EP0122171A1 - Automatische hydraulische Vorrichtung zur Förderstromregelung und Überdruckschutz für hydraulische Pumpen mit konstantem Förderstrom - Google Patents

Automatische hydraulische Vorrichtung zur Förderstromregelung und Überdruckschutz für hydraulische Pumpen mit konstantem Förderstrom Download PDF

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Publication number
EP0122171A1
EP0122171A1 EP84400460A EP84400460A EP0122171A1 EP 0122171 A1 EP0122171 A1 EP 0122171A1 EP 84400460 A EP84400460 A EP 84400460A EP 84400460 A EP84400460 A EP 84400460A EP 0122171 A1 EP0122171 A1 EP 0122171A1
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EP
European Patent Office
Prior art keywords
chamber
control
hydraulic
pump
piston
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.)
Withdrawn
Application number
EP84400460A
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English (en)
French (fr)
Inventor
Et Cie S A Societe Ano Besnard
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.)
Besnard Et Cie Sa SA
Original Assignee
Besnard Et Cie Sa SA
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Filing date
Publication date
Application filed by Besnard Et Cie Sa SA filed Critical Besnard Et Cie Sa SA
Publication of EP0122171A1 publication Critical patent/EP0122171A1/de
Withdrawn legal-status Critical Current

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    • 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
    • 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
    • F04B49/007—Installations or systems with two or more pumps or pump cylinders, wherein the flow-path through the stages can be changed, e.g. from series to parallel

