the high pressure side along the underside of the sealing plate to the low pressure side, so that the delivery volume of the pump is limited to a certain value. So this is possible without a special flow control valve, as was previously necessary. This results in significant savings.
  • FIG. 1 shows a longitudinal section through a gear pump
  • FIG. 2 shows a section along II-II according to FIG. 1
  • FIG. 3 shows a section along III-III according to FIG. 2
  • FIG. 4 shows a schematic diagram
  • FIG. 5 shows a diagram, FIGS. 6 and 7 schematic diagrams.
  • the gear pump has a housing 10, the interior 11 of which has approximately the cross-sectional shape of an eight, which is closed on both sides by covers 12, 13.
  • two gears 14, 15 mesh with one another in external engagement, the shafts 16, 17 of which are mounted in spectacle-shaped bearing bodies 18, 19.
  • Bearing bodies of this type are generally known and are therefore not described further.
  • a passage 20 is formed in the cover 13, through which an extension 23 of the shaft 17 penetrates to the outside; it is sealed there by a sealing ring 24.
  • a sealing plate 26 is arranged between the bearing body 18 and the adjacent side surfaces of the gear wheels 14, 15, which also has the contour of the housing interior, covers the entire surface of the gear wheels and has little axial freedom of movement. Two pressure fields are effective on the back, as described below.
  • FIG. 2 shows, inter alia, a top view of the bearing body 18, specifically from its end face facing the sealing plate 26.
  • a first use 27 running near the outer contour of the bearing body, which runs partially concentrically to the gear shaft and extends from the high-pressure side HD to the low-pressure side ND, but does not extend as far as this.
  • Usage 27 ends in two groove ends 27A, 27B, which penetrate to the edge of the bearing body.
  • a seal 28 made of rubber-elastic material is arranged in this use.
  • a second usable part 29 which also extends from the high pressure side to the low pressure side, its ends 29A, 29B projecting further to the low pressure side than the groove ends of the usable part 27 29 also has an indentation 29C in its central region, which leads approximately to an imaginary straight line connecting the shaft centers.
  • the high-pressure side HD is characterized by a recess 31, into which the high-pressure bore 32 penetrates from the outside of the housing, namely at the level of the gearwheels 14, 15.
  • the low-pressure side ND is characterized by a recess 33, in which an axially coextensive with the high-pressure bore 32 Low pressure bore 34 penetrates, which also extends from the exterior of the housing.
  • FIG. 2 there is an intermediate space between the usages 27, 29, which forms a somewhat enlarged field 35 in the area 29C.
  • This is acted upon via a channel 36, 37, which is partially formed in the bearing body 18, partially in the housing 10.
  • the channel 36, 37 is connected to a bore 38 formed in the housing, which opens into the outlet bore 32, in which an aperture 39 is arranged.
  • the bore 38 opens downstream of the orifice 39 into the outlet bore 32.
  • the orifice 39 is fastened in the outlet bore 39 by means of a locking ring 39A. From this it can be seen that the sealing field B is always subjected to a pressure which prevails downstream of the orifice 39.
  • FIG. 4 shows the operation of the pump in a schematic representation. The same parts as in Figures 1, 2 and 3 are denoted by the same numbers.
  • the gear pump delivers pressure medium, it passes from the container 40 through the low pressure line into the high pressure bore 32. Pressure medium reaches the pressure field A via the recess 31 in which the high pressure prevails. This is therefore always acted upon by the delivery pressure.
  • the pressure field B is applied via the channels 36, 37, 38, specifically from the bore 32, which is located downstream of the orifice 39.
  • the sealing plate 26 is now brought into sealing contact with the gear side surfaces. If the delivery rate of the gear pump continues to increase, the pressure difference at the orifice 39 increases in proportion to the speed n of the gear pump. If the so-called regulating point Z - see diagram according to FIG.
  • the gear pump sucks pressure medium from the container through line 34 40 on and displaces it in line 41.
  • the pressure fields A and B are connected in series.
  • the cut-off pressure Z is reached, the sealing plate is raised, causing pressure medium to flow from the high-pressure side to the low-pressure side. It is functionally represented by a valve function 26.
  • the line 50 with throttle 51 symbolically means the gap losses in the gear pump, which always occur, but are very small.

