EP2878816B1 - Pump control device - Google Patents

Pump control device Download PDF

Info

Publication number
EP2878816B1
EP2878816B1 EP14773145.9A EP14773145A EP2878816B1 EP 2878816 B1 EP2878816 B1 EP 2878816B1 EP 14773145 A EP14773145 A EP 14773145A EP 2878816 B1 EP2878816 B1 EP 2878816B1
Authority
EP
European Patent Office
Prior art keywords
pressure
spool
discharge
pump
signal
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.)
Active
Application number
EP14773145.9A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2878816A4 (en
EP2878816A1 (en
Inventor
Midori NAGASHIMA
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.)
KYB Corp
Original Assignee
KYB Corp
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 KYB Corp filed Critical KYB Corp
Publication of EP2878816A1 publication Critical patent/EP2878816A1/en
Publication of EP2878816A4 publication Critical patent/EP2878816A4/en
Application granted granted Critical
Publication of EP2878816B1 publication Critical patent/EP2878816B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/26—Control
    • F04B1/30—Control of machines or pumps with rotary cylinder blocks
    • F04B1/306—Control of machines or pumps with rotary cylinder blocks by turning the swash plate, e.g. with fixed inclination
    • 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
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/26—Control
    • F04B1/30—Control of machines or pumps with rotary cylinder blocks
    • F04B1/32—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block
    • F04B1/324—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash plate
    • 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
    • F04B49/002—Hydraulic systems to change the pump delivery
    • 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
    • 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

