EP0197320A2 - Pompe à pistons radiaux - Google Patents

Pompe à pistons radiaux Download PDF

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Publication number
EP0197320A2
EP0197320A2 EP86103092A EP86103092A EP0197320A2 EP 0197320 A2 EP0197320 A2 EP 0197320A2 EP 86103092 A EP86103092 A EP 86103092A EP 86103092 A EP86103092 A EP 86103092A EP 0197320 A2 EP0197320 A2 EP 0197320A2
Authority
EP
European Patent Office
Prior art keywords
pump
pressure
valve
pump according
bore
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
EP86103092A
Other languages
German (de)
English (en)
Other versions
EP0197320A3 (en
EP0197320B1 (fr
Inventor
Klaus Dipl.-Ing. Griese
Siegfried Mayer
Dieter Dipl.-Ing. Weigle
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 EP0197320A2 publication Critical patent/EP0197320A2/fr
Publication of EP0197320A3 publication Critical patent/EP0197320A3/de
Application granted granted Critical
Publication of EP0197320B1 publication Critical patent/EP0197320B1/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
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0448—Sealing means, e.g. for shafts or housings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0452—Distribution members, e.g. valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/06—Control
    • F04B1/08—Control regulated by delivery pressure

Definitions

  • the invention relates to a radial piston pump according to the preamble of the main claim.
  • a radial piston pump has a so-called suction pressure control, by means of which, when a certain delivery pressure or a certain delivery quantity is reached, a control element is set by a pressurized piston in such a way that the supply of pressure medium to the bores receiving the pistons is interrupted. This happens within a certain pressure switching range in which the pump then works without pressure for a long time.
  • Such a device is complex, complicated and therefore prone to failure (DE-OS 21 55 789).
  • the radial piston pump according to the invention with the characterizing features of the main claim has the advantage that the flow rate limitation is very simple, i. H. no moving parts required, and that the pump can be controlled depending on the load pressure so that it no longer delivers from a certain load pressure.
  • FIG. 1 shows a longitudinal section through a radial piston pump
  • FIG. 1a shows a partial section according to FIG. 1
  • FIG. 2 shows a view of the drive side of the radial piston pump according to FIG. 1, part of which is cut out and shows a cross section
  • FIG. 3 shows a piston with an outlet valve
  • 4 shows a modification according to FIG. 3
  • FIG. 5 shows a single part (sealing washer)
  • FIG. 6 shows a modification of the single part according to FIG. 5
  • FIG. 7 shows a control device in a schematic representation.
  • the radial piston pump is designed as a so-called plate pump and has a housing middle part 10, which is closed on both sides by housing covers 11 and 12.
  • the middle part of the housing is a cast part and has a plurality of approximately radially extending bores 13 in which pistons 14 are guided in a sliding manner.
  • a cylindrical central recess 15 is also formed, in which the eccentric 16 of a drive shaft 17 is located.
  • the drive shaft is in aligned, central bores 18 and 19 of the housing cover 11 and 12 stored.
  • An enlarged bore part 20 is formed on the bore 16 near its outer end, in which a shaft seal 21 is arranged, but this is not the subject of the invention.
  • Floating on the eccentric 16 are two bushes 24, 25, on which the undersides of the hollow cylindrical pistons 14 are supported.
  • the bores 13 receiving the pistons are closed on their outside by screw plugs 26.
  • a compression spring 27 is arranged in each piston, which is supported on the one hand on the piston head and on the other hand on a so-called flat seat 28A for a valve body 29 of an exhaust valve 28.
  • annular channel 30 extends around the bore 19 in the cover 12, and an annular channel 31 of this kind extends around the bore 18 in the cover 11. These annular channels have no functional significance.
  • annular channel 33 extends in the cover 12 and opens into an inlet bore 34 on the cover 12. Starting from the ring channel 33, a channel 35 penetrates into each bore 13. The outer edge of the channel 35 is designated 35A and forms a control edge.
  • a ring channel 37 runs even further outside of the ring channel 33 in the cover 12 and, as FIG. 1 a shows, has a connection to the outlet bore 38.
  • a channel 39 extends from the ring channel 37, which also opens into the bores 13, but outside the outlet valve 28.
  • a thin sealing disk 40 is arranged between the middle part of the housing and the cover 12, which is shown in FIG view is shown. It has a continuous channel 42, which is only interrupted by thin webs 49 and extends around its central bore 41 and which has a somewhat wavy ring shape as a result of through bores 43.
  • the channel 42 forms a passage from the ring channel 37 to the channels 39, which are connected to the bores 13. This connection exists in each case on an outwardly directed bulge 46 of the channel 42.
  • Two seals 44, 45 which are attached to the outside and inside of the channel 42 by adhesive bonding or vulcanization to the sealing disk 40 or are printed on the sealing disk 40 in a screen printing process, ensure good sealing are.
  • an aperture 47 assigned to each bore 13 is formed as a passage. It establishes a connection from the annular channel 33 to the channel 35 and serves for a so-called suction throttling.
