EP2055949A1 - Procédé de fonctionnement de machine de travail pour fluides - Google Patents

Procédé de fonctionnement de machine de travail pour fluides Download PDF

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Publication number
EP2055949A1
EP2055949A1 EP08016532A EP08016532A EP2055949A1 EP 2055949 A1 EP2055949 A1 EP 2055949A1 EP 08016532 A EP08016532 A EP 08016532A EP 08016532 A EP08016532 A EP 08016532A EP 2055949 A1 EP2055949 A1 EP 2055949A1
Authority
EP
European Patent Office
Prior art keywords
pumping
fluid
motoring
stroke
working 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.)
Ceased
Application number
EP08016532A
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German (de)
English (en)
Inventor
Ken Kin-Ho Lai
Onno Kuttler
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.)
Danfoss Power Solutions ApS
Artemis Intelligent Power Ltd
Original Assignee
Sauer Danfoss ApS
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
Priority claimed from EP07254337A external-priority patent/EP2055946A1/fr
Priority claimed from EP07254332.5A external-priority patent/EP2055944B1/fr
Priority claimed from EP07254333.3A external-priority patent/EP2055945B8/fr
Priority claimed from EP07254331.7A external-priority patent/EP2055943B1/fr
Application filed by Sauer Danfoss ApS filed Critical Sauer Danfoss ApS
Priority to EP08016532A priority Critical patent/EP2055949A1/fr
Publication of EP2055949A1 publication Critical patent/EP2055949A1/fr
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B25/00—Regulating, controlling, or safety means
    • F01B25/02—Regulating or controlling by varying working-fluid admission or exhaust, e.g. by varying pressure or quantity
    • F01B25/08—Final actuators
    • F01B25/10—Arrangements or adaptations of working-fluid admission or discharge valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B25/00—Regulating, controlling, or safety means
    • F01B25/02—Regulating or controlling by varying working-fluid admission or exhaust, e.g. by varying pressure or quantity
    • 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
    • F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
    • F04B11/005—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using two or more pumping pistons
    • 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
    • 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
    • F04B49/243—Bypassing by keeping open the inlet valve
    • 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
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/0076—Piston machines or pumps characterised by having positively-driven valving the members being actuated by electro-magnetic means
    • 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
    • F04B2201/06—Valve parameters
    • F04B2201/0601—Opening times
    • 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
    • F04B2205/00—Fluid parameters
    • F04B2205/09—Flow through the pump
    • 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
    • F04B2205/00—Fluid parameters
    • F04B2205/13—Pressure pulsations after the pump

