WO2008046544A1 - Machine hydraulique de travail - Google Patents

Machine hydraulique de travail Download PDF

Info

Publication number
WO2008046544A1
WO2008046544A1 PCT/EP2007/008796 EP2007008796W WO2008046544A1 WO 2008046544 A1 WO2008046544 A1 WO 2008046544A1 EP 2007008796 W EP2007008796 W EP 2007008796W WO 2008046544 A1 WO2008046544 A1 WO 2008046544A1
Authority
WO
WIPO (PCT)
Prior art keywords
working
machine according
hydraulic
piston
working machine
Prior art date
Application number
PCT/EP2007/008796
Other languages
German (de)
English (en)
Inventor
Michael Gaumnitz
Roland Schempp
Joachim Schmitt
Friedemann Nordt
Manfred Unger
Alexander Zorn
Stefan Hoppe
David Breuer
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 WO2008046544A1 publication Critical patent/WO2008046544A1/fr

Links

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
    • 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
    • F04B1/063—Control by using a valve in a system with several pumping chambers wherein the flow-path through the chambers can be changed, e.g. between series and parallel flow
    • 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
    • F04B49/02—Stopping, starting, unloading or idling control
    • F04B49/03—Stopping, starting, unloading or idling control by means of valves
    • F04B49/035—Bypassing
    • 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
    • F04B49/06—Control using electricity
    • F04B49/065—Control using electricity and making use of computers