Definitions

  • the present invention relates to a pump control apparatus for controlling a discharge capacity of a pump.
  • a conventional driving pressure source for a hydraulic device installed in a construction machine such as a hydraulic shovel may employ a swash plate type multiple piston pump that is driven to rotate by an engine.
  • the piston pump includes two sets of an intake port and a discharge port, and discharges working oil from the respective discharge ports.
  • JP2008-291732A discloses a pump control apparatus that controls a discharge capacity of a swash plate type multiple piston pump.
  • the pump control apparatus includes a regulator that controls a tilt angle of the swash plate so that a power of the piston pump remains constant, and an average discharge pressure obtained by averaging discharge pressures led from respective discharge ports is used as a source pressure led to the regulator.
  • JP2008-240518A discloses a regulator that is provided in a piston pump driven by an engine in order to control a discharge capacity of the pump in accordance with a signal pressure led thereto when a device such as an air conditioner is operated.
  • JP2008-280942 shows a a pump control apparatus for controlling a discharge capacity of a pump that discharges a working fluid through a plurality of discharge ports, comprising:an actuator that varies the discharge capacity of the pump; and a regulator that regulates a control pressure led to the actuator, the regulator comprising:a driving pressure port to which an average discharge pressure obtained by averaging respective discharge pressures of the working fluid discharged from the plurality of discharge ports is led; a source pressure port to which a high pressure side discharge pressure, which is the highest discharge pressure of the working fluid discharged from the plurality of discharge ports, is led; a signal pressure port to which a signal pressure is led; and a spool that regulates the control pressure.
  • a spool forming the regulator must be increased in size in response to an increase in a number of signal pressures, and as a result, the regulator increases in structural complexity.
  • An object of the present invention which is defined by the appended claims, is to provide a pump control apparatus that controls a discharge capacity of a pump using a regulator having a simple structure even when the number of signal pressures increases.
  • a pump control apparatus for controlling a discharge capacity of a pump that discharges a working fluid from a plurality of discharge ports.
  • the pump control apparatus includes: an actuator that varies the discharge capacity of the pump; and a regulator that regulates a control pressure led to the actuator.
  • the regulator includes: a driving pressure port to which an average discharge pressure obtained by averaging respective discharge pressures of the working fluid discharged from the plurality of discharge ports is led; a source pressure port to which a high pressure side discharge pressure, which is the highest discharge pressure of the working fluid discharged from the plurality of discharge ports, is led; a signal pressure port to which a signal pressure is led; and a spool that regulates the control pressure using the high pressure side discharge pressure as a source pressure by moving upon reception of the average discharge pressure and the signal pressure, wherein a driving pressure receiving surface that receives the average discharge pressure is formed inside the spool, and a signal pressure receiving surface that receives the signal pressure is formed in an outer peripheral step portion of the spool.
  • FIG. 1 is a view showing a hydraulic circuit of a pump control apparatus 1 according to this embodiment of the present invention.
  • the pump control apparatus 1 is an apparatus for driving a hydraulic device installed in a construction machine such as a hydraulic shovel, for example.
  • the pump control apparatus 1 controls a discharge capacity (a pump displacement) of a variable capacity pump 11.
  • variable capacity pump 11 is a swash plate type multiple piston pump, for example, that includes one intake port and two discharge ports.
  • variable capacity pump 11 is driven by an engine 10 to suction working oil through the intake port from a tank port 30 connected to a tank via an intake passage 20, and discharge the working oil, which is pressurized by a piston that reciprocates so as to follow a swash plate 15, through the respective discharge ports.
  • the working oil discharged from the respective discharge ports is distributed to respective hydraulic cylinders for driving a boom, an arm, and a bucket of the hydraulic shovel, left and right travel motors, and so on via a first discharge passage 21, a second discharge passage 22, pump ports 31, 32, and control valves (not shown).
  • a part of the working oil is discharged from one of the discharge ports at a pressure P1 and supplied to the left travel motor through the first discharge passage 21.
  • Another part of the working oil is discharged from the other discharge port at a pressure P2 and supplied to the right travel motor through the second discharge passage 22.
  • the pump control apparatus 1 includes a first fixed capacity pump 12 and a second fixed capacity pump 13 that are disposed coaxially with the variable capacity pump 11.
  • the first fixed capacity pump 12 and second fixed capacity pump 13 are pumps having a fixed discharge capacity, and are driven by the engine 10, which also serves as a drive source of the variable capacity pump 11.
  • gear pumps are used as the first fixed capacity pump 12 and the second fixed capacity pump 13, but the embodiment is not limited thereto.
  • the first fixed capacity pump 12 suctions working oil through an intake passage 25 that branches off from the intake passage 20, and delivers the pressurized working oil to a pump port 39 via a third discharge passage 23.
  • This working oil is supplied via a control valve connected to the pump port 39 to a turning motor or the like for turning a cab (a driving seat) of the hydraulic shovel.
  • the second fixed capacity pump 13 suctions working oil through an intake passage 26 that branches off from the intake passage 25, and delivers the pressurized working oil to a signal pressure port 34 via a signal pressure passage 24.