  • a stepped bore 50 also formed in the cover 12, opens into the annular channel 37 which is arranged a pressure limiting valve 51, which consists of a spherical valve body 52 and a spring 53 loading it.
  • the stepped bore 50 is closed to the outside by a screw plug 54.
  • a stepped bore 55 extends from the stepped bore into the annular channel 30 Ring channel 30 runs a throttle bore 56 to the bore 20 receiving the sealing ring 21.
  • the outlet valve 28 is shown in detail. It has a so-called flat seat 28A in the form of a ring which is embedded in the upper edge of the bore 13.
  • the flat seat 28A has a central through bore 58, which is closed by the valve body 29.
  • This has a central cylindrical extension 59 facing the locking screw 26, on the edge of which the inner edge of a plate spring 60 is supported, the outer edge of which rests in a cylindrical recess 61 of the locking screw 26.
  • the plate spring 60 serves as Centering spring for the valve body 59.
  • the flat seat 28A is pressed in and at the same time held by the pressure,
  • the operation of the radial piston pump described is relatively simple.
  • the piston 14 is given a stroke movement by the drive shaft 17.
  • the channel 35 is opened so that pressure medium can flow into the bores 13 via the inlet bore 34 and the orifices 47 in the sealing disk 40.
  • the amount of the pressure medium drawn in is limited by the orifices 47 in the sealing disk 40, which results in a flow rate limitation.
  • the upper edge of the piston closes the control edge 35A, whereupon the pressure lifting process begins.
  • the valve body 29 is raised from its flat seat. Pressure medium now flows to the consumer via the channel 39 and the outlet bore 38.
  • FIG. 4 a variant of the outlet valve 28 will be explained, see FIG. 4.
  • the flat seat 28A is provided, which, however, now rests on a disk 65 in which a plurality of through bores 66 are formed.
  • the shaft 68 of the Valve body 69 In the central bore 67 of the disk 65, the shaft 68 of the Valve body 69 out.
  • two disc springs 70, 71 are arranged, which are so biased by a snap ring 72 also arranged on the shaft that they press the valve body 69 onto the valve seat.
  • the function is the same as the exhaust valve described above.
  • the pump according to the invention can also be designed as a multiple pump. Then e.g. two outlet channels and requires another sealing washer, which is shown in Figure 6 and is designated 75. It is essentially similar again, now has a first channel 76, which is assigned to several piston bores, and a channel 77, which only belongs to a single piston bore. The second consumer is connected here, which of course receives correspondingly less pressure medium.
  • the pressure control for lifting the pistons 14 at a certain delivery pressure can also be achieved by an arrangement according to FIG. 7, which is shown in simplified form.
  • a consumer line 80 is connected to the outlet 38 and a suction line 81 to the inlet 34. In this or in front of the inlet 34 there is the orifice 47 for the suction throttling.
  • a pressure control valve 82 is also provided, in which a slide bore 83 is formed. In this a control slide 84 is guided, which is loaded from the bottom by a control spring 85. This is located in a space 86 of the slide bore 83, into which a line 87 opens, in which the load pressure at the consumer is effective.
  • a pressure relief valve 88 is arranged, which is set to maximum pressure.
  • a line 89 extends from the line 80 and opens into an annular groove 90 at the slide bore 83.
  • a line 21 branches off from line 89 and leads into an upper pressure chamber 92 of the slide bore 83 opens.
  • a line 93 extends from the line 81 and opens into an annular groove 94 at the slide bore 83, which lies above the annular groove 90.
  • a line 95 branches off from line 93 and opens into the outlet space of pressure-limiting valve 88.
  • a line 96 branches off from a point between the two annular grooves 90, 94 and runs to the recess 15 of the middle part of the pump housing.
  • the pressure from the delivery line 80 acts in the pressure chamber 92 on the control slide 84.
  • the load pressure currently prevailing at the consumer acts via the line 87;
  • the control spring 85 acts on the control slide 84 from this side. If the delivery pressure prevailing in line 80 is greater than the load pressure prevailing in bore part 86 plus the force of spring 85, then the control slide is moved downward, so that a connection is made from line 89 to line 96.
  • Pressure medium can now enter the recess 15 flow in and build up a pressure by which the pistons 14 are lifted from the eccentric.
  • the pump now no longer delivers pressure medium until the pressure in the pressure chamber 92 has dropped accordingly.
  • the pressure limiting valve 88 opens, so that a so-called pressure cut-off is achieved, i. H. an operating state in which funding is also no longer provided.
  • a pump according to the invention also has the advantage, among other things, that a pump designed as a constant pump has the advantages of a variable displacement pump, but with a significantly lower construction cost.
  • a combination of suction throttling, load sensing technology (exemplary embodiment according to FIG. 7) and speed-independent delivery flow is achieved.
  • the pump can also be designed as a multiple pump.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Reciprocating Pumps (AREA)
EP86103092A 1985-04-12 1986-03-07 Pompe à pistons radiaux Expired EP0197320B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3513164 1985-04-12
DE19853513164 DE3513164A1 (de) 1985-04-12 1985-04-12 Radialkolbenpumpe