Definitions

  • the invention relates to a method of operating a fluid working machine, comprising at least one working chamber of cyclically changing volume, a high pressure fluid connection, a low pressure fluid connection and at least one electrically actuated valve, connecting said working chamber to said high pressure fluid connection and/or said low pressure fluid connection, wherein the timing of the actuation of said electrically actuated valve is varied depending on the fluid flow demand.
  • the invention further relates to a fluid working machine, comprising at least one working chamber of cyclically changing volume, a high pressure fluid connection, a low pressure fluid connection, at least one electrically actuated valve, connecting said working chamber to said high pressure fluid connection and/or said low pressure fluid connection and at least one electronic controller unit.
  • fluid working machines are generally used, when fluids are pumped or a fluid is generating a mechanical movement.
  • the word “fluid” can relate to both gases and liquids.
  • the word “fluid” can even relate to a mixture of gas and liquid and furthermore to a supercritical fluid, where no distinction between gas and liquid can be made anymore.
  • such fluid working machines are used, if the pressure level of a fluid has to be increased.
  • a fluid working machine could be an air compressor or a hydraulic pump.
  • fluid working machines comprise one or more working chambers of a cyclically changing volume.
  • a fluid inlet valve and a fluid outlet valve are provided for each cyclically changing volume.
  • the fluid inlet valves and the fluid outlet valves are passive valves.
  • its fluid inlet valve opens, while its fluid outlet valve closes, due to the pressure differences, caused by the volume increase of the working chamber.
  • the fluid inlet valve closes, while the fluid outlet valve opens due to the changed pressure differences.
  • a relatively new and promising approach for improving fluid working machines are the so-called “synthetically commutated hydraulic pumps", also known as “digital displacement pumps”. Such pumps are a subset of variable displacement pumps. Such synthetically commutated hydraulic pumps are known, for example, from EP 0 494 236 B1 or WO 91/05163 A1 .
  • the passive fluid inlet valves are replaced by electrically actuated inlet valves.
  • the passive fluid outlet valves are also replaced by electrically actuated outlet valves.
  • a full-stroke pumping mode, an empty cycle pumping mode (idle mode) and a part-stroke pumping mode can be achieved.
  • the pump can be used as a hydraulic motor as well. If the pump is run as a hydraulic motor, full-stroke motoring and part-stroke motoring is possible, as well.
  • a major advantage of such synthetically commutated hydraulic pumps is their higher efficiency, as compared to traditional hydraulic pumps. Furthermore, because the valves are electrically actuated, the output characteristics of a synthetically commutated hydraulic pump can be changed very quickly.
  • the synthetically commutated hydraulic pump it is, for example, possible to switch the synthetically commutated hydraulic pump to a full pumping mode for a certain time.
  • a high pressure fluid reservoir is filled.
  • the synthetically commutated pump is switched to an idle mode and the fluid flow demand is supplied by the high pressure fluid reservoir.
  • the synthetically commutated hydraulic pump is switched on again.
  • the problem is solved by modifying a method of operating a fluid machine according to the preamble of claim 1 in a way, that the timing of the actuation of said electrically actuated valve is changed at least in part continuously.
  • the (main) input parameter is the fluid flow demand
  • the (main) output parameter is the actuation time (also called actuation angle, firing time or firing angle) of the electrically actuated valve.
  • the actuation of the electrically actuated valve is varied dynamically, depending on the fluid flow demand. Contrary to the state of the art, no fixed fractional value is used anymore. Admittedly, this may cause the problem that the real fluid flow output can only be approximated from the actuation time.
  • At least the pumping/motoring fraction between 0 % and 33.3 % (one third) of the maximum pumping/motoring volume of said working chamber is chosen.
  • the electrically actuated inlet valve is closed a relatively short time before the working chamber reaches its minimum volume. In fluid working machines of the piston and cylinder type this would be close to the top dead center. It has been discovered that closing the electrically actuated valve in other regions could lead to increased noise generation and to an increased wear of the electrically actuated valve. This is because of the sinusoidal change of the working chamber's volume in standard type fluid working machines.
  • the electrically actuated valve is closed in a region of a high change of the working chamber's volume, the speed of the hydraulic fluid entering and/or leaving the working chamber is accordingly high.
  • the mentioned numbers of 0 and 33.3 % for the interval limits are not fixed numbers. Instead, also 5 %, 10 %, 15 %, 20 %, 25 %, 30 %, 35 % and/or 40 % could be used as upper/lower interval limits.