  • This working oil is supplied through a signal pressure passage (not shown) connected to the signal pressure port 34 to a hydraulic drive unit or the like that switches the respective control valves.
  • working oil is used as the working fluid that is supplied to and discharged from the variable capacity pump 11, the first fixed capacity pump 12, and the second fixed capacity pump 13.
  • a working fluid such as an aqueous replacement fluid, for example, may be used instead of working oil.
  • the variable capacity pump 11 which is constituted by a swash plate type piston pump, includes a cylinder block that is driven to rotate by the engine 10, a piston that reciprocates through a cylinder of the cylinder block so as to discharge the suctioned working oil, the swash plate 15 that follows the piston, horsepower control springs 48, 49 that bias a tilt angle of the swash plate 15 in an increasing direction, a small diameter actuator 47 that drives the swash plate 15 in a same direction to a spring force of the horsepower control springs 48, 49, a large diameter actuator 16 that drives the swash plate 15 against the spring force of the horsepower control springs 48, 49 and a driving force of the small diameter actuator 47, and a casing that houses these components.
  • the multiple variable capacity pump 11 includes the single intake port and the two discharge ports, and in the cylinder block, a cylinder that communicates with the first discharge passage 21 and a cylinder that communicates with the second discharge passage 22 are provided.
  • variable capacity pump 11 The discharge capacity of the variable capacity pump 11 is varied by driving the large diameter actuator 16 in order to vary the tilt angle of the swash plate 15, thereby varying a piston stroke of the piston that reciprocates so as to follow the swash plate 15.
  • the large diameter actuator 16 reduces the tilt angle of the swash plate 15 in accordance with an increase in a control pressure Pcg led thereto.
  • the discharge capacity of the variable capacity pump 11 decreases as the tilt angle of the swash plate 15 decreases.
  • the pump control apparatus 1 includes a load sensing regulator 60 (referred to as an "LS regulator 60" hereafter) that regulates the control pressure Pcg led to the large diameter actuator 16, and a horsepower control regulator 40 that regulates a working oil pressure (a control pressure) Pc led to the LS regulator 60.
  • LS regulator 60 load sensing regulator 60
  • a horsepower control regulator 40 that regulates a working oil pressure (a control pressure) Pc led to the LS regulator 60.
  • a throttle 57 is interposed in a second control pressure passage 56.
  • the throttle 57 reduces pressure variation in the control pressure Pcg led to the large diameter actuator 16.
  • the control pressure Pcg generated in the second control pressure passage 56 is extracted through a control pressure port 35 and detected by a pressure sensor.
  • the horsepower control regulator 40 is a three-port, two-position switch valve having a spool 70 (see FIG. 2 ) that switches a position of the horsepower control regulator 40 to a position a or a position b.
  • the spring force of the horsepower control springs 48, 49 is exerted on the spool 70, and an average discharge pressure Pave obtained by averaging the discharge pressure P1 and the discharge pressure P2 of the working oil discharged through the respective discharge ports is led to the spool 70 through a discharge pressure signal passage 63 as a signal pressure (a driving pressure) that counteracts the spring force.
  • the spool 70 moves to a position in which the average discharge pressure Pave and the spring force of the horsepower control springs 48, 49 are counterbalanced. As a result, the position of the horsepower control regulator 40 is switched to the position a or the position b.
  • the discharge pressure signal passage 63 includes a first discharge pressure signal passage 61 and a second discharge pressure signal passage 62 that branches off respectively from the first discharge passage 21 and the second discharge passage 22.
  • a throttle 64 is provided in the first discharge pressure signal passage 61.
  • a throttle 65 is provided in the second discharge pressure signal passage 62.
  • the discharge pressure P1 generated in the first discharge passage 21 is led to the discharge pressure signal passage 63 through the throttle 64, and the discharge pressure P2 generated in the second discharge passage 22 is led to the discharge pressure signal passage 63 through the throttle 65. Accordingly, the average discharge pressure Pave serving as the average of the discharge pressure P1 and the discharge pressure P2 is generated in the discharge pressure signal passage 63. The average discharge pressure Pave is also extracted through an average discharge pressure port 32.
  • the horsepower control springs 48, 49 are coupled to the spool 70 at one end and linked to the swash plate 15 at another end.
  • a spring length of the horsepower control spring 49 is shorter than a spring length of the horsepower control spring 48 so that the spring force of the horsepower control springs 48, 49 increases in steps in accordance with the tilt angle of the swash plate 15 and a stroke of the spool 70.
  • the horsepower control regulator 40 regulates a source pressure led to a first control pressure passage 55 from a source pressure passage 53, and a working oil pressure (a control pressure) Pc that is discharged into a low pressure passage 59 from the first control pressure passage 55 so as to be led to the LS regulator 60.
  • the source pressure passage 53 includes a first source pressure passage 51 and a second source pressure passage 52 that branch off respectively from the first discharge passage 21 and the second discharge passage 22, and a high pressure selection valve 50 that generates the higher of the working oil pressure P1 generated in the first source pressure passage 51 and the working oil pressure P2 generated in the second source pressure passage 52 selectively in the source pressure passage 53.
  • the higher of the working oil pressure P1 led into the first source pressure passage 51 from the first discharge passage 21 and the working oil pressure P2 led into the second source pressure passage 52 from the second discharge passage 22 is extracted by the high pressure selection valve 50, and led to the horsepower control regulator 40 and the small diameter actuator 47 through the source pressure passage 53.