Publications (3)

Publication Number Publication Date
EP0197320A2 true EP0197320A2 (fr) 1986-10-15
EP0197320A3 EP0197320A3 (en) 1987-06-16
EP0197320B1 EP0197320B1 (fr) 1989-06-07

Family

ID=6267852

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86103092A Expired EP0197320B1 (fr) 1985-04-12 1986-03-07 Pompe à pistons radiaux

Country Status (3)

Country Link
US (1) US4681514A (fr)
EP (1) EP0197320B1 (fr)
DE (2) DE3513164A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2690483A1 (fr) * 1992-04-27 1993-10-29 Rexroth Mannesmann Gmbh Pompe à pistons radiaux, notamment pompe de carburant pour moteur à combustion interne.
WO1994012789A1 (fr) * 1992-11-24 1994-06-09 Itt Automotive Europe Gmbh Soupape comportant peu de composants, en particulier soupape de pression pour pompe a pistons radiaux
FR2702250A1 (fr) * 1993-03-06 1994-09-09 Rexroth Mannesmann Gmbh Machine ou moteur hydraulique à pistons et à contre-pression.
DE4336673A1 (de) * 1993-10-27 1995-05-04 Zahnradfabrik Friedrichshafen Radialkolbenpumpe
US5839349A (en) * 1992-12-11 1998-11-24 Itt Automotive Europe Gmbh Noise-abated pump unit, in particular for controlled brake systems
WO1999019621A1 (fr) * 1997-10-09 1999-04-22 Robert Bosch Gmbh Pompe a pistons radiaux pour l'alimentation haute pression en carburant