  • the mentioned interval can apply for one, a plurality of or all working chambers and/or for one, a plurality of or all pumping strokes of one, a plurality of or all working chambers.
  • Another preferred embodiment of the invention can be realised, if at least a pumping/motoring fraction between 66.7 % (two thirds) and 100 % of the maximum pumping/motoring volume of said working chamber is chosen.
  • the mentioned numbers are not fixed numbers. Instead, 60 %, 65 %, 70 %, 75 %, 80 %, 85 %, 90 % and/or 95 % can be chosen as upper/lower interval limits as well.
  • the electrically actuated valve will be closed some time after the working chamber has reached its maximum volume and starts to shrink again.
  • Another preferred solution can be obtained, if a pumping/motoring fraction between 33.3 % and 66.7 % of the maximum pumping motoring volume of said working chamber is excluded.
  • This can be considered as a combination of the previously mentioned embodiments.
  • the objects and advantages of this embodiment are similar to the already mentioned objects and advantages. It is noted, that the already mentioned alternative numbers can be used as well.
  • a plurality of different pumping/motoring fractions of a plurality of working chambers and/or a plurality of different pumping/motoring strokes of at least one working chamber are combined in a way, that the time averaged effective pumping/motoring fraction is adjusted to satisfy the fluid-flow demand. Therefore, the fluid-flow output of several working chambers and/or of several pumping/motoring strokes, presumably some or all of a different value can be combined together in a way, that almost any given demand can be satisfied. Particularly, it is possible to combine several pumping/motoring strokes from different regions in a way, that "forbidden" or undesirable volume fractions in the part-stroke modes are omitted.
  • an alternating 25 % part-stroke pulse and a 75 % part-stroke pulse will sum up to an effective time average of a 50 % part-stroke mode.
  • the pressure variations can still be lower as compared to an alternating series of 0 % and 100 % stroke pulses, as it is done according to the state of the art.
  • At least one calibration point is used for deriving the pumping/motoring actuation angle(s) from the fluid-flow demand.
  • the system can be set up in a way, that the value of the fluid outflow of the system can be very close to the value of the demand. Even then, only a very limited set of measurements can be sufficient to set up the limited amount of calibration points.
  • a combination of two or more of these parameters can be used as well.
  • a look up table could be used as well. This look up table can be stored in a memory device, e. g. in the electronic controller unit.
  • a fluid-flow machine comprising at least one working chamber of cyclically changing volume, a high pressure fluid connection, a low pressure fluid connection, at least one electrically actuated valve, connecting said working chamber to said high pressure fluid connection and/or said low pressure fluid connection and at least one electronic controller unit, wherein said electronic controller unit is designed and arranged in a way, that the electronic controller unit actuates said electrically actuated valve according to one or several embodiments of previously described method. If several working chambers are present, a high-pressure fluid manifold and/or a low pressure fluid manifold can be used.
  • the fluid working machine can be of a type, where only the fluid inlet valves of the working chambers is electrically actuated. Such a fluid working machine should only be used as a pump. Of course it is also possible, that both the inlet and the outlet valves are of the electrically actuated type. Such a fluid working machine could be used as a pump as well as a hydraulic motor. The hydraulic working machine could be of a commonly known piston-and-cylinder type.
  • Fig. 1 shows the schematic overview of a synthetically commutated hydraulic pump, comprising one bank 2 with six cylinders 3.
  • the cylinders 3 are connected to a single rotatable shaft 4, that is common to all cylinders 3.
  • the cylinders 3 are comprising a cylinder portion 5 and a piston 6, each.
  • each cylinder 3 starts its working cycle at a different time during the rotation of the rotatable shaft 4, i. e. at a different angle of the rotatable shaft 4.
  • the six cylinders 3 are arranged at regular intervals. Therefore, the phase difference between two neighbouring cylinders 3 is 60 %.
  • cylinders 3 i. e. four, five, seven or eight cylinders or any other integer number (it can be even or odd).
  • a different number of cylinder banks 2 may be provided.
  • the cylinders 3 in one or several banks 2 of the synthetically commutated hydraulic pump 1 may be arranged at non-equidistant angles.
  • the number of cylinders 3 in different banks 2 of the synthetically commutated hydraulic pump 1 needs not to be the same.
  • one bank 2 might comprise six cylinders 3, while a second bank 2 of the synthetically commutated hydraulic pump 1 comprises just three cylinders 3.
  • piston-and-cylinder pumps are possible. Instead, other types of pumps can take advantage of the invention as well.
  • the cylinders 3 have a working chamber 7 of a cyclically changing volume.