  • the horsepower control regulator 40 regulates the working oil pressure Pc such that a signal pressure based on the average discharge pressure Pave and the spring force of the horsepower control springs 48, 49 are counterbalanced.
  • a signal pressure passage 29 that branches off from the third discharge passage 23 is connected to the horsepower control regulator 40, and a discharge pressure (referred to hereafter as a "second signal pressure") P3 of the first fixed capacity pump 12, which is led to the spool 70 through the signal pressure passage 29, acts on the horsepower control regulator 40 in a direction that counteracts the spring force.
  • the second signal pressure P3 is also extracted through a second signal pressure port 39.
  • an external signal pressure passage 28 is connected to the horsepower control regulator 40, and a horsepower control signal pressure Pi led to the horsepower control regulator 40 through the external signal pressure passage 28 acts on the spool 70 in a same direction to the spring force.
  • the horsepower control signal pressure Pi increases, the spool 70 of the horsepower control regulator 40 moves in a direction for switching to the position b, leading to a reduction in the working oil pressure Pc.
  • the LS regulator 60 is a three-port, two-position switch valve that includes a spool for switching the position of the LS regulator 60 to a position c or a position d.
  • a signal pressure Pps generated on an upstream side of the control valve is led to one end of a spool of the LS regulator 60 from a signal port 36 through a signal passage 43.
  • a signal pressure Pls generated on a downstream side of the control valve is led to another end of the spool of the LS regulator 60 from a signal pressure port 37 through a signal passage 44. Furthermore, a spring force of an LS spring 14 is exerted on the other end of the spool of the LS regulator 60.
  • the spool of the LS regulator 60 moves to a position in which an LS differential pressure (Pps-Pls) generated before and after the control valve and the spring force of the LS spring 14 exerted on the other end of the spool are counterbalanced. As a result, the position of the LS regulator 60 is switched to the position c or the position d.
  • Pps-Pls LS differential pressure
  • the LS differential pressure (Pps-Pls) decreases as a result, the spool of the LS regulator 60 is held in the position c by the spring force of the LS spring 14, as shown in FIG. 1 .
  • the first control pressure passage 55 connected to the horsepower control regulator 40 communicates with the second control pressure passage 56 connected to the large diameter actuator 16, and therefore the control pressure Pcg led to the large diameter actuator 16 from the LS regulator 60 takes a value based on the value Pc regulated by the horsepower control regulator 40.
  • the signal pressure (the load pressure) Pls decreases.
  • the LS differential pressure (Pps-Pls) increases as a result, the spool of the LS regulator 60 is moved in a direction for switching to the position d against the spring force of the LS spring 14.
  • the source pressure passage 54 branching off from the second discharge passage 22, to which the discharge pressure P2 is led communicates with the second control pressure passage 56 connected to the large diameter actuator 16, and as a result, the control pressure Pcg increases.
  • the LS regulator 60 regulates the control pressure Pcg led to the large diameter actuator 16 so that the LS differential pressure and the spring force of the LS spring 14 are counterbalanced.
  • the discharge capacity of the variable capacity pump 11 is controlled such that the LS differential pressure (Pps-Pls) remains substantially constant irrespective of variation in the load on the hydraulic cylinders.
  • a throttle 66 is provided in the first control pressure passage 55, and a throttle 67 is provided in the source pressure passage 54. As a result, pressure variation in the source pressure led to the LS regulator 60 is reduced.
  • a control pressure connecting passage 69 communicates with the first control pressure passage 55 and the second control pressure passage 56.
  • a throttle 18 and a check valve 17 are provided in the control pressure connecting passage 69.
  • the check valve 17 is closed in a normal condition where the control pressure Pcg in the second control pressure passage 56 is higher than the working oil pressure Pc in the first control pressure passage 55.
  • the check valve 17 opens such that the working oil pressure Pc in the first control pressure passage 55 is led to the large diameter actuator 16 through the second control pressure passage 56 that bypasses the LS regulator 60.
  • the pump control apparatus 1 includes a regulating mechanism for increasing a discharge flow rate of the variable capacity pump 11 in accordance with an increase in a pump rotation speed of the second fixed capacity pump 13.
  • the regulating mechanism is constituted by a throttle 27 interposed in the signal pressure passage 24 through which the working oil discharged from the second fixed capacity pump 13 is led, and a control pressure actuator 90 that drives the spool of the LS regulator 60 in accordance with a front-rear differential pressure of the throttle 27.
  • An upstream pressure P4 of the throttle 27 in the signal pressure passage 24 is led to the control pressure actuator 90 through an upstream side control pressure connecting passage 94, and a downstream pressure P5 of the throttle 27 is led to the control pressure actuator 90 through a downstream side control pressure connecting passage 95.
  • FIG. 2 is a sectional view of the horsepower control regulator 40 according to this embodiment of the present invention.
  • the horsepower control regulator 40 includes a tubular housing 100 having a spool housing hole 110, and the columnar spool 70, which is housed in the spool housing hole 110 to be free to slide.
  • the housing 100 is attached to the casing of the variable capacity pump 11.
  • the spool 70 has a tip end portion that projects from an open end of the spool housing hole 110, and a spring bearing is attached to the tip end portion.
