EP0283348A1 - Hydraulische Pumpen - Google Patents

Hydraulische Pumpen Download PDF

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Publication number
EP0283348A1
EP0283348A1 EP88400381A EP88400381A EP0283348A1 EP 0283348 A1 EP0283348 A1 EP 0283348A1 EP 88400381 A EP88400381 A EP 88400381A EP 88400381 A EP88400381 A EP 88400381A EP 0283348 A1 EP0283348 A1 EP 0283348A1
Authority
EP
European Patent Office
Prior art keywords
valves
valve
hydraulic
pump according
chamber
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
EP88400381A
Other languages
English (en)
French (fr)
Other versions
EP0283348B1 (de
Inventor
Louis Claude Porel
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.)
Hydro Rene Leduc SA
Original Assignee
Hydro Rene Leduc SA
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 Hydro Rene Leduc SA filed Critical Hydro Rene Leduc SA
Publication of EP0283348A1 publication Critical patent/EP0283348A1/de
Application granted granted Critical
Publication of EP0283348B1 publication Critical patent/EP0283348B1/de
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
    • 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
    • F04B49/22—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 by means of valves
    • F04B49/24—Bypassing
    • F04B49/246—Bypassing by keeping open the outlet valve

Definitions

  • the present invention relates to an improvement to hydraulic pumps which are fitted with discharge valves, of the non-return valve type.
  • the solution consisting in returning the pumped liquid continuously to the reservoir may, in certain cases, have the drawback that the liquid heats up, which makes it necessary to have additional cooling means if it is desired to prevent the liquid n '' reaches too high a temperature.
  • the circulation of the fluid requires energy consumption; the latter is then wasted.
  • the solution consisting in disengaging the pump drive is better with regard to the problems of energy expenditure and heating of the hydraulic fluid, but it requires the installation of expensive mechanisms.
  • this arrangement does not allow selective control of certain valves, which would allow, in the case of a multi-flow pump, to cancel a flow while maintaining the others.
  • the discharge valves which it is desired to control the deactivation or the putting into service are constituted by a closing member slidably mounted in a support being constrained by a spring, said support being itself mounted at sliding in a housing provided in the pump body, said sliding support being connected by any suitable means to the piston of a control cylinder; so that, by actuating said control jack, the support or supports which are attached to it or are slid, which puts the corresponding check valve or check valves out of service.
  • means are provided making it possible to make the shutdown of the valves sequential, so that a progressive cancellation or restoration of the pump flow rate (s) is obtained.
  • the hydraulic pump comprises, in a manner known per se a plurality of pistons 1, hollow, which slide in cylinders 2 under the action of a bias plate 3 driven in rotation by a shaft 4.
  • the hydraulic fluid arrives in the inlet chamber 5 of the pump through an orifice 6.
  • the hydraulic fluid passes through a passage 7 etched in the bias plate 3 and enters the head 8 of the piston 1 which it crosses so as to fill the piston 1 which is hollow.
  • the communication between the head 8 of the piston and the passage 7 is interrupted and the liquid is discharged through the line 9 which opens through an orifice 11 into a chamber 10 into which also opens a line 12 which communicates with an outlet orifice 13.
  • a non-return valve designated by the general reference 14 the liquid discharged by the movement of the piston 1 raises said valve and arrives at the outlet orifice 13 by the pipe 12.
  • the liquid discharged by the movement of the piston 1 raises said valve and arrives at the outlet orifice 13 by the pipe 12.
  • all the chambers 10 of the pump are connected to each other by the pipes 12.
  • the discharge valve 14 is constituted by a hollow body 15 which is coaxial with the chamber 10 so as to be able to slide in the chamber 10 along this axis. Inside the hollow body 15 is placed, in a sliding manner, the valve itself 16 which is constrained by a spring 17, bearing against a plug 18, fixed to the sliding hollow body 15.
  • Each sliding hollow body 15 projects, by its end 15a, opposite the valve 16, in a chamber 19 in which a piston 20 moves.
  • This piston 20 is subjected on one side to a return spring 21 and on the other at a hydraulic pressure, brought by a pipe 22, coming from a hydraulic transmitter 23, actuated by a control 24.
  • the pump is intended to supply the lifting cylinder of a tipper body for a truck, it is no longer necessary, as is currently the case, to have a mechanical clutch control for the shaft 4 of the pump.
  • the pump is continuously driven by the gearbox of the truck, the control 24 being in the position shown in FIG. 1.