Definitions

  • the present invention relates to an automatic hydraulic device for regulating the flow and protecting against overpressure, intended to equip multiple hydraulic pumps with constant flow supplying oil to one or more hydraulic receivers, working continuously under variable speed conditions and dump.
  • Such a device can be applied for example in the supply of oil to hydrostatic power steering or hydraulic lifting devices, in particular for agricultural tractors.
  • the object of the invention is to produce a hydraulic subassembly associated with several pumps, which is intended to allow the reduction of the loss of excess hydraulic energy supplied by the pumps and dissipated in heat when a hydraulic receiver is controlled which works under variable speed and load conditions.
  • the hydraulic control of a hydraulic receiver which works continuously under variable conditions of speed and load, is generally carried out by using a constant displacement pump, when a simple and inexpensive overall solution is desired. , or by using a variable displacement pump fitted with a flow and pressure regulator, when trying to minimize the excess hydraulic energy transformed into heat.
  • the purpose of the present invention is therefore mainly to create an automatic hydraulic device which linked to a multiple pump of constant displacement (generally a gear pump) combines the advantage of the simplicity of this pump, the functional and energy advantage variable displacement pumps fitted with flow and pressure regulators, providing the installation with the flow closest to the instantaneous flow required.
  • Another object of the present invention is to create an automatic hydraulic device easily adaptable to multiple pumps with constant displacement of the same or different value, regardless of the number of pumps (double, triple, etc.).
  • Another object of the invention is to create a hydraulic device of simple and economical construction which can be placed on the front or side face of the pump or in the vicinity thereof.
  • Another object of the invention is to create an automatic hydraulic device which also includes a pressure limiting valve which allows working under load on a single pump while the other pumps deliver at low pressure to the oil tank.
  • the automatic hydraulic adjustment device provides for each individual pump an automatic adjustment section which, linked from the functional point of view to the other sections, firstly performs the hydraulic connection in series of each pump to its corresponding section; in a second step, the hydraulic connection in parallel with the return circuits of the sections; thirdly, the parallel connection of the discharge ports of the pumps to the common discharge circuit by a non-return valve; in a fourth step, the hydraulic connection in series with the control circuits of the adjustment sections and at the same time, the connection in parallel with the pressure limiting valve; and in a fifth step, depending on the position working of the relief valve, the hydraulic connection in parallel from the control circuits to the return circuit.
  • the sections are mounted by frontal superposition automatic adjustment 39, 40, 41 which correspond respectively to pump 3, to pump 2, and to pump 1.
  • the adjustment sections 39, 40 and 41 are fixed to the multiple pump 54 by tie rods 42, so as to produce a one-piece functional assembly.
  • the suction ports of pumps 1, 2 and 3 are connected to the oil tank 20 via the conduit 24 and the extension 21 thereof for the pump 1, of the conduit 25 and the extension 22 thereof for the pump 2, and of the conduit 26 and the extension 23 thereof for the pump 3.
  • the return circuit 34.1 of the device is hydraulically connected to the suction duct 26 via the plug 55 and the duct 56.
  • a second branching of the circuit 34.2 is carried out at the front suction orifice of the pump 3.
  • the discharge circuits of the multiple pump 54 are connected to the automatic hydraulic device by means of a connector 27, the conduit 29 and the annular connector 32 for the pump 1; the connector 28, the conduit 30 and the annular connector 31 for the pump 2; and directly into the common pressure channel 33 for the pump 3.
  • the adjustment section 39 (see FIG. 2) which is functionally connected with the pump 3, consists of a body 4 in which an internal cylindrical bore 63 is produced, in which a piston 7 can slide. The rest position of the piston 7 is imposed by the cover 13 and the compression spring 10 on which a pressure relief valve 57 is mounted.
  • the common pressure channel 33 (see FIG. 2) communicates with the orifice 58 to which is connected the general discharge conduit 59 of the device which is itself linked to the control device 60 of the hydraulic receiver 62.
  • the cavity 70 is in connection with the cavity 71, which is formed in the valve 57 and the orifice 61 by means of a nozzle 72.
  • the cavity 71 is hermetically closed by the conical piston 43 (see FIG. 1) which is supported on the valve seat 47 by the compression spring 44 whose pressing force is adjusted by the adjusting screw 46 and the washer 45.
  • the cavity 74 is connected to the chamber 38 by the channel 73.
  • the adjustment section 40 (see FIG. 3) which works with the pump 2 consists of a body 5 where an internal cylindrical bore 75 is made in which a piston 8 can slide. The rest position of the piston 8 is imposed by the cover 14 and the compression spring 11 on which is mounted cover 17.
  • the non-return valve 48 of an annular shape is placed which is supported by the compression spring 49 on the conical surface 101 of the plug 50.
  • the non-return valve 48 can slide in the bore 105 by the compression of the spring 49 allowing communication between the internal cavity of the plug 50 and the common pressure channel 33 via the cavity 107.
  • the adjustment section 41 (see FIG. 4) which operates with the pump 2, consists of a body 6, in which an internal cylindrical bore 85 is made, in which the piston 9 can slide.
  • the rest position of the piston 9, is imposed by the cover 15 and the compression spring 12, on which the cover 18 is mounted.
  • a first external clearance 86 is made, which allows, through the hole 88, the communication of the chamber 97 with the cavity 100 delimited by the end of the piston 9 and the cover 15.
  • a chamber 84 which communicates with the chamber 79 via the channel 82.
  • a non-return valve 51 of annular shape is placed which is supported by the compression spring 52 on the conical surface 102 of the plug 53.
  • the annular non-return valve 51 can slide in the bore 106 by the compression of the spring 52 thus allowing communication between the internal cavity of the plug 53 and the common pressure channel 33, via the cavity 108.
  • control circuit 114 When the control device 60 is in the neutral position 109, the control circuit 114 is in direct connection with the reservoir 20, via the circuit 115, thus allowing the pumps 1, 2 and 3 to deliver to low pressure their flow in the circuit 34 and then to the reservoir 20.
  • the oil discharged by the pump 3 arrives in the cavity 35 and through the hole 36 in the chamber 34, bringing the piston 7 out of neutral position and simultaneously the communication of the chamber 35 with the chamber 38 and the channel 34.
  • the communication between the chamber 35 and the chamber 38 occurs after the edges of the slots 92, formed in the piston 7, exceed the planar surface 91 of the chamber 38.
  • the edge 89 exceeds the first edge of the chamber 65, and the edge 116 exceeds the other edge of the chamber 65, producing communication between the chamber 65 and the chamber 38, therefore from room 83, via channel 66.
  • the pump 1 which delivers its flow through the circuit 29 in the chamber 97, puts the piston 9 out of the rest position, by the introduction of the oil in the chamber 100 through the hole 88, thus producing at the same time the communication between the chamber 97 and the chamber 98, after the edges of the slots 94 have exceeded the flat surface 110 of the chamber 98.
  • the pressure circuit 59 is connected to the receiver 62, at the same time making a connection of the circuit 114 to the receiver 62.
  • the working pressure of the pump 3 is that imposed by the load that the receiver must move hydraulics 62.
  • control device 60 there is a restriction of the circuit corresponding to the movement made of the device 60, therefore corresponding to the speed of movement of the receiver 62.
  • the pressure of the hydraulic receiver 62 opens into the chamber 70, via the orifice 61, the nozzle 72 and the chamber 71, acting on the piston 7 to bring it closer to the neutral position, and thus achieving, with the using the edges of the slots 92 and the flat surface of the channel 91, a constriction of the communication section between the chamber 35 and the chamber 38, which has the effect of pushing back towards the reservoir 20, through the channel 34, the excess flow supplied by pump 3, and to maintain communication between chamber 65 and channel 38 permanently.
  • This fact allows pumps 2 and 1 to deliver towards the tank 20 all their low pressure flow through the chambers 96 and 98 on channel 34.
  • the chamber 79 communicates with the chamber 96, which allows the piston 9 to be kept away from the rest position and the pump 1 to discharge towards the reservoir 20 all of its flow at low pressure.
  • the maximum opening of the orifice 113 is achieved, so that the working pressure of the receiver 62 stabilizes on all three pistons via circuit 114, chamber 70, channel 66, chambers 83 and 79, channel 82 and chamber 84 and puts the pistons 7, 8 and 9 in the rest position, while pumps 1, 2 and 3 discharge all their flow into the channel 33, and from there through the circuit 59 to the hydraulic circuit 62.
  • the automatic hydraulic adjustment and protection device for multiple pumps which has been described, can also be produced in the variant of mounting on the lateral face of the pump or in the vicinity thereof in the hydraulic installation.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Details Of Reciprocating Pumps (AREA)
EP84400460A 1983-03-09 1984-03-07 Automatische hydraulische Vorrichtung zur Förderstromregelung und Überdruckschutz für hydraulische Pumpen mit konstantem Förderstrom Withdrawn EP0122171A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8303821A FR2542390B1 (fr) 1983-03-09 1983-03-09 Dispositif hydraulique automatique de reglage de debit et de protection contre les surpressions pour pompes hydrauliques a debit constant
FR8303821 1983-03-09