  • the horsepower control springs 48, 49 are interposed between the spring bearing and a feedback pin that moves in conjunction with the swash plate 15 of the variable capacity pump 11.
  • a plug 140 is screwed, and thereby attached, to a base end portion of the housing 100.
  • the spool 70 is biased in a direction heading toward the plug 140 (a leftward direction in FIG. 2 ) by the horsepower control springs 48, 49 such that the base end thereof impinges on the plug 140, and as a result, the stroke of the spool 70 is restricted.
  • a back pressure chamber 130 is formed between the housing 100, the base end portion of the spool 70, and the plug 140.
  • the back pressure chamber 130 communicates with the interior (on a tank side) of the casing of the variable capacity pump 11 through a through hole.
  • An axial hole 79 extending in an axial direction is formed as an opening in the base end of the spool 70.
  • a stepped columnar pin 96 is housed in the axial hole 79 to be free to slide.
  • the pin 96 includes a large diameter pin portion 98 that impinges on the plug 140, a small diameter pin portion 97 that is thinner than the large diameter pin portion 98, and a pin outer peripheral step portion 99 formed between the large diameter pin portion 98 and the small diameter pin portion 97.
  • the housing 100 includes five ports 101 to 105.
  • the ports 101 to 105 extend in a radial direction of the spool 70 and open into the spool housing hole 110.
  • the ports 101 to 105 communicate respectively with the passages 55, 53, 63, 29, 28 (see FIG. 1 ) described above via respective annular grooves formed in an outer periphery of the spool 70.
  • a control pressure port 101 constitutes the first control pressure passage 55.
  • the working oil pressure (control pressure) Pc that is led to the large diameter actuator 16 via the LS regulator 60 in response to an operation of the spool 70 is generated in the control pressure port 101.
  • a source pressure port 102 constitutes the source pressure passage 53.
  • the higher of the discharge pressures P1, P2 of the first discharge passage 21 and the second discharge passage 22 is led to the source pressure port 102.
  • a driving pressure port 103 constitutes the discharge pressure signal passage 63.
  • the average discharge pressure Pave obtained by averaging the discharge pressures P1, P2 of the working fluid discharged from the respective discharge ports of the variable capacity pump 11 is led to the driving pressure port 103.
  • a second signal pressure port 104 constitutes the signal pressure passage 29.
  • the pressure P3 of the working oil supplied to the turning motor from the first fixed capacity pump 12 is led to the second signal pressure port 104.
  • a first signal pressure port 105 constitutes the external signal pressure passage 28.
  • the horsepower control signal pressure Pi used to switch an operating mode is led to the first signal pressure port 105.
  • a tank pressure port connecting hole 71, a driving pressure port connecting hole 72, and a second signal pressure connecting hole 73 are formed in the spool 70.
  • These port connecting holes 71 to 73 extend in the radial direction of the spool 70, and respective ends thereof on both sides open onto annular grooves formed in the outer periphery of the spool 70.
  • a tank pressure port 74 is formed in the tip end portion of the spool 70.
  • the tank pressure port 74 extends in the axial direction of the spool 70 such that one end thereof opens into the tank pressure port connecting hole 71, and another end opens at the tip end of the spool 70 so as to communicate with the interior (on the tank side) of the casing of the variable capacity pump 11.
  • the tank pressure port 74 discharges the working oil pressure Pc into the casing.
  • the land portions 81, 82 open the tank pressure port connecting hole 71 and the source pressure port 102 selectively onto the spool housing hole 110, and as a result, the working oil pressure (control pressure) generated in the control pressure port 101 is regulated.
  • the land portion 81 blocks communication between the tank pressure port connecting hole 71 and the control pressure port 101, and the land portion 82 blocks communication between the source pressure port 102 and the control pressure port 101.
  • the tank pressure port connecting hole 71 communicates with the control pressure port 101, and as a result, the working oil pressure Pc is discharged into the case so as to decrease.
  • the land portion 82 blocks communication between the source pressure port 102 and the control pressure port 101.
  • the source pressure port 102 and the control pressure port 101 communicate such that the higher of the discharge pressures P1, P2 led to the source pressure passage 53 is led to the LS regulator 60 through the first control pressure passage 55.
  • the working oil pressure Pc increases.
  • the land portion 81 blocks communication between the tank pressure port connecting hole 71 and the control pressure port 101.
  • the driving pressure port connecting hole 72 and the driving pressure port 103 communicate with each other at all times, regardless of the position of the spool 70.
  • the land portion 83 blocks communication between the driving pressure port 103 and the source pressure port 102, and the land portion 84 blocks communication between the driving pressure port 103 and the second signal pressure port 104.
  • a tip end 95A of the pin 96 projecting from the open end of the axial hole 79 faces a center of the driving pressure port connecting hole 72.
  • a site on an inner wall surface of the driving pressure port connecting hole 72 that opposes the tip end 95A of the pin 96 constitutes a driving pressure receiving surface 72A.
  • the driving pressure receiving surface 72A has a pressure receiving surface area that corresponds to a sectional area of the small diameter pin portion 97.
  • a recessed portion 89 is formed in the site on the inner wall surface of the driving pressure port connecting hole 72 that opposes the tip end 95A of the pin 96.
  • the recessed portion 89 is formed coaxially with the axial hole 79 so that the tip end 95A of the pin 96 does not interfere with the spool 70.
  • a second signal pressure chamber 121 is defined between the axial hole 79 and the pin 96.
  • the second signal pressure chamber 121, the second signal pressure port connecting hole 73, and the second signal pressure port 104 communicate with each other at all times, regardless of the position of the spool 70.