Definitions

  • the invention relates to a hydraulic working machine according to the
  • Such, designed as a radial piston hydraulic hydraulic machine is known for example from DE 40 41 800 C2.
  • This conventional solution has cylinder-guided pistons which are diametrically opposed in pairs and driven by an eccentric shaft.
  • the piston / cylinder arrangements each delimit a working space with a cyclically changing volume, which is connected in each case to a low-pressure connection and a high-pressure connection.
  • the work spaces are connected via a connecting channel in which an electronically controlled, operable from an open position against the force of a return spring in a blocking position blocking valve is provided which can be controlled via an electronic control unit. If the switching valve in its open position, there is no pressure medium delivery to the high-pressure connection, since only pressure medium is displaced via the connecting line between the working spaces of the piston / cylinder arrangements.
  • the present invention seeks to provide a hydraulic see machine, in which an improved control of the delivery or suction volume flow is made possible with minimal manufacturing effort. This object is achieved by a hydraulic working machine having the features of patent claim 1.
  • the working machine has a multiplicity of work spaces with cyclically changing volumes, which are each connected to a low-pressure connection and a high-pressure connection, between which connection channels (36) are provided, in each of which an electronically controlled shut-off valve is arranged an electronic control unit is controllable.
  • each shut-off valve can be controlled individually via the electronic control unit as a function of the changing volume of each working space, so that a change in the sip or delivery volume flow between an idle mode in which the usable volume of a working space is substantially displaced into the other working space and a full mode in which essentially all the usable volume of the workrooms is used.
  • the idle mode or a partial mode is realized by the volume of a working space is timely controlled completely or partially ejected in the other working space of the pair of working over a controlled by the electronic control unit check valve to change the time-averaged effective flow through the machine and to achieve a low pulsation of the delivery or suction volume flow.
  • This solution has the advantage that a substantially continuous change of the delivery or suction volume is achieved with minimal pulsation with minimal manufacturing effort, since the check valves over the prior art according to DE 40 41 800 C2 are individually controlled.
  • the hydraulic working machine can be designed, for example, as a radial piston machine, in particular as a radial piston pump, wherein the working spaces are preferably bounded by pistons which can be moved back and forth in cylinders.
  • the check valves are controlled in the manner of a rotating field and optimized for pulsation.
  • the check valves connect, for example, in each case directly successive working spaces with each other.
  • the number of work spaces is even and a check valve connects two 180 ° offset from each other work rooms together.
  • the check valve opens in partial mode preferably a defined time before the top dead center of the piston, wherein a portion of the usable volume is moved to the other working space (phase control section).
  • the low-pressure piston chambers are prefilled at idling and partial delivery, so that an improvement in the efficiency, the pumping speed and the cavitation resistance is achieved. Since the switching of the idling or the partial delivery is possible at any time of the displacement, in addition to the phase portion control, a phase control and / or a phase cut control can be realized.
  • the check valve is opened in the partial mode a defined time after the bottom dead center of the piston, so that a portion of the usable volume is moved into the other working space.
  • the check valve in the partial mode opens a defined time between the bottom and the top dead center of the piston, so that a portion of the usable volume is moved into the other working space.
  • the electronic control unit preferably controls the shut-off valve as a function of a characteristic curve, a program or a setpoint specification for pressure and / or volume flow.
  • the switching mode is preferably selected by an electronic system and a controller algorithm (computer program) in such a way that the lowest possible volume-flow volume flow of a pump or sum-sip volume flow of a hydraulic motor is achieved.
  • the hydraulic work machine has an even number of work spaces, i. at least two working spaces, on, which are each connected via a connecting channel.
  • the check valve is designed as a 2/2-way valve.
  • the check valve is magnetically actuated.
  • the outlet and / or supply lines of the working spaces are combined in one embodiment of the invention into a low-pressure or high-pressure main line. Thereby, the pulsation of the sum-flow volume flow of a pump or the sum-sip volume flow of a hydraulic motor can be further reduced.
  • Figure 1 is a schematic representation of a designed as a radial piston pump according to the invention hydraulic working machine according to a first embodiment.
  • Fig. 2 is a schematic representation of a radial piston pump according to a second embodiment;
  • Fig. 3 is a schematic representation of a radial piston pump according to a third embodiment.
  • FIG. 1 shows a designed as a radial piston pump 1 inventive hydraulic working machine according to a first embodiment with an even number of diametrically opposed cylinders 2, 4, in each of which a piston 6, 8 is slidably guided, with the cylinders 2, 4 each one Working space 10, 12 limited with cyclically changing volume, with only two cylinder / piston arrangements are shown in the figure for reasons of clarity.
  • Each working space 10, 12 is connected via a high-pressure line 14, 16 to a common high-pressure connection P (pressure connection) and via a low-pressure line 18, 20 to a common low-pressure connection S (suction connection).
  • P pressure connection
  • S suction connection
  • Low pressure lines 18, 20 is in each case one in the direction of the working spaces 10, 12 opening, working as a suction valve check valve 26, 28 is arranged.
  • the pistons 6, 8 are driven via a drive shaft 29, which is provided in the region of the pistons 6, 8 with an eccentric 30, so that they are biased by piston rods 32, 34, against which the pistons 6, 8 with a piston foot , in the rotational movement of the eccentric shaft 30 perform an opposite input and extension movement.