  • the driver of the truck wishes to actuate the bucket, he just has to act on the control 24 according to arrow F to bring it into the position shown in Figure 2; the valves 16 are then all brought back to the active position by the piston 20 and the pump provides the flow rate and the hydraulic pressure necessary for maneuvering the bucket.
  • FIGS 4 to 6 illustrate two alternative embodiments in which the same elements have the same references.
  • the movement of the piston 20 which controls the implementation of the non-return valves is reversed compared to the previous example in the sense that, in the absence of any pressure at the rear of the piston 20, the valves are active and that they are deactivated when the piston 20 is subjected to hydraulic pressure.
  • the piston 20 is a double-acting piston. It moves in a bore 30 which is on one side connected to a pipe 31 opening into the chamber 30a and on the other to a pipe 32 opening into the room 30b.
  • the piston 20 comprises a gripping member 33 which is engaged in a groove formed at the rear of each plug 18.
  • the piston 20 is no longer subjected to the influence of the spring 21 but to that of a spring. 34 which is arranged in reverse. It follows that when the piston 20 is moved from the left to the right by the pressure arriving in the chamber 30a, it compresses the spring 34 and drives the plugs 18 and therefore the hollow bodies 15 and the valves by the member 33 16 are released from the orifices 11 and therefore made inactive. On the contrary, under the action of the spring 34, or of a pressure arriving in the chamber 30b, the piston is moved from the right to the left and the valves 16 are made active.
  • the outlet orifice 13 of the pump delivers the pressurized liquid into a pipe 35 which ends at a junction point 36.
  • a pipe 35 which ends at a junction point 36.
  • the pipe 32 which ends in the chamber 30b
  • the pipe 37 which leads to a regulator 38
  • the line 39 which is the service line, leading to any hydraulic equipment, not shown.
  • a non-return valve 41 On the pipe 39 are arranged a non-return valve 41 and a hydraulic accumulator 40.
  • the pipe 39 also communicates with the regulator 38 by a pipe 42 located between the hydraulic accumulator 40 and the non-return valve 41.
  • the regulator 38 is intended to fulfill the function of a contactor-circuit breaker. To this end, it includes a pressure relief valve and a control drawer.
  • the pipe 37 opens into a chamber 43 which communicates with the reservoir 44 through an orifice 45 closed by a valve 46 constrained by a spring 47, bandaged by an adjustable stop 48.
  • On the other side of the chamber 43 is a drawer 49 which receives at its other end the pressure arriving through line 42; the drawer 49 slides in a bore 50 connected on the one hand to the pipe 31 (and therefore to the chamber 30a) and on the other hand to the tank 44 by the pipe 51, said pipes 31 and 51 being separated or brought into communication by a partition 52 carried by the drawer 49.
  • the bias plate 3 gives the pistons 1 und back and forth movement; the liquid arriving through the orifice 6 of the reservoir 44 enters the pistons 1 through the passage 7 and the heads 8 of the pistons and is discharged by the pistons into the pipes 9.
  • the piston 20 is pushed back by the spring 34 so that all the valves 16 are in the active position on their respective orifices 11.
  • the pressurized liquid leaves the pump through the orifice 13 and through the line 35 arrives at the junction point 36.
  • the pressurized liquid arrives through the line 32 at the rear of the piston 20 in the chamber 32b and adds its action to that of the spring 34.
  • the pressurized liquid borrows the pipe 39 and, through the valve 41 charges the accumulator 40.
  • the pressurized liquid also arrives at the chamber 43 of the conjunctor-breaker 38 via the pipe 37 by crossing a calibrated passage 53.
  • the slide 49 receiving the high pressure on its two faces by the pipes 37 and 42 is in the equilibrium position.
  • the valve 46 opens and puts the chamber 43 in communication with the reservoir 44.
  • the drawer 49 has a bore 54 which allows the pressure arriving through the pipe 42 to reach the partition 52 and therefore, when the drawer 49 has moved, to communicate with the pipe 31 and therefore with the chamber 30a.
  • the chamber 30a being under pressure, while the chamber 30b is connected to the reservoir by the pipe 32, the chamber 43 and the valve 46, which is kept open by the rod 49a, it follows that the piston 20 moves from the left to the right in Figure 4 by driving the hollow bodies 15 and the valves 16 which become inactive. From this moment, the pump no longer provides any flow. The pressure falls in the pipes 32, 35, 37.
  • the hydraulic accumulator 40 supplies the hydraulic equipment, not shown, located downstream with the pressurized hydraulic liquid necessary for its operation. As this hydraulic fluid under pressure is not renewed by the pump which does not produces no more flow, the pressure gradually drops so that the valve 46 returns to its original position, which puts the chamber 30a in connection with the reservoir 44 via the pipes 31 and 51; the piston 20 returns to the original position and the pump starts to flow again.