  • the working chamber 7 is connected to a low-pressure hydraulic fluid manifold 34 via an electrically actuated inlet valve 8 and to a high-pressure hydraulic fluid manifold 35 via an outlet valve 9, as it is known in the art.
  • the outlet valves 9 can be of a passive type (e.g. a spring loaded poppet valve).
  • the outlet valves 9 can also be of an electrically actuated type, as shown in Fig. 1 . In the latter case, the synthetically commutated hydraulic pump 1 can be used as a hydraulic motor as well.
  • a valve which is an inlet valve 8 when the fluid working machine 1 is used as a hydraulic pump, will become an outlet valve, if the fluid working machine is used as a hydraulic motor and vice versa.
  • the actuation of the electrically actuated valves 8, 9 is done by an electronic controller 33.
  • the main input values for the electronic controller 33 are the shaft's 4 angular position 32 and the current fluid flow demand.
  • the shaft's angular position is measured by an appropriate sensor 36.
  • the position of the piston 6 relative to the cylinder portion 5 of each cylinder 3 can be determined.
  • the other main input parameter is the actual fluid flow demand.
  • opening and closing of the inlet valve 8 is chosen in a way, that the respective cylinder 3 is working in an idle mode, a part-stroke mode or a full-stroke mode.
  • the inlet valve 8 remains open, so that no effective pumping to the high pressure manifold 35 is performed.
  • the full stroke mode the inlet valve 8 is closed at the bottom dead center of the respective cylinder 3. Therefore, the complete usable volume of the respective working chamber 7 is used for pumping.
  • the firing angle (actuation time, firing time, actuation angle) of the inlet valve 8 is chosen in a way, that the fraction of the volume of the working chamber 7 which is used for pumping is adapted to and varied with the actual fluid flow demand.
  • pressure information being indicative of the pressure in the high pressure manifold 35 or the output value of a fluid flow meter can be used. Such information can be used for refining the exact actuation angle of the electrically actuated valves 8.
  • Fig. 2 shows the principal flow diagram 10 of the electronic controller.
  • the fluid flow demand 11 is input to the accumulator 14 via an adding unit 12.
  • the adding unit 12 also takes into account the actual pumping work, performed by the synthetically commutated pump 1 using a feedback signal 13.
  • the accumulator 14 is a variable, adding up a fluid flow demand 11, which cannot be satisfied by the hydraulic pump 1 at least partially. This could happen, for example, if the fluid flow demand 11 lies within a "forbidden interval", as it will be explained later.
  • the quantisation unit 15 makes a decision'about the fraction of the working chamber's volume 7, which has to be used for pumping. Based on this decision, the firing angle of the electrically actuated valves 8, 9 is determined, and an appropriate actuation signal 16 is sent to the electrically actuated valves 8, 9.
  • the firing angle 17, at which the inlet valve 8 is actuated lies somewhere between the bottom dead center (BDC) and the top dead center (TDC). If the inlet valve 8 is closed at firing angle 17, only the remaining volume of the working chamber 7 can be used for pumping. This is indicated by the hatched area, whereas the length 37 of the respective area in the direction of the ordinate is proportional (by piston area) to the pumping displacement.
  • the connection between firing angle 17 and the fractional pumping volume is normally not linear but approximately sinusoidal. In real applications, the curve is even further modified. This is for example due to compressibility effects and dead volumes within the cylinder portions 5 of the cylinders 3 or to the kinematics of the eccentric rotatable shaft 4.
  • valves which are normally the output valves 9 (i. e. the valves connecting the working chambers 7 to the high pressure fluid manifold) are used as inlet valves and have to be of the electrically actuated type as well.
  • the firing angle 18 a part of the downward stroke of the piston 6 within the cylinder portion 5 is used for driving the rotable shaft.
  • the length 38 of the hatched area in the direction of the ordinate is proportional to the motoring displacement.
  • the shape of the curve 19, showing the pumping fraction is normally not known.
  • the curve 19 could be determined by measurements in principle, it has to be understood, that the pumping fraction 19 not only depends on the firing angle, but also on different parameters, like the rotation speed of the shaft, the pressure conditions in the high-pressure fluid manifold or the temperature of the hydraulic oil. Therefore, an accordingly large number of measurements would be necessary to measure these conditions for the entire operational range, which is too time-consuming and expensive for practical applications.
  • connection should be continuous. I. e., the operator should receive more power, when he is forwarding the lever, and should receive less power, if he is taking back the lever. Ideally, there should be no noticeable steps or changes in the slope of the function between demand and actual output of the pump. Therefore, the curve 19 should also be continuous and show roughly the same slope in the whole accessible region.
  • a synthetically commutated hydraulic pump 1 as depicted in Fig. 1 .
  • the number of cylinders 3 is 6 and the number of banks 2 is 1.