  • a land portion 85 blocks communication between the second signal pressure port 104 and the first signal pressure port 105.
  • the pin outer peripheral step portion 99 of the pin 96 faces the second signal pressure chamber 121, and a site on an inner wall surface of the second signal pressure port connecting hole 73 that opposes the pin outer peripheral step portion 99 of the pin 96 constitutes a second signal pressure receiving surface 73A.
  • the second signal pressure receiving surface 73A has a pressure receiving surface area that corresponds to a sectional area difference between the small diameter pin portion 97 and the large diameter pin portion 98.
  • the spool 70 is moved in the rightward direction of FIG. 2 by the second signal pressure P3 received by the second signal pressure receiving surface 73A, and as a result, the tip end portion of the spool 70 is pushed out of the housing 100.
  • the spool 70 includes a small diameter spool portion 77, a large diameter spool portion 76 that is thicker than the small diameter spool portion 77, and an outer peripheral step portion 78 formed therebetween.
  • the spool housing hole 110 of the housing 100 includes a small diameter hole portion 111 into which the small diameter spool portion 77 is inserted, and a large diameter hole portion 112 into which the large diameter spool portion 76 is inserted.
  • a first signal pressure chamber 120 is defined between the large diameter hole portion 112 of the housing 100 and the spool 70.
  • the first signal pressure chamber 120 and the first signal pressure port 105 communicate with each other at all times, regardless of the position of the spool 70.
  • a land portion 86 blocks communication between the first signal pressure chamber 120 and the back pressure chamber 130.
  • the outer peripheral step portion 78 of the spool 70 faces the first signal pressure chamber 120, and a site corresponding to a sectional area difference between the small diameter spool portion 77 and the large diameter spool portion 76 constitutes a first signal pressure receiving surface 78A.
  • the spool 70 is moved in the leftward direction of FIG. 2 by the horsepower control signal pressure Pi received by the first signal pressure receiving surface 78A.
  • the horsepower control regulator 40 regulates the working oil pressure Pc such that a signal pressure based on the average discharge pressure Pave and the spring force of the horsepower control springs 48, 49 are counterbalanced. Even after the rotation speed of the variable capacity pump 11 is increased, when the average discharge pressure Pave increases, the control pressure Pcg led through the LS regulator 60 is increased by the operation of the horsepower control regulator 40, and as a result, the discharge capacity of the variable capacity pump 11 decreases.
  • a control system of the hydraulic shovel is switched between a high load mode (a normal operation mode) in which the engine 10 is operated at a predetermined rated rotation speed and a low load mode (a fuel saving operation mode) in which the engine 10 is operated at a lower rotation speed than the rated rotation speed.
  • the horsepower control signal pressure Pi is increased in the high load mode and reduced in the low load mode.
  • a mode switch is performed in response to a switch operation or the like performed by a driver, but is not limited thereto, and may be performed automatically when an air conditioner or the like is operated or the vehicle is stopped.
  • the horsepower control signal pressure Pi is reduced such that a force generated by the horsepower control signal pressure Pi received by the first signal pressure receiving surface 78A decreases, and therefore the spool 70 moves in a direction for switching the position of the horsepower control regulator 40 to the position a.
  • the working oil pressure Pc in the control pressure port 101 increases, leading to a reduction in the discharge capacity of the variable capacity pump 11.
  • the working oil pressure P3 supplied to the turning motor from the first fixed capacity pump 12 increases.
  • the second signal pressure P3 received by the second signal pressure receiving surface 73A increases, and therefore the spool 70 moves in a direction for switching the position of the horsepower control regulator 40 to the position a.
  • the working oil pressure Pc in the control pressure port 101 increases, leading to a reduction in the discharge capacity of the variable capacity pump 11.
  • FIG. 3 is a characteristic diagram showing a relationship between the signal pressures Pave, Pi, P3 and the discharge capacity of the variable capacity pump 11.
  • the discharge capacity of the variable capacity pump 11 decreases. Accordingly, the power (horsepower) of the variable capacity pump 11 is regulated so as to remain substantially constant, and therefore an operation can be performed smoothly even when the rotation speed of the engine 10 is varied.
  • the discharge capacity of the variable capacity pump 11 is reduced in comparison with the high load mode by the operation of the horsepower control regulator 40 in response to the horsepower control signal pressure Pi. Accordingly, the power of the variable capacity pump 11 decreases, leading to a reduction in the load exerted on the engine 10 that drives the variable capacity pump 11.
  • the discharge capacity of the variable capacity pump 11 is reduced by the operation of the horsepower control regulator 40 in response to the second signal pressure P3 from the first fixed capacity pump 12. Accordingly, the power of the variable capacity pump 11 decreases further, leading to a further reduction in the load exerted on the engine 10 that drives the variable capacity pump 11.
  • the pump control apparatus 1 is not limited to a construction machine such as a hydraulic shovel, and may also be used as a fluid pressure supply source provided in another machine or facility.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Operation Control Of Excavators (AREA)
  • Reciprocating Pumps (AREA)
EP14773145.9A 2013-03-27 2014-02-24 Pump control device Active EP2878816B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2013066851A JP6075866B2 (ja) 2013-03-27 2013-03-27 ポンプ制御装置
PCT/JP2014/054303 WO2014156415A1 (ja) 2013-03-27 2014-02-24 ポンプ制御装置