  • such an arrangement can be advantageously used for controlling a power steering of a motor vehicle.
  • the power steering is practically only necessary to perform the maneuvers to park a vehicle, that is to say when the engine is idling and its speed practically zero.
  • the steering effort is minimal while the engine is running much faster, for example at 4,000 rpm, which means that the hydraulic pump provides five times greater power.
  • the hydraulic pump provides five times greater power.
  • the steering system operates with the accumulator on the road, said accumulator being regularly recharged, the pump providing no flow most of the time.
  • Figures 5 and 6 show an alternative embodiment of the device of Figure 4 in which the same elements have the same references.
  • the hydraulic pump is a two-flow pump, that is to say that it has six pistons 1 which discharge the liquid into six chambers 10, the chambers 10a, 10b, 10c being connected to one another by collecting pipes 12a and 12b open into an outlet orifice 13a; while the chambers 10d, 10c, 10f are interconnected by collecting pipes 12c and 12d which open into an outlet orifice 13b. Two different output flows are thus obtained, independent of each other, one at 13a and the other at 13b.
  • the bodies 55 of the valves 56 of the chambers 10d, 10c and 10f are screwed and are therefore fixed; while the bodies 15 of the valves 16 of the chambers 10a, 10b and 10c are movable and moved by the piston 20.
  • the pump described in FIGS. 5 and 6 provides two flow rates, one of which, through the outlet orifice 13b, is constant while the other, through the outlet orifice 13a is intermittent.
  • the various chambers 10 can be arranged in which the hollow bodies 15 carrying the non-return valves 16 slide, so that their respective depths are different; thus when the piston 20 moves, the valves 16 do not all simultaneously close their respective orifices 11 but come to close them one after the other in a sequential manner: a progressive commissioning or deactivation is thus obtained.
  • the pump which can be particularly advantageous.
  • FIGS. 7 to 10 represent a preferred embodiment of the invention for this particular use.
  • the chamber 30b of the jack 20 is connected by a pipe 56 to a control distributor 57.
  • the distributor 57 is connected to the source of compressed air of the truck, but it could be connected to a hydraulic source.
  • the collecting pipe 12 comprises just upstream of the outlet 13 (which feeds the lifting cylinder of the bucket) a bypass 12 bis which ends in a chamber 60 which is connected by a bore 12ter to the intake chamber 5.
  • This pipe 12bis is closed by a controlled valve 61 which is integral with a hollow piston 62 sliding in a bore 63 and constrained by a spring 64.
  • the valve 61 is pierced in its center with a calibrated orifice of very small diameter 61a.
  • the bore 63 is connected by a pipe 65 to a control valve 66 and by a pipe 67 to the chamber 30a of the jack 20.
  • the control valve 66 is connected to the chamber 60, in front of the piston 62, by a pipe 68.
  • the control valve 66 comprises a ball 69, actuated by a pusher 70, moved by a handle 71, with interposition of a spring 72 between the pusher 70 and the ball 69.
  • FIG. 8 it can be seen that the command 57 has been implemented.
  • the chamber 30b is then supplied (by compressed air for example) and the jack 20 is pushed back: the discharge valves 15 are then all in the active position.
  • the pressure arising at the discharge of the pump raises the valve 61 and the pressure delivered returns through the line 12ter into the intake chamber 5.
  • the user will be able, at will, to modulate the pressure which arrives at the jack 73. If the lever is barely pushed and the spring 72 barely compressed, the pressure arriving at 65 will raise the ball 69, arrive by 68 in the chamber 60 and push back the piston 62 by opening the valve 61, which causes the pressure to drop until the ball 69 closes the pipe 65. The maximum pressure is obtained when the shoulder 70a of the pusher 70 is in abutment against the body of the valve 66.
  • the bucket 74 has a finger 75 which, at the end of the stroke, acts on a microswitch 76 which controls a valve 77 by a solenoid 78.
  • This valve 77 restores the communication between the pipes 65 and 68 by the branches 65a and 68a bypassing the control 66. We then find us in the same case as when the ball 69 is in the fully open position.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
EP88400381A 1987-02-20 1988-02-19 Hydraulische Pumpen Expired - Lifetime EP0283348B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8702238 1987-02-20
FR8702238A FR2611236B1 (fr) 1987-02-20 1987-02-20 Pompe hydraulique a pistons axiaux munie de clapets antiretour de refoulement commandes hydrauliquement