  • the phases of the six cylinders 3 are equally spaced within a full revolution of the rotatable shaft 4, i.e., 60° out of phase from each other.
  • a fluid flow demand 23 of 2 % of the maximum fluid flow of the hydraulic pump 1 is shown.
  • the accumulator 14 sums up the 2 % demand 11. This will continue for eight decision points (i. e. eight times a 60° movement of the rotable shaft 4).
  • the accumulator 14 finally reaches 16 %. Therefore, a 16 % part-stroke pumping cycle will be initiated. This can be seen from the overall pumping output curve 25. This pumping output 25 is considered via the feedback signal line 13 and decreases the value of the accumulator 14 accordingly.
  • the accumulator 14 will again slowly build up, until another part-stroke pumping is initiated. As can be seen from Fig. 5 , the time interval between two pumping strokes is quite large.
  • variable part stroke pumping This is much better with the suggested variable part stroke pumping, which is illustrated in Fig. 6 .
  • the 2 % value of the accumulator 14 will trigger a 2 % part-stroke pumping.
  • the output flow is therefore a series of identical small volume pulses.
  • the pressure pulses will be much smaller. Also, the response time will be faster.
  • Fig. 7 and 8 show a change from a 16 % demand to a 17 % demand.
  • Fig. 7 the behaviour of a synthetically commutated hydraulic pump, having a part-stroke mode with a fixed part-stroke fraction of 16 % is shown.
  • the fluid flow demand 23 equals 16 %. This is equivalent to the volume fraction of the part stroke volume. Therefore, one part-stroke pumping cycle is initiated at each decision point. This way, the accumulator 24 remains constant and equals the demand 23.
  • the situation changes, when the demand increases slightly above the volume fraction of the part-stroke volume. In the example of Fig. 7 , the demand is increased to a slightly higher demand 26 of 17 %.
  • the part-stroke mode is inhibited, because the elevated demand 26 is higher than the volume fraction of the part-stroke mode. Consequently, the demand causes the accumulator 24 to increase step by step, until the accumulator 24 reaches the 100 % threshold. Then a full-stroke cycle 27 is performed. The accumulator 24 drops accordingly and builds up again, until the 100 % threshold is reached again and another full-stroke cycle is initiated.
  • a continuation of part stroke pulses with 16 % volume fraction would even worsen the situation. This is, because the basic load would be mostly covered by part-stroke pulses and the accumulator 24 would therefore require an even longer time, until it reaches the threshold for a full stroke cycle 27 to be initiated.
  • variable part stroke method ( Fig. 8 )
  • the differences when jumping from the 16 % demand 23 to the 17 % increased demand 26 are almost negligible.
  • the only difference is, that the variable part stroke cycle will actuate the electrically actuated valve 8 a little bit earlier, so that a higher fraction is pumped.
  • the output characteristics of the fixed part stroke method and the variable part stroke method are compared to each other, when the demand 23 is set to 90 %.
  • the single pumping strokes 29 are chosen in a way, that the pumped fraction amounts to 90 %, which is exactly equal to the demand 23. Therefore, no single pumping stroke will be omitted, and therefore, the total output flow 25 will show no ditch 28, i. e. will be more homogeneous.
  • variable part stroke method may comprise a "forbidden interval" in various situations, as described. Because of the sinusoidal motion of the pistons 6 within the cylinder portion 5 of each cylinder 3, the fluid speed of the hydraulic oil flowing around the opened valve heads of the inlet valve 8 varies in a sinusoidal way as well.
  • variable part stroke method can be superior to the fixed part stroke pumping method.
  • the demand 23 is chosen to be 30 %.
  • accumulator 24 builds up until a single full stroke cycle is initiated.
  • a series of three full stroke cycles 27 with a gap 28 in-between each series is performed.
  • the fluid flow output 25 is much more homogeneous.
  • the method will lock in with groups of four strokes, wherein each group shows three small strokes 30 (at 25 % volume fraction) and one large stroke 31 (with 75 % volume fraction).
  • Table 1 shows the numerical values of the curves, shown in Fig. 11
  • Table 2 shows the numerical development of the curves, shown in Fig. 12 .
  • the value of the interval for the allowed pumping fractions of the part stroke pulses can be dependent on the actual speed of the fluid, leaving the working chamber 7, as well.
  • This decision on fluid speed instead of the firing angle is normally advantageous, in that it links the problem with the real course.
  • the fluid speed can be determined by the shaft speed of the fluid working machine and the angular position of shaft 4.
  • this method can be implemented in a way, that the limiting value of the firing angle is chosen to be a function of the shaft speed of the fluid working machine.
EP08016532A 2007-11-01 2008-09-19 Procédé de fonctionnement de machine de travail pour fluides Ceased EP2055949A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP08016532A EP2055949A1 (fr) 2007-11-01 2008-09-19 Procédé de fonctionnement de machine de travail pour fluides