Publications (3)

Publication Number Publication Date
EP2878816A1 EP2878816A1 (en) 2015-06-03
EP2878816A4 EP2878816A4 (en) 2016-05-04
EP2878816B1 true EP2878816B1 (en) 2018-04-18

Family

ID=51623412

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14773145.9A Active EP2878816B1 (en) 2013-03-27 2014-02-24 Pump control device

Country Status (6)

Country Link
US (1) US20150139824A1 (zh)
EP (1) EP2878816B1 (zh)
JP (1) JP6075866B2 (zh)
KR (1) KR101675659B1 (zh)
CN (1) CN104302910B (zh)
WO (1) WO2014156415A1 (zh)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20160003237A1 (en) * 2013-03-27 2016-01-07 Kayaba Industry Co., Ltd. Pump discharge flow-rate control device
JP6248144B2 (ja) * 2016-06-08 2017-12-13 Ｋｙｂ株式会社 ポンプ装置
DE102016119310A1 (de) 2016-10-11 2018-04-12 Danfoss Power Solution a.s. Verbessertes Fluidsteuerventil
CN107781126B (zh) * 2017-11-22 2023-12-05 江苏恒立液压科技有限公司 液压泵控制阀
JP7471901B2 (ja) 2020-04-28 2024-04-22 ナブテスコ株式会社 流体圧駆動装置
CN112523728B (zh) * 2021-02-09 2021-04-27 山东鼎点环保科技有限公司 一种套管气回收装置