Publications (1)

Publication Number Publication Date
EP0122171A1 true EP0122171A1 (de) 1984-10-17

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ID=9286644

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84400460A Withdrawn EP0122171A1 (de) 1983-03-09 1984-03-07 Automatische hydraulische Vorrichtung zur Förderstromregelung und Überdruckschutz für hydraulische Pumpen mit konstantem Förderstrom

Country Status (2)

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EP (1) EP0122171A1 (de)
FR (1) FR2542390B1 (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2574867A1 (fr) * 1984-12-13 1986-06-20 Reimers Getriebe Ag Pompe a engrenage a denture interieure a plusieurs etages
DE19622517A1 (de) * 1996-06-05 1997-12-11 Eckerle Rexroth Gmbh Co Kg Ventilanordnung für eine hydraulische Zahnradmaschine

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE972842C (de) * 1953-12-08 1959-10-08 Rickmeier Pumpen Regeleinrichtung fuer eine Foerderstufe oder mehrere parallel geschaltete Foerderstufen von Zahnradpumpen zum Foerdern von Fluessigkeit unter Druck
DE2335054A1 (de) * 1972-07-10 1974-01-31 Komatsu Mfg Co Ltd Zahnradpumpe bzw. zahnradmotor

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3022514A (en) * 1959-01-26 1962-02-27 Walter L Kaiser Clothing protector
US3361068A (en) * 1966-08-18 1968-01-02 Allis Chalmers Mfg Co Double hydraulic pump with built-in unloading valve

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE972842C (de) * 1953-12-08 1959-10-08 Rickmeier Pumpen Regeleinrichtung fuer eine Foerderstufe oder mehrere parallel geschaltete Foerderstufen von Zahnradpumpen zum Foerdern von Fluessigkeit unter Druck
DE2335054A1 (de) * 1972-07-10 1974-01-31 Komatsu Mfg Co Ltd Zahnradpumpe bzw. zahnradmotor

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2574867A1 (fr) * 1984-12-13 1986-06-20 Reimers Getriebe Ag Pompe a engrenage a denture interieure a plusieurs etages
DE19622517A1 (de) * 1996-06-05 1997-12-11 Eckerle Rexroth Gmbh Co Kg Ventilanordnung für eine hydraulische Zahnradmaschine

Also Published As

Publication number Publication date
FR2542390B1 (fr) 1987-05-15
FR2542390A1 (fr) 1984-09-14

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