Families Citing this family (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BR8707630A (pt) * 1986-03-07 1989-03-14 Zahnradfabrik Friedrichshafen Bomba de pistao radial
IT212433Z2 (it) * 1987-08-25 1989-07-04 Weber Srl Pompa a stantuffi radiali
DE4139611A1 (de) * 1991-11-30 1993-06-03 Zahnradfabrik Friedrichshafen Getriebe mit einer verdraengerpumpe
DE4241825A1 (de) * 1992-12-11 1994-06-16 Teves Gmbh Alfred Geräuschreduzierte Hochdruckpumpe, insbesondere für geregelte Bremsanlagen
DE4241826A1 (de) * 1992-12-11 1994-08-25 Teves Gmbh Alfred Hochdruckpumpe mit Radialkolben und Dämpfungsschicht
US5354183A (en) * 1993-02-11 1994-10-11 Elasis Sistema Ricerca Fiat Nel Mezzogiorno Societa Consortile Per Azioni Pumping device with a main pumping stage and a supply pump
DE19920168A1 (de) * 1998-05-16 1999-11-18 Luk Automobiltech Gmbh & Co Kg Radialkolbenpumpe
EP1000245B1 (fr) * 1998-05-26 2004-08-25 Caterpillar Inc. Systeme hydraulique avec pompe a debit variable
DE10128431A1 (de) * 2001-06-12 2002-12-19 Zf Batavia Llc Radialkolbenpumpe
DE10253189A1 (de) * 2002-11-15 2004-05-27 Robert Bosch Gmbh Radialkolbenpumpe mit flächiger Dichtung zwischen Flansch und Gehäuse
DE102004050886A1 (de) * 2004-10-19 2006-04-20 Siemens Ag Radialkolbenpumpe mit Wellenabdichtung
WO2006053792A1 (fr) * 2004-11-17 2006-05-26 Siemens Aktiengesellschaft Systeme de pompage
DE102007005837B4 (de) * 2006-02-03 2016-04-07 Novopress Gmbh Pressen Und Presswerkzeuge & Co. Kg Antriebseinheit für ein Preßgerät
US7588119B2 (en) * 2006-04-12 2009-09-15 Gm Global Technology Operations, Inc. Hydrostatic retarder pump and motor
DE102008023674B4 (de) * 2008-05-15 2012-03-22 Ab Skf Schmiermittelversorgungsvorrichtung
DE102015007465A1 (de) * 2015-06-09 2016-12-15 Thomas Magnete Gmbh Hubkolbenpumpe mit eingangsseitiger Förderstrombegrenzung und Verfahren zum Betrieb der Hubkolbenpumpe
CN106939886A (zh) * 2016-01-04 2017-07-11 熵零技术逻辑工程院集团股份有限公司 流体机构及应用其的系统
SK288973B6 (sk) * 2020-08-13 2022-06-30 Up-Steel, S.R.O. Radiálny piestový rotačný stroj

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2650543A (en) * 1944-10-28 1953-09-01 Installation Et D App Soc D High-pressure radial piston pump for liquids
FR1464906A (fr) * 1965-11-26 1967-01-06 Pompe du type à cylindres et pistons en étoile
DE1453475A1 (de) * 1962-04-03 1969-02-06 Deere & Co Ventil zum selbsttaetigen Regeln von Kolbenpumpen,insbesondere Radialkolbenpumpen
DE2616437A1 (de) * 1976-04-14 1977-10-27 Fichtel & Sachs Ag Radialkolbenpumpe
GB2043804A (en) * 1979-01-18 1980-10-08 Renault Vehicules Ind Gaskets
DE2242435B2 (de) * 1972-08-29 1981-01-15 Alfred Teves Gmbh, 6000 Frankfurt Radialkolbenpumpe
DE3043860A1 (de) * 1980-11-21 1982-06-24 Fichtel & Sachs Ag, 8720 Schweinfurt Radialkolbenpumpe