Landscapes

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

Claims (3)

1. Pompe à engrenages avec deux roues dentées engrenant par engrènement externe, dans laquelle est disposé au moins sur un côté des roues dentées un disque d'étanchéité (26) ajusté au contour du volume intérieur (11) du carter (10), légèrement mobile axialement, disque qui est comprimé de façon étanche contre les faces latérales des roues dentées par la pression du fluide agissant dans deux champs de pression (A, B) et dans laquelle les champs de pression sont limités par des joints d'étanchéité (28, 30) disposés sur le côté situé à l'opposé des roues dentées, pompe dans laquelle les champs de pression sont constitués comme deux zones sensiblement concentriques aux alésages des arbres (27, 28) du moins sur une zone partielle et en fait un premier champ de pression préalable (A) situé radialement à l'extérieur et un deuxième champ de pression principal (B) situé radialement à l'intérieur, pompe à engrenages
caractérisée en ce que
sur le côté haute pression (32) de la pompe à engrenages est constitué un rétrécissement (39) et en ce que la différence de pression régnant dans celui-ci agit sur le disque d'étanchéité, de telle façon que ce disque se soulève des faces latérales des roues dentées à partir d'une vitesse de rotation déterminée par le rétrécissement.
2. Pompe selon la revendication 1,
caractérisée en ce que
le rétrécissement en forme de diaphragme ou d'étranglement est disposé dans l'alésage de vidange (32) de la pompe à engrenages elle-même.
3. Pompe selon la revendication 1,
caractérisée en ce
qu'un appareil à jet (55) est disposé en aval de l'étranglement (39), à travers lequel, d'une part, le courant de refoulement coule, d'autre part, mène à une liaison (56) vers le réservoir.
EP89106034A 1988-05-14 1989-04-06 Pompe à engrenages Expired - Lifetime EP0342346B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3816537A DE3816537A1 (de) 1988-05-14 1988-05-14 Zahnradpumpe
DE3816537 1988-05-14

Publications (3)

Publication Number Publication Date
EP0342346A2 EP0342346A2 (fr) 1989-11-23
EP0342346A3 EP0342346A3 (en) 1990-04-18
EP0342346B1 true EP0342346B1 (fr) 1992-04-15

Family

ID=6354402

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89106034A Expired - Lifetime EP0342346B1 (fr) 1988-05-14 1989-04-06 Pompe à engrenages

Country Status (3)

Country Link
US (1) US4971534A (fr)
EP (1) EP0342346B1 (fr)
DE (2) DE3816537A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3902139A1 (de) * 1989-01-25 1990-07-26 Bosch Gmbh Robert Hydrostatischer antrieb
ATE172006T1 (de) * 1994-06-26 1998-10-15 Maag Pump Systems Ag Zahnradpumpe
US7963186B2 (en) * 2006-04-12 2011-06-21 Arvinmeritor Technology, Llc Ancillary oil pumping for gear box assembly
DE102015100350B3 (de) * 2015-01-12 2016-03-03 Ludwig Michelbach Zahnradpumpe und Luftbefeuchtungsvorrichtung mit einer derartigen Zahnradpumpe

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2990341A (en) * 1956-08-27 1961-06-27 Pittsburgh Plate Glass Co Process for concentrating hydrogen peroxide
US2996999A (en) * 1958-01-22 1961-08-22 Hupp Corp Gear pump
US3476055A (en) * 1967-12-19 1969-11-04 Lucas Industries Ltd Gear pumps
DE2349304C3 (de) * 1973-10-01 1981-07-16 Robert Bosch Gmbh, 7000 Stuttgart Mit Druckflüssigkeit betriebener Zahnradmotor
DE2846547A1 (de) * 1978-10-26 1980-04-30 Pierburg Luftfahrtgeraete Elbstdichtende zahnradpumpe
DD142741A1 (de) * 1979-04-09 1980-07-09 Hubert Stroehl Einrichtung zur steuerung des fluidstroms von rotationskolbenmaschinen,insbesondere zahnradpumpen
DE3430271A1 (de) * 1984-08-17 1986-02-27 Robert Bosch Gmbh, 7000 Stuttgart Zahnradmotor
US4678341A (en) * 1985-05-16 1987-07-07 Stuckey William C Integrated liquid distribution apparatus
DE3605246C2 (de) * 1986-02-19 1993-11-25 Bosch Gmbh Robert Zahnradmaschine (Pumpe oder Motor)
DE8806388U1 (de) * 1987-09-10 1989-01-12 Robert Bosch Gmbh, 7000 Stuttgart Zahnradmotor

Also Published As

Publication number Publication date
DE58901138D1 (de) 1992-05-21
EP0342346A3 (en) 1990-04-18
DE3816537A1 (de) 1989-11-23
EP0342346A2 (fr) 1989-11-23
US4971534A (en) 1990-11-20

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