EP0205954B1 - Machine à déplacement positif - Google Patents

Machine à déplacement positif Download PDF

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Publication number
EP0205954B1
EP0205954B1 EP86107036A EP86107036A EP0205954B1 EP 0205954 B1 EP0205954 B1 EP 0205954B1 EP 86107036 A EP86107036 A EP 86107036A EP 86107036 A EP86107036 A EP 86107036A EP 0205954 B1 EP0205954 B1 EP 0205954B1
Authority
EP
European Patent Office
Prior art keywords
gear pump
bore
gear
flow
connection
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
Application number
EP86107036A
Other languages
German (de)
English (en)
Other versions
EP0205954A1 (fr
Inventor
Claus Dipl.-Ing. Jöns
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 EP0205954A1 publication Critical patent/EP0205954A1/fr
Application granted granted Critical
Publication of EP0205954B1 publication Critical patent/EP0205954B1/fr
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

Definitions

  • the invention is based on a displacement machine according to the preamble of claim 1.
  • a displacement machine is known from US-A-3 442 218.
  • the connecting channel is designed as a complex and relatively expensive housing bore.
  • Such holes have to be aligned relatively precisely, which is associated with high workload and costs.
  • the displacement machine according to the invention with the characterizing features of the main claim has the advantage that even a curved course of the connection is possible without the need for complicated manufacturing processes.
  • the displacement machine 10 consists of two gear pumps 11, 12 with housings 13, 14 flanged to one another.
  • the housing 13 of the gear pump 11 is closed on both ends by housing covers 15, 16. It has a continuous recess 17 in which the gears 18, 18a of the gear pump 11 are arranged.
  • the shaft journals of the gear wheels 18, 18a of the gear pump 11 are mounted in bearing bodies 21, 21a, 22, 22a.
  • an inlet bore 23, which leads to the low pressure region 24 of the gear pump 11, and an outlet bore 25, which connects the high pressure region 26 to a consumer A, not shown, are formed in the housing 13, an inlet bore 23, which leads to the low pressure region 24 of the gear pump 11, and an outlet bore 25, which connects the high pressure region 26 to a consumer A, not shown, are formed.
  • the gear pump 12 is designed.
  • the housing 14 is closed on its end face facing the housing 13 by an end plate 27.
  • the housing 28 of a flow control valve 29 is arranged on the other end face.
  • the housing 14 of the gear pump 12 also has a continuous recess 31 in which the gears 32, 32a are arranged.
  • the shaft journals of the gear pump 12 are mounted in bearing bodies 34, 34a, 35, 35a, which are also arranged in the recess 31.
  • the gear 18 of the gear pump 11 has a drive shaft 36, which penetrates to the outside in a sealed manner through a bore in the housing cover 15 and is used to drive both gear pumps 11 and 12. It is possible to design both gear pumps 11, 12 of the same size or with different delivery rates.
  • a bore 38, 39 is formed in each of the flanged housing cover 16 and in the end plate 27, via which the low-pressure area 24 of the gear pump 11 is connected to the low-pressure area 40 of the gear pump 12. Furthermore, there is a second bore 41, 42 in the end plate 27 and in the housing cover 16, which are connected to one another.
  • the bore 41 opens into the high-pressure region 26 of the pump 11.
  • a check valve 43 which is open towards the high-pressure region 26 is arranged in it.
  • a longitudinal bore 45 is formed in the housing 28 of the flow control valve 29 and is closed at both ends by locking screws 46, 47.
  • Three ring grooves 48, 49, 50 are arranged in it, the ring grooves 48, 50 serving as drainage chambers.
  • the annular groove 48 is connected via a bore 51 to a consumer B, not shown.
  • a tubular channel 52 leads from the annular groove 50 to the bore 42.
  • the channel 52 runs through the pressure chamber of the pump 12 and has pipe plug connections at its ends.
  • a control slide 53 is slidably guided in the longitudinal bore 45. It has a blind bore 54 which is the same axis as the longitudinal bore 45 and which is cut in the bottom 55 of a bore 56 extending transversely to the blind bore 54. At the end of the control slide 53 facing away from the opening of the blind bore 54, there is the end of a control spring 57, the other end of which rests on the end plug 46.
  • a measuring orifice 58 is arranged in the opening of the blind bore 54. The space between the orifice plate 58 and the end screw 47 serves as the pressure chamber 59.
  • the pressure chamber 59 is connected to the high-pressure region 61 of the gear pump 12 via a bore 60.
  • the gear pumps 11, 12 suck in pressure medium via the inlet bore 23, then this flows into the low pressure region 24 of the gear pump 11 and via the bores 38, 39 also into the low pressure region 40 of the gear pump 12.
  • the gear pump 12 is to be kept constant with the help of the flow control valve 29 Deliver output to a consumer.
  • the pressure medium flows from the high pressure region 61 of the gear pump 1 via the bore 60 into the pressure chamber 59 of the longitudinal bore 45. From there it flows through the measuring orifice 58 into the blind bore 54 and through the bore 56 into the annular groove 48 and to the consumer.
  • the dynamic pressure which arises at the orifice plate 58 displaces the control slide 53 against the force of the regulator spring 57, so that the connection from the pressure chamber 59 to the annular groove 50 is opened, while the connection from the bore 56 to the annular groove 48 becomes smaller and smaller.
  • the length of the control slide 53 is adjusted so that the connection from the pressure chamber 59 to the annular groove 50 is completely open, on the other hand, the connection from the bore 56 to the annular groove 48 is almost completely closed.
  • the delivery flow flowing to the consumer thus always has a constant value which is regulated by the flow control valve 29.
  • the excess pressure medium flowing into the annular groove 50 flows via the line 52, the bores 42, 41 and the check valve 43 into the high-pressure region 26 of the gear pump 11.
  • This quantity of pressure medium is added to the delivery flow conveyed by the gear pump 11.
  • the check valve 43 prevents a pressure medium flow from the high-pressure region 26 of the gear machine 11 to the flow control valve 29, as a result of which its control level is not influenced. So thus after the constant flow rate determined by the flow control valve 29 has been reached, the pressure medium excessly delivered by the gear pump 12 is additionally added to the flow rate of the gear pump 11. This makes it possible to design the gear pump 11 to be smaller than the desired delivery quantity, because the excess pressure medium of the gear pump 12 is still available.