Publications (2)

Publication Number Publication Date
EP0283348A1 true EP0283348A1 (de) 1988-09-21
EP0283348B1 EP0283348B1 (de) 1990-09-19

Family

ID=9348139

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88400381A Expired - Lifetime EP0283348B1 (de) 1987-02-20 1988-02-19 Hydraulische Pumpen

Country Status (5)

Country Link
US (1) US5032061A (de)
EP (1) EP0283348B1 (de)
DE (1) DE3860624D1 (de)
ES (1) ES2018614B3 (de)
FR (1) FR2611236B1 (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2668547A1 (fr) * 1990-10-30 1992-04-30 Bendix Europ Services Tech Pompe a piston alternatif comportant une chambre de sortie a volume variable, notamment pour circuit de freinage.
WO2014117787A1 (fr) * 2013-01-30 2014-08-07 Baroud Billal Pompe hydraulique a pistons axiaux et l'axe a rainure glisseur et distributeur

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2606758Y2 (ja) * 1992-12-22 2001-01-09 株式会社小松製作所 油圧ポンプ・モータのシリンダ室内圧力コントロール装置
DE4424609B4 (de) * 1994-07-13 2006-01-19 Danfoss A/S Hydraulische Axialkolbenmaschine
JP3656205B2 (ja) * 1997-06-25 2005-06-08 株式会社日立製作所 パワーステアリング装置用油圧ポンプ
DE19953766C1 (de) 1999-11-09 2001-08-09 Danfoss As Hydraulische Axialkolbenmaschine
RU2172428C1 (ru) * 2000-10-18 2001-08-20 Смирнов Игорь Сергеевич Аксиально-поршневой насос и гидравлическая трансмиссия транспортного средства с аксиально-поршневым насосом
US7018181B2 (en) * 2003-05-01 2006-03-28 Wagner Spray Tech Corporation Swashplate pump

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2346987A (en) * 1940-11-09 1944-04-18 Honeywell Regulator Co Variable capacity compressor
FR1350753A (fr) * 1962-12-15 1964-01-31 Anciens Etablissements Panhard Perfectionnements apportés aux installations de transmission hydraulique à raison variable, notamment pour véhicules automobiles
DE3142230A1 (de) * 1980-10-27 1982-09-23 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho, Kariya, Aichi Mehrzylinder-kompressor

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2464448A (en) * 1949-03-15 Cylinder construction for parallel
US2682227A (en) * 1950-07-11 1954-06-29 John G Burris Hydraulic control apparatus
US2806430A (en) * 1952-03-22 1957-09-17 Bendix Aviat Corp Positive displacement variable volume delivery pump and associated control system
US3093081A (en) * 1959-01-29 1963-06-11 New York Air Brake Co Pumping device
JPS59113279A (ja) * 1982-12-20 1984-06-29 Toyoda Autom Loom Works Ltd 可変容量冷媒圧縮機
AT401087B (de) * 1986-04-16 1996-06-25 Hoerbiger Ventilwerke Ag Verfahren zum anpassen eines verdichterventils an unterschiedliche betriebsverhältnisse des verdichters und verdichterventil zur durchführung des verfahrens
AT396002B (de) * 1987-10-28 1993-05-25 Hoerbiger Ventilwerke Ag Plattenventil fuer verdichter

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2346987A (en) * 1940-11-09 1944-04-18 Honeywell Regulator Co Variable capacity compressor
FR1350753A (fr) * 1962-12-15 1964-01-31 Anciens Etablissements Panhard Perfectionnements apportés aux installations de transmission hydraulique à raison variable, notamment pour véhicules automobiles
DE3142230A1 (de) * 1980-10-27 1982-09-23 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho, Kariya, Aichi Mehrzylinder-kompressor

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2668547A1 (fr) * 1990-10-30 1992-04-30 Bendix Europ Services Tech Pompe a piston alternatif comportant une chambre de sortie a volume variable, notamment pour circuit de freinage.
EP0484192A1 (de) * 1990-10-30 1992-05-06 Alliedsignal Europe Services Techniques Flüssigkeitspumpe
US5176428A (en) * 1990-10-30 1993-01-05 Bendix Europe Services Techniques Hydraulic pump
WO2014117787A1 (fr) * 2013-01-30 2014-08-07 Baroud Billal Pompe hydraulique a pistons axiaux et l'axe a rainure glisseur et distributeur

Also Published As

Publication number Publication date
US5032061A (en) 1991-07-16
FR2611236B1 (fr) 1991-12-13
EP0283348B1 (de) 1990-09-19
ES2018614B3 (es) 1991-04-16
DE3860624D1 (de) 1990-10-25
FR2611236A1 (fr) 1988-08-26

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