EP0086276A1 - Dispositif stabilisateur du produit de la pression de refoulement et du volume transporté d'une pompe réglable - Google Patents

Dispositif stabilisateur du produit de la pression de refoulement et du volume transporté d'une pompe réglable Download PDF

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Publication number
EP0086276A1
EP0086276A1 EP82112000A EP82112000A EP0086276A1 EP 0086276 A1 EP0086276 A1 EP 0086276A1 EP 82112000 A EP82112000 A EP 82112000A EP 82112000 A EP82112000 A EP 82112000A EP 0086276 A1 EP0086276 A1 EP 0086276A1
Authority
EP
European Patent Office
Prior art keywords
force
lever
spring
pump
delivery
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
EP82112000A
Other languages
German (de)
English (en)
Other versions
EP0086276B1 (fr
Inventor
Gerhard Dipl.-Ing. Nonnenmacher
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 EP0086276A1 publication Critical patent/EP0086276A1/fr
Application granted granted Critical
Publication of EP0086276B1 publication Critical patent/EP0086276B1/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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/08—Regulating by delivery pressure
    • 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
    • F04B2201/00—Pump parameters
    • F04B2201/12—Parameters of driving or driven means
    • F04B2201/1203—Power on the axis

Definitions

  • the invention relates to a device according to the preamble of the main claim.
  • a known device has the disadvantage that its application is limited in that it requires adaptation work for every type of pump and every desired product of pressure and volume, which causes undesirable costs.
  • this facility is often not available for pumps with a small adjustment range.
  • the device according to the invention with the characterizing features of the main claim has the advantage that it is much more flexible, since different pump sizes and types with the exception of a spring with the same Controllers can be operated and that it is also very suitable for pumps with a small adjustment range.
  • 10 denotes an adjustable pump, for example a radial piston pump, whose adjusting member 12, which determines the stroke of piston 11, is adjusted with the aid of two pressurized adjusting pistons 13, 14.
  • the actuating piston 13 has a substantially smaller area than the actuating piston 14.
  • the actuating piston 13 is always acted upon by the pressure prevailing in the delivery line 15 via a line 16.
  • a line 17 also branches off from the delivery line 15 and leads to a 3/3-way valve 18 with the switching positions I, II, III.
  • a line 19 leads from the directional control valve 18 to the bore 20 receiving the actuating piston 14.
  • a line 21 leads from the directional control valve 18 to the container 22, from which the pump 10 also sucks in pressure medium.
  • a compression spring 24 is arranged in the actuating piston 14, one end of which rests against the bottom of the actuating piston 14, while its other end always acts on the one slide side 18 ′ of the directional control valve 18.
  • the other side 18 '' of the directional valve spool is articulated via an extension 25 to one end 26 of an angled, two-armed lever 27, on the other end 28 of which a spring 29 acts on a lever arm a which is always of the same length. It is also essential that the spring acting on the directional control valve 18 has a largely linear characteristic.
  • the pivot point D of the lever 27 rests on a roller 31 which is arranged at the end of the piston rod 32 of a piston 33 which is slidably guided even in a pressurized cylinder 34.
  • the pressure chamber 35 of the cylinder 34 is always acted upon by the delivery pressure of the pump via a line 36 connected to the delivery line 15.
  • a compression spring 37 acts on the piston 33 against the liquid force. It is essential that the spring 37 has a largely linear characteristic.
  • the pivot point D forms two lever arms a and b on the lever 27.
  • the force of the spring 29 is denoted by F1 or second force, the force of the spring 24 by F2 or first force.
  • the control valve 18 is in neutral position II when there is a balance of forces on the lever 27.
  • the piston 33 moves against the force of the spring 37, as a result of which the lever arm b becomes larger.
  • the moment from the spring force F2 times the lever arm b is greater than the constant torque from the spring force F1 times the lever arm a, so that the spring 24 ver the lever 27 can pivot that the directional valve 18 reaches its switching position I.