Landscapes

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

Claims (2)

1. Machine à déplacement positif (10), constituée d'au moins deux pompes à engrenages (11, 12), auxquelles correspond un circuit hydraulique propre ou commun et qui refoulent du produit comprimé, chacune vers un utilisateur (A, B), la quantité refoulée d'au moins une pompe à engrenages (12) est régulée à l'aide d'une soupape de régulation d'écoulement (29) et dont le courant résiduel en excès est régulé par un canal de liaison (52) vers la partie haute pression (26) de l'une des autres pompes à engrenages (11), caractérisée en ce que la machine est constituée de pièces constitutives fixées l'une à l'autre et que la liaison (52) est constituée d'un tube avec des raccords terminaux et qu'elle passe au moins dans la chambre de pression d'une pompe à engrenages (12).
2. Machine selon la revendication 1 caractérisée en ce que dans la liaison (52) est disposée à l'opposé de la soupape de régulation d'écoulement (29) une soupape anti-retour (43).
EP86107036A 1985-06-18 1986-05-23 Machine à déplacement positif Expired EP0205954B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE8517637U DE8517637U1 (de) 1985-06-18 1985-06-18 Verdrängermaschine
DE8517637U 1985-06-18

Publications (2)

Publication Number Publication Date
EP0205954A1 EP0205954A1 (fr) 1986-12-30
EP0205954B1 true EP0205954B1 (fr) 1989-12-20

Family

ID=6782221

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86107036A Expired EP0205954B1 (fr) 1985-06-18 1986-05-23 Machine à déplacement positif

Country Status (2)

Country Link
EP (1) EP0205954B1 (fr)
DE (2) DE8517637U1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5017098A (en) * 1989-03-03 1991-05-21 Vickers, Incorporated Power transmission
DE19622518A1 (de) * 1996-06-05 1997-12-11 Eckerle Rexroth Gmbh Co Kg Hydraulische Doppelzahnradpumpe
DE19915319C2 (de) * 1998-09-02 2002-06-13 Eckerle Ind Elektronik Gmbh Doppel-Zahnradpumpe
GB2367095A (en) * 2000-09-13 2002-03-27 Sauer Danfoss Valve arrangement in separating plate of multiple hydraulic pump and motor ass emblies

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2533320A (en) * 1949-01-04 1950-12-12 Du Pont Rotary gear-type metering pump
US3402891A (en) * 1965-08-20 1968-09-24 Trw Inc Furnace pump and oil burner circuit
US3442218A (en) * 1966-04-12 1969-05-06 Gen Electric Dual purpose pump
DE2608980A1 (de) * 1976-03-04 1977-09-08 Rickmeier Pumpen Zahnradpumpe
US4204811A (en) * 1977-08-19 1980-05-27 The Garrett Corporation Fluid pumping system
JPS58180790A (ja) * 1982-04-19 1983-10-22 Jidosha Kiki Co Ltd オイルポンプ

Also Published As

Publication number Publication date
EP0205954A1 (fr) 1986-12-30
DE8517637U1 (de) 1986-10-16
DE3667709D1 (de) 1990-01-25

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