  • the work spaces 10, 12 are each connected via a connecting line 36, in which an electronically controlled, operable from an open position shown in a blocking position blocking valve 38 is provided which via an electronic control unit, not shown, depending on the changing volume of each of the working spaces 10, 12 is controlled.
  • Each of a cylinder / piston pair associated shut-off valves 38 can be controlled individually via the electronic control unit, so that a change in the delivery volume flow between an idle Mode in which the usable volume of a working space 10, 12 is substantially moved to the other working space 12, 10 and a full mode in which substantially all the usable volume of the working spaces 10, 12 is used, is reached. It has proven to be particularly advantageous if the check valve 38 is designed as a magnetically actuated 2/2 way valve.
  • the upper piston 6 is at top dead center, so that the working space 10 has its smallest and the working space 12 has its maximum volume.
  • the piston 6 moves during the rotational movement of the drive shaft 30 in the direction of the eccentric.
  • the working space 10 increases, wherein the non-return valve 26 operating as a suction valve opens by the resulting negative pressure.
  • Pressure fluid flows from the low pressure port S via the low pressure line 18 and the open suction valve 26 in the increasing working space 10.
  • the piston 8 is at bottom dead center, the working chamber 12 is completely filled with pressure medium.
  • the suction valve 28 is closed.
  • the piston 8 With the rotational movement of the drive shaft 30, the piston 8 is moved via the eccentric 30 and the piston rod 34 in the direction of top dead center.
  • open check valve 38 see figure
  • the usable volume of the working space 12 is moved via the connecting line 36 into the working space 10 of the piston 6, so that in the open position of the check valve 38 no pressure medium to the
  • High pressure port P is promoted (idle mode).
  • the pressure valves 22, 24 are in this case closed, for example spring or pressure loaded. If now the check valve 38 is closed, so that the pressure medium connection between the work spaces 10, 12 interrupted by the connecting line 36, so is substantially the whole usable volume of
  • phase-angle control and phase-cut control can be realized.
  • the check valve 38 remains open a defined time after the bottom dead center of the piston 8, so that a portion of the usable volume flow is displaced via the connecting line 36 into the working chamber 10 of the piston 6. Subsequently, the check valve 38 is closed and the remaining volume via the high pressure line 16 and the opening pressure valve 24 to the high pressure port P promoted (partial flow promotion).
  • the blocking valve 38 opens a defined time in the partial mode between the lower and upper dead center of the piston 8, so that part of the usable volume flow is displaced into the other working space 10. Subsequently, the check valve 38 is also closed again and the remaining volume via the high-pressure line 16 and the opening pressure valve 24 is conveyed to the high pressure port P.
  • the electronic control unit controls the shut-off valve 38 in this case in response to a characteristic curve, a program or a setpoint specification for pressure and or flow.
  • This radial piston machine 1 has, in contrast to the first embodiment in Figure 1, an odd number of cylinders 40, 42, 44, 46, 48, which are arranged in a star shape around the drive shaft 29 around.
  • Each working space 50 of a cylinder 40-48 is connected via a connecting line 52, in which a check valve 54, 56, 58, 60, 62 is provided, with the working space 50 of its respective adjacent cylinder 40-48.
  • the blocking valve 56 is arranged between the cylinder 42 and its cylinder 44, viewed in the direction of rotation (see Fig. 2) of the drive shaft.
  • the blocking valve 56 is arranged.
  • cylinder 40 Viewed against the direction of rotation, cylinder 40 is the adjacent cylinder of cylinder 42, between which the check valve 54 is interposed.
  • the check valves 54, 56 in the open state in each case a connection of the working chambers of the cylinder 40, 42 and the cylinder 42, 44 ago.
  • the check valves 54-62 can each be regulated or controlled individually, independently of each other and with a variable time.
  • Usable volume is in this case either from a cylinder 40 in the direction of rotation (see Fig. 2) leading to the next cylinder 42 leading, lagging towards the next cylinder 48 seen against the direction of rotation or simultaneously moved to these two adjacent cylinders 42, 48.
  • check valve 56 is opened, closed again after a certain time and for this purpose shut-off valve 58 is opened and so on.
  • the control of the check valves 54-62 is variable, so that a wide variety of variations are possible and not adjacent check valves 54-62 can be opened and closed simultaneously or at different times.
  • a complete idle circuit or idle mode as in the first embodiment in Figure 1 is not possible because the working spaces 50 of the cylinder 40-48 have different high volume change during rotation and the difference in volume change of all working spaces 50 does not give zero, but something is larger. However, it is conceivable that the difference in the volume change is compensated by the compressibility of the pressure medium.
  • a third embodiment is disclosed with a radial piston machine 1 which three cylinders 64, 66, 68, between which the check valves 70, 72, 74 are arranged.
  • This radial piston machine 1 basically has the same construction as the radial piston machine 1 from FIG. 2, so that reference is made to the embodiment of FIG. 2 for a detailed description.
  • the working machine 1 is not limited to the described radial piston pumps, but the working machine 1 may be formed as a radial piston motor or axial piston machine. Furthermore, the invention is not limited to reciprocating engines, for example, the working machine may be designed as a vane pump or vane motor. Also in the pneumatic field, use of this working machine 1 is possible, compressed air being used instead of pressurized fluid. Another possible use of this machine 1 would be conceivable as an air compressor.
  • a hydraulic working machine 1 with a plurality of working spaces 10, 12 with cyclically changing volume, which are connected via at least one connecting channel 36, in which an electronically controlled shut-off valve 38 is provided, which is controlled via an electronic control unit.
  • each shut-off valve 38 can be individually controlled via the electronic control unit as a function of the changing volume of each working space 10, 12, so that a change in the sip or delivery volume flow is achieved between an idle mode and a full mode.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Computer Hardware Design (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)