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR586095A (fr) * 1924-06-19 1925-03-14 Cie Francaise De Manutention D Mesureur-distributeur d'huile
US3002462A (en) * 1957-08-13 1961-10-03 Racine Hydraulics & Machinery Fluid translating apparatus
US3418937A (en) * 1966-11-04 1968-12-31 White Motor Corp Radial piston pump
US3434428A (en) * 1967-06-05 1969-03-25 White Motor Corp Intake control for multiple piston pump
DE2155789A1 (de) * 1971-11-10 1973-05-17 Bosch Gmbh Robert Kolbenpumpe fuer hydraulische anlagen
DE2404762A1 (de) * 1974-02-01 1975-08-07 Bosch Gmbh Robert Hydraulische kolbenpumpe
DE2425022A1 (de) * 1974-05-24 1975-12-04 Bosch Gmbh Robert Kolbenpumpe
DE2732247A1 (de) * 1977-07-16 1979-02-01 Bosch Gmbh Robert Druck- oder saugventil fuer eine pumpe
DE2817173A1 (de) * 1978-04-20 1979-10-25 Rexroth Gmbh G L Radialkolbenpumpe
DE2838918A1 (de) * 1978-09-07 1980-05-22 Bosch Gmbh Robert Hydraulisches druckbeschaffungssystem
US4610606A (en) * 1984-08-06 1986-09-09 Hch Development, Inc. Gas refrigerant compressor including ported walls and a piston of unitary construction having a domed top

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2650543A (en) * 1944-10-28 1953-09-01 Installation Et D App Soc D High-pressure radial piston pump for liquids
DE1453475A1 (de) * 1962-04-03 1969-02-06 Deere & Co Ventil zum selbsttaetigen Regeln von Kolbenpumpen,insbesondere Radialkolbenpumpen
FR1464906A (fr) * 1965-11-26 1967-01-06 Pompe du type à cylindres et pistons en étoile
DE2242435B2 (de) * 1972-08-29 1981-01-15 Alfred Teves Gmbh, 6000 Frankfurt Radialkolbenpumpe
DE2616437A1 (de) * 1976-04-14 1977-10-27 Fichtel & Sachs Ag Radialkolbenpumpe
GB2043804A (en) * 1979-01-18 1980-10-08 Renault Vehicules Ind Gaskets
DE3043860A1 (de) * 1980-11-21 1982-06-24 Fichtel & Sachs Ag, 8720 Schweinfurt Radialkolbenpumpe

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2690483A1 (fr) * 1992-04-27 1993-10-29 Rexroth Mannesmann Gmbh Pompe à pistons radiaux, notamment pompe de carburant pour moteur à combustion interne.
WO1994012789A1 (fr) * 1992-11-24 1994-06-09 Itt Automotive Europe Gmbh Soupape comportant peu de composants, en particulier soupape de pression pour pompe a pistons radiaux
US5609182A (en) * 1992-11-24 1997-03-11 Itt Automotive Europe Gmbh Valve
US5839349A (en) * 1992-12-11 1998-11-24 Itt Automotive Europe Gmbh Noise-abated pump unit, in particular for controlled brake systems
FR2702250A1 (fr) * 1993-03-06 1994-09-09 Rexroth Mannesmann Gmbh Machine ou moteur hydraulique à pistons et à contre-pression.
DE4336673A1 (de) * 1993-10-27 1995-05-04 Zahnradfabrik Friedrichshafen Radialkolbenpumpe
DE4336673C2 (de) * 1993-10-27 1999-08-12 Zahnradfabrik Friedrichshafen Radialkolbenpumpe
WO1999019621A1 (fr) * 1997-10-09 1999-04-22 Robert Bosch Gmbh Pompe a pistons radiaux pour l'alimentation haute pression en carburant

Also Published As

Publication number Publication date
US4681514A (en) 1987-07-21
EP0197320A3 (en) 1987-06-16
DE3663840D1 (de) 1989-07-13
DE3513164A1 (de) 1986-10-23
EP0197320B1 (fr) 1989-06-07

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