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE7408167L (zh) * 1973-06-22 1974-12-23 Robert Cecil Clerk
DE2813486C2 (de) * 1977-03-31 1986-06-26 Kabushiki Kaisha Komatsu Seisakusho, Tokio/Tokyo Steuervorrichtung für Hydraulikpumpen
WO1982001048A1 (en) * 1980-09-12 1982-04-01 Ruseff W Multiple pump system with horsepower limiting control
JP3758399B2 (ja) * 1999-01-18 2006-03-22 株式会社豊田自動織機 可変容量型圧縮機における容量制御弁取り付け構造
US7076946B2 (en) * 2004-08-16 2006-07-18 Eaton Corporation Hydraulic kicker control piston
US7484939B2 (en) * 2004-12-17 2009-02-03 Eaton Corporation Variable displacement radial piston pump
JP4869118B2 (ja) * 2007-03-23 2012-02-08 カヤバ工業株式会社 馬力制御レギュレータ、馬力制御装置、及び、ピストンポンプ
JP4936984B2 (ja) * 2007-05-11 2012-05-23 カヤバ工業株式会社 油圧回路
JP5004665B2 (ja) * 2007-05-24 2012-08-22 カヤバ工業株式会社 ピストンポンプの油圧回路
JP4922068B2 (ja) 2007-05-24 2012-04-25 カヤバ工業株式会社 斜板式２連ピストンポンプの油圧回路
JP4976920B2 (ja) * 2007-05-24 2012-07-18 カヤバ工業株式会社 ポンプ吐出量制御装置

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
JP2014190255A (ja) 2014-10-06
EP2878816A4 (en) 2016-05-04
KR20150002840A (ko) 2015-01-07
KR101675659B1 (ko) 2016-11-22
WO2014156415A1 (ja) 2014-10-02
JP6075866B2 (ja) 2017-02-08
EP2878816A1 (en) 2015-06-03
CN104302910B (zh) 2016-05-25
CN104302910A (zh) 2015-01-21
US20150139824A1 (en) 2015-05-21

Similar Documents

Publication Publication Date Title
EP2878816B1 (en) Pump control device
JP6312701B2 (ja) 流体ポンプアセンブリの比例フロー制御
JP2009103304A (ja) 建設機械用油圧制御弁
JP5188444B2 (ja) 作業機の液圧駆動装置
JP2015200412A (ja) 切り替え可能な流体静力学的調整デバイス
JP6111116B2 (ja) ポンプ容積制御装置
JP2016169818A (ja) 油圧駆動システム
US20060198736A1 (en) Pump control system for variable displacement pump
KR101702253B1 (ko) 펌프 토출 유량 제어 장치
EP3470676B1 (en) Pump device
JP4933299B2 (ja) 建設機械の油圧制御装置
JPH1082368A (ja) ローダの油圧装置
JP2005320912A (ja) 可変容量型油圧ポンプ
EP3470677B1 (en) Pump device
JP3974076B2 (ja) 液圧駆動装置
JP2004316839A (ja) 液圧駆動装置
WO2018008209A1 (ja) 斜板式ピストンポンプ
KR102010592B1 (ko) 건설기계의 유압시스템
JP2014177910A (ja) 油圧ポンプの容量制御装置
JPH05280471A (ja) 可変容量型油圧ポンプの容量制御装置

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20141118

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: KYB CORPORATION

RA4 Supplementary search report drawn up and despatched (corrected)

Effective date: 20160404

RIC1 Information provided on ipc code assigned before grant

Ipc: F04B 1/26 20060101AFI20160329BHEP

Ipc: F04B 1/32 20060101ALI20160329BHEP

Ipc: F04B 49/00 20060101ALI20160329BHEP

DAX Request for extension of the european patent (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTG Intention to grant announced

Effective date: 20180103

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

RIN1 Information on inventor provided before grant (corrected)

Inventor name: NAGASHIMA, MIDORI

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 990781

Country of ref document: AT

Kind code of ref document: T

Effective date: 20180515

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602014024146

Country of ref document: DE

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20180418

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180418

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180418

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180418

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180418

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180718

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180418

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180718

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180418

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180418

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180719

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180418

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180418

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180418

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK05

Ref document number: 990781

Country of ref document: AT

Kind code of ref document: T

Effective date: 20180418

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180820

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602014024146

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180418

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180418

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180418

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180418

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180418

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180418

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180418

26N No opposition filed

Effective date: 20190121

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20190318

Year of fee payment: 11

Ref country code: IT

Payment date: 20190228

Year of fee payment: 6

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180418

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180418

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190224

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20190228

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190228

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190228

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190224

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190228

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180418

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190224

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20200224

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200224

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200229

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180418

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180818

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20140224

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200224

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180418

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20240219

Year of fee payment: 11