Abstract

Machine hydraulique de travail comprenant une pluralité de compartiments de travail avec des volumes à variation cyclique reliés par au moins un canal de raccordement intégrant une valve d'arrêt à commande électronique commandée par une unité de commande électronique. Selon l'invention, chaque valve d'arrêt peut être commandée individuellement par l'unité de commande électronique en fonction du volume variable de chaque compartiment de travail de manière à obtenir une modification du débit volumétrique d'absorption ou du débit volumétrique de refoulement entre un mode volume minimal et un mode volume maximal.
PCT/EP2007/008796 2006-10-20 2007-10-10 Machine hydraulique de travail WO2008046544A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102006049577.2 2006-10-20
DE102006049577 2006-10-20
DE102007029670.5 2007-06-27
DE102007029670A DE102007029670A1 (de) 2006-10-20 2007-06-27 Hydraulische Arbeitsmaschine

Publications (1)

Publication Number Publication Date
WO2008046544A1 true WO2008046544A1 (fr) 2008-04-24

Family

ID=39109319

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2007/008796 WO2008046544A1 (fr) 2006-10-20 2007-10-10 Machine hydraulique de travail

Country Status (2)

Country Link
DE (1) DE102007029670A1 (fr)
WO (1) WO2008046544A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9133839B2 (en) 2010-02-23 2015-09-15 Artemis Intelligent Power Limited Fluid-working machine and method of detecting a fault
US9739266B2 (en) 2010-02-23 2017-08-22 Artemis Intelligent Power Limited Fluid-working machine and method of operating a fluid-working machine

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2211058A1 (fr) 2009-01-27 2010-07-28 Sauer-Danfoss ApS Pompe hydraulique
DE102010064262A1 (de) * 2010-12-28 2012-04-26 Continental Automotive Gmbh Pumpe und Verfahren zur Steuerung einer Pumpe
ES2614468T3 (es) 2014-12-30 2017-05-31 Multivac Sepp Haggenmüller Se & Co. Kg Máquina de envasado con un conjunto de bombas de fluido

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2161560A1 (de) * 1971-12-11 1973-06-14 Langen & Co Kolbenpumpe
DE8915720U1 (de) * 1989-12-12 1991-02-28 Hydac Technology GmbH, 6603 Sulzbach Steuervorrichtung zum Festlegen der Fördermenge eines Fluids bei einer Pumpe
US5032065A (en) * 1988-07-21 1991-07-16 Nissan Motor Co., Ltd. Radial piston pump
DE4041800A1 (de) * 1990-12-24 1992-06-25 Teves Gmbh Alfred Pumpeneinrichtung
EP0685644A2 (fr) * 1994-05-06 1995-12-06 Cummins Engine Company, Inc. Pompe à haute pression pour systèmes d'injection de combustible

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2161560A1 (de) * 1971-12-11 1973-06-14 Langen & Co Kolbenpumpe
US5032065A (en) * 1988-07-21 1991-07-16 Nissan Motor Co., Ltd. Radial piston pump
DE8915720U1 (de) * 1989-12-12 1991-02-28 Hydac Technology GmbH, 6603 Sulzbach Steuervorrichtung zum Festlegen der Fördermenge eines Fluids bei einer Pumpe
DE4041800A1 (de) * 1990-12-24 1992-06-25 Teves Gmbh Alfred Pumpeneinrichtung
EP0685644A2 (fr) * 1994-05-06 1995-12-06 Cummins Engine Company, Inc. Pompe à haute pression pour systèmes d'injection de combustible

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9133839B2 (en) 2010-02-23 2015-09-15 Artemis Intelligent Power Limited Fluid-working machine and method of detecting a fault
US9133838B2 (en) 2010-02-23 2015-09-15 Artemis Intelligent Power Limited Fluid-working machine and method of operating a fluid-working machine
US9739266B2 (en) 2010-02-23 2017-08-22 Artemis Intelligent Power Limited Fluid-working machine and method of operating a fluid-working machine

Also Published As

Publication number Publication date
DE102007029670A1 (de) 2008-04-24

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