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WO2002004820A1 - Circuit de verin hydraulique - Google Patents

Circuit de verin hydraulique Download PDF

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Publication number
WO2002004820A1
WO2002004820A1 PCT/JP2001/005828 JP0105828W WO0204820A1 WO 2002004820 A1 WO2002004820 A1 WO 2002004820A1 JP 0105828 W JP0105828 W JP 0105828W WO 0204820 A1 WO0204820 A1 WO 0204820A1
Authority
WO
WIPO (PCT)
Prior art keywords
hydraulic
hydraulic cylinder
pump
pressure
pumps
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
PCT/JP2001/005828
Other languages
English (en)
Japanese (ja)
Inventor
Hideaki Yoshimatsu
Yoshimi Saotome
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.)
Kobelco Construction Machinery Co Ltd
Original Assignee
Kobelco Construction Machinery Co Ltd
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 JP2000207985A external-priority patent/JP2002021807A/ja
Priority claimed from JP2000226655A external-priority patent/JP2002039110A/ja
Application filed by Kobelco Construction Machinery Co Ltd filed Critical Kobelco Construction Machinery Co Ltd
Publication of WO2002004820A1 publication Critical patent/WO2002004820A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
    • F15B7/005—With rotary or crank input
    • F15B7/006—Rotary pump input
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20507—Type of prime mover
    • F15B2211/20515—Electric motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20569—Type of pump capable of working as pump and motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/27—Directional control by means of the pressure source
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6306—Electronic controllers using input signals representing a pressure
    • F15B2211/6313—Electronic controllers using input signals representing a pressure the pressure being a load pressure

Definitions

  • the present invention relates to a hydraulic cylinder circuit for controlling a hydraulic flow rate supplied to a hydraulic cylinder, and more particularly to a hydraulic circuit suitable for a hydraulic circuit for supplying a hydraulic pressure to a hydraulic cylinder by driving a hydraulic pump with an electric motor. It relates to a cylinder circuit.
  • a hydraulically operated press working device described in JP-A-9-1174300 is known. .
  • the hydraulic cylinder of this device has a volume difference between the head side and the rod side (the cross-sectional area of the rod side pressure chamber is larger than that of the head side pressure chamber. This is because the one-sided cylinder 60 is driven by one hydraulic pump 62 driven by the electric motor 61, and the head side when the hydraulic cylinder 60 is extended. An imbalance occurs between the hydraulic fluid flow on the rod side and the hydraulic fluid flow discharged and sucked from the hydraulic pump 62. If the unbalance amount is excessive, return to tank T, and conversely, if insufficient, inhale from tank T.
  • the hydraulic pump 62 Since the area A R of the head-side pressure chamber 60 b in the hydraulic cylinder 60 is smaller than that of the head-side pressure chamber 60 c, the hydraulic pump 62 to the head-side pressure chamber 6 The flow rate of the hydraulic fluid fed to 0 c alone is insufficient, and the insufficient amount is sucked from the tank through the pilot check valve 64. Next, when the processing tool 63 comes into contact with the workpiece 65, the pressure in the head side pressure chamber 60c becomes high due to the processing reaction force. In this state, the hydraulic pump 62 is The rod 60a extends to feed the pressure fluid into the side pressure chamber 60c.
  • 59-39601 states that the combination of two variable displacement pumps 70 and 71 and a charge pump 72 as shown in FIG. Regardless, a drive hydraulic circuit that can drive the cylinder 73 at a speed corresponding to the discharge amount of the hydraulic pump 70 and the sub hydraulic pump 71 is shown.
  • the high-pressure side and the low-pressure side of the sub-pump 71 are used separately, and the hydraulic oil from the charge pump 72 is pushed into the low-pressure side of the sub-hydraulic pump 71. Therefore, in this drive hydraulic circuit, the excess flow rate discharged from the charge pump 72 is relieved from the relief valve 74, resulting in a loss, and the sub-pump 71 is connected to the line 75 When the hydraulic pump 70 discharges oil, the flow amount is relieved from the relief valve 74, resulting in a loss.Furthermore, controlling the flow rate by the hydraulic pump 70 means that the prime mover that drives the pump is Since it is assumed that the motor is used at a constant rotation speed, there is a problem that energy loss is large.
  • the present invention has been made in consideration of the above-described problems in the conventional electric hydraulic drive device, and has a hydraulic pressure having a volume difference between the head side and the mouth side pressure chambers.
  • An object of the present invention is to provide a hydraulic cylinder circuit that can efficiently drive a cylinder while suppressing loss in both the extension direction and the contraction direction.
  • the invention of claim 1 includes first and second hydraulic pumps driven by an electric motor, and the first hydraulic pump is provided between a head-side pressure chamber of a single-sided hydraulic cylinder and a tank.
  • the second hydraulic pump is connected between the pressure pump, the rod-side pressure chamber, and the tank, and the discharge rates of the two hydraulic pumps are Ql and Q2, and the head-side pressure of the hydraulic cylinder is Assuming that the cross-sectional area of the chamber is Ah and the cross-sectional area of the rod-side pressure chamber is Ar, the pressurized liquid is applied to the pressure chambers on both sides so that the discharge amount Q2 becomes substantially the same as the value of Q1X (Ar ZAh).
  • This is a hydraulic cylinder circuit configured to supply and discharge from the pressure chambers on both sides.
  • the relationship of Q2 Q1X (Ar / Ah) from separate hydraulic pumps to both the head side chamber and the rod side pressure chamber of the one-sided rod type hydraulic cylinder, That is, since the hydraulic pressure is supplied and discharged at the flow rate ratio corresponding to the cross-sectional area ratio, the hydraulic cylinder can be operated at the same speed on the extension side and the reduction side, respectively.
  • the circuit configuration can be simplified because the replenishment of the pressurized liquid and the discharge of the excess pressure liquid are not performed. Furthermore, even if the electric motor is rotated according to the driving of the hydraulic pump, there is an advantage that cavitation due to insufficient suction of the hydraulic fluid does not occur.
  • the invention according to claim 4 further comprises at least one pump.
  • the purpose of the present invention can be achieved by controlling the pump displacement as a variable displacement type.
  • both pumps are driven by separate electric motors, it is possible to obtain an appropriate pressure liquid flow rate only by adjusting the pump speed without strictly setting the pump volume. Yes, according to the invention of claim 4 If the pump volume is not specific, a commercially available pump can be used, or another pump can flow.
  • the invention according to claim 5 is characterized in that the first and second hydraulic pumps driven by the electric motor and the hydraulic cylinder to which the hydraulic fluid discharged from the hydraulic pump is supplied because there is a volume difference between the pressure chambers on both sides.
  • the first hydraulic pump is connected to the pressure chambers on both sides of this hydraulic cylinder, one port of the second hydraulic pump is connected