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
EP07254337A EP2055946A1 (fr) 2007-11-01 2007-11-01 Procédé de fonctionnement de machine de travail pour fluides
EP07254332.5A EP2055944B1 (fr) 2007-11-01 2007-11-01 Procédé de contrôle de pompe hydraulique commutée cycliquement
EP07254333.3A EP2055945B8 (fr) 2007-11-01 2007-11-01 Procédé pour la commande d'une machine de travail pour fluides
EP07254331.7A EP2055943B1 (fr) 2007-11-01 2007-11-01 Procédé pour la commande d'une machine de travail pour fluides
EP08016532A EP2055949A1 (fr) 2007-11-01 2008-09-19 Procédé de fonctionnement de machine de travail pour fluides

Publications (1)

Publication Number Publication Date
EP2055949A1 true EP2055949A1 (fr) 2009-05-06

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Family Applications (4)

Application Number Title Priority Date Filing Date
EP08016533.5A Active EP2055950B1 (fr) 2007-11-01 2008-09-19 Procédé de contrôle de pompe hydraulique commutée cycliquement
EP08016531A Active EP2055948B1 (fr) 2007-11-01 2008-09-19 Procédé de contrôle de pompe hydraulique commutée cycliquement
EP08016530A Active EP2055947B1 (fr) 2007-11-01 2008-09-19 Procédé de contrôle de pompe hydraulique commutée cycliquement
EP08016532A Ceased EP2055949A1 (fr) 2007-11-01 2008-09-19 Procédé de fonctionnement de machine de travail pour fluides

Family Applications Before (3)

Application Number Title Priority Date Filing Date
EP08016533.5A Active EP2055950B1 (fr) 2007-11-01 2008-09-19 Procédé de contrôle de pompe hydraulique commutée cycliquement
EP08016531A Active EP2055948B1 (fr) 2007-11-01 2008-09-19 Procédé de contrôle de pompe hydraulique commutée cycliquement
EP08016530A Active EP2055947B1 (fr) 2007-11-01 2008-09-19 Procédé de contrôle de pompe hydraulique commutée cycliquement

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EP (4) EP2055950B1 (fr)
AT (2) ATE475014T1 (fr)
DE (2) DE602008001854D1 (fr)

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WO2012150383A2 (fr) 2011-05-05 2012-11-08 Teknologian Tutkimuskeskus Vtt Procédé de modification de la surface d'un corps

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EP2775144B1 (fr) 2010-02-23 2018-09-26 Artemis Intelligent Power Limited Synchronisation de vanne de machine entraînée par fluide
GB2477997B (en) * 2010-02-23 2015-01-14 Artemis Intelligent Power Ltd Fluid working machine and method for operating fluid working machine
JP5576929B2 (ja) 2010-02-23 2014-08-20 アルテミス インテリジェント パワー リミティド 流体作動機および流体作動機の動作方法
AU2018204487B1 (en) * 2017-11-10 2019-05-30 Quantum Servo Pumping Technologies Pty Ltd Pumping systems
EP3674546B1 (fr) 2018-12-28 2022-07-13 Artemis Intelligent Power Limited Synchronisation de soupape dans une machine hydraulique commutée électroniquement

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WO1991005163A1 (fr) 1988-09-29 1991-04-18 The University Of Edinburgh Machine a fonctionnement fluidique ameliore
EP1537333B1 (fr) 2002-09-12 2006-06-14 Artemis Intelligent Power Ltd. Machine de travail fluidique et methode d'utilisation

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ATE475014T1 (de) 2010-08-15
EP2055950B1 (fr) 2017-04-12
DE602008001854D1 (de) 2010-09-02
EP2055947A1 (fr) 2009-05-06
DE602008001855D1 (de) 2010-09-02
ATE475013T1 (de) 2010-08-15
EP2055948B1 (fr) 2010-07-21
EP2055950A1 (fr) 2009-05-06
EP2055948A1 (fr) 2009-05-06
EP2055947B1 (fr) 2010-07-21

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