  • Now pressure medium from the delivery line 15 can enter the bore 20 via the lines 17, 19 and move the actuating piston 14 to the left, whereupon the adjusting member 12 of the pump is set to a lower delivery rate. This has the consequence that the spring 24 relaxes by moving the actuating piston 14 to the left.
  • the moment of spring force F1 and lever arm a now predominates, so that the lever 27 is now pivoted clockwise and the directional valve 18 returns to its neutral position. A new state of equilibrium has thus occurred.
  • the power or torque controller thus converts via the spring 24 with an approximately linear characteristic a path of the actuating piston 14 which is at least approximately linearly proportional to the delivery volume of the pump into a force (spring 24).
  • the length of the lever arm b on which the force of the spring 24 acts changes its Length linearly proportional to the respective working pressure of the pump. This way of working gives an exact hyperbolic characteristic curve over delivery pressure and delivery quantity.
  • the exemplary embodiment according to FIG. 2 is shown in simplified form compared to the previous one, ie the pump and the lines connected there are missing. The same parts are labeled with the same numbers.
  • the now stretched double-acting lever bears the designation 40.
  • the lever 40 counteracts this spring 41 in the same line of action as that of the spring 24. It is supported on a bearing 42 fixed to the housing. It is hereby achieved that no transverse forces act on the control slide 18 and the cylinder 34, as a result of which the adjustability to changes in force is improved.
  • the mode of operation is otherwise exactly the same as in the exemplary embodiment according to FIG. 1.
  • the exemplary embodiment according to FIG. 3 differs significantly in its constructive design from the two above exemplary embodiments, but is basically the same in principle in its mode of operation.
  • the lever for comparing forces is now designed with one arm and is designated 45 and is articulated on the piston rod 32 of the cylinder 34.
  • one end of a spiral spring 46 is fastened, the other end of which acts on the lever 45.
  • the spiral spring takes over the function of the spring 29, that is, it generates the counter torque to the torque from the force of the spring 24 times the lever arm b.
  • the mode of action is exactly the same as described above.
  • the exemplary embodiments according to FIGS. 5 to 7 again largely correspond to those described above, but with the following difference:
  • the pump is reset to a smaller delivery rate by actuating the actuating piston 14 - see FIG. 8 for the exemplary embodiments according to Figures 5 to 7, it is just the opposite.
  • the pump is set to a larger delivery rate by acting on the actuating piston 14.
  • the spring 29 acts on the lever 27 in the opposite direction.
  • the eccentricity e is now opposite to that of the examples described above.
  • FIGS. 6 and 7 correspond to exemplary embodiments 4 and 3, the mode of operation results automatically from what has been described above and what has been said about exemplary embodiments 3 and 4, so that further discussions regarding the mode of operation are no longer necessary.
  • the pressure measuring element designed as a cylinder 34 is advantageously designed to be free of lateral forces in accordance with FIGS. 10 and 11.
  • the cylinder is pivotally attached at 60.
  • the reaction force of the lever 27 is supported on a part 61 fixed to the housing by means of at least one roller 31, preferably attached with the same axis, with the same or different diameter.
  • the roller 31 advantageously consists of three rollers that can move independently of one another.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
EP82112000A 1982-01-14 1982-12-24 Dispositif stabilisateur du produit de la pression de refoulement et du volume transporté d'une pompe réglable Expired EP0086276B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE3200867 1982-01-14
DE3200867 1982-01-14
DE19823207961 DE3207961A1 (de) 1982-01-14 1982-03-05 Einrichtung zum konstanthalten des produktes von foerderdruck und foerdervolumen einer verstellbaren pumpe
DE3207961 1982-03-05

Publications (2)

Publication Number Publication Date
EP0086276A1 true EP0086276A1 (fr) 1983-08-24
EP0086276B1 EP0086276B1 (fr) 1986-04-02

Family

ID=25798858

Family Applications (1)

Application Number Title Priority Date Filing Date
EP82112000A Expired EP0086276B1 (fr) 1982-01-14 1982-12-24 Dispositif stabilisateur du produit de la pression de refoulement et du volume transporté d'une pompe réglable

Country Status (3)

Country Link
US (1) US4496290A (fr)
EP (1) EP0086276B1 (fr)
DE (2) DE3207961A1 (fr)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6131675A (ja) * 1984-07-24 1986-02-14 Nippon Denso Co Ltd 可変容量ポンプ
US6623250B2 (en) * 2000-02-17 2003-09-23 Goodrich Pump And Engine Control Systems, Inc. Fuel metering unit
US6962485B2 (en) * 2003-04-14 2005-11-08 Goodrich Pump And Engine Control Systems, Inc. Constant bypass flow controller for a variable displacement pump
US6916158B2 (en) * 2003-04-30 2005-07-12 Actuant Corporation Radial piston pump
US6996969B2 (en) * 2003-09-09 2006-02-14 Goodrich Pump & Engine Control Systems, Inc. Multi-mode shutdown system for a fuel metering unit
US20050100447A1 (en) * 2003-11-11 2005-05-12 Desai Mihir C. Flow control system for a gas turbine engine
US20080189085A1 (en) * 2004-07-29 2008-08-07 Can Technologies, Inc. System and method for optimizing animal production
US8123492B2 (en) * 2004-09-20 2012-02-28 Magna Powertrain Inc. Speed-related control mechanism for a pump and control method

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1425756A1 (de) * 1962-12-01 1969-04-10 Conen Dipl Ing Helmut Leistungsregler fuer ein hydrostatisches Triebwerk
DE1939918B2 (de) * 1968-08-16 1971-06-03 General Motors Corp , Detroit, Mich (V St A ) Stellgeraet fuer ein hydrostatisches getriebw
DE2362093A1 (de) * 1973-12-14 1975-06-19 Bosch Gmbh Robert Drehmoment-regeleinrichtung fuer eine verstellbare pumpe
DE2419460A1 (de) * 1974-04-23 1975-11-06 Bosch Gmbh Robert Einrichtung zur regelung einer pumpe
DE2620692A1 (de) * 1976-05-07 1977-11-17 Volvo Hydraulikfabrik Gmbh Hydrostatischer wandler

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2531492C2 (de) * 1975-07-15 1982-09-16 Robert Bosch Gmbh, 7000 Stuttgart Verstellbare hydrostatische Pumpe
DE2734933A1 (de) * 1977-08-03 1979-02-15 Linde Ag Regeleinrichtung fuer eine axialkolbenpumpe
DE2930139A1 (de) * 1979-07-25 1981-02-12 Linde Ag Regeleinrichtung fuer ein hydrostatisches getriebe oder eine kolbenpumpe
DE2942403A1 (de) * 1979-10-19 1981-04-30 Linde Ag, 6200 Wiesbaden Leistungsregeleinrichtung fuer eine kolbenpumpe

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1425756A1 (de) * 1962-12-01 1969-04-10 Conen Dipl Ing Helmut Leistungsregler fuer ein hydrostatisches Triebwerk
DE1939918B2 (de) * 1968-08-16 1971-06-03 General Motors Corp , Detroit, Mich (V St A ) Stellgeraet fuer ein hydrostatisches getriebw
DE2362093A1 (de) * 1973-12-14 1975-06-19 Bosch Gmbh Robert Drehmoment-regeleinrichtung fuer eine verstellbare pumpe
DE2419460A1 (de) * 1974-04-23 1975-11-06 Bosch Gmbh Robert Einrichtung zur regelung einer pumpe
DE2620692A1 (de) * 1976-05-07 1977-11-17 Volvo Hydraulikfabrik Gmbh Hydrostatischer wandler

Also Published As

Publication number Publication date
DE3207961A1 (de) 1983-07-21
DE3270327D1 (en) 1986-05-07
US4496290A (en) 1985-01-29
EP0086276B1 (fr) 1986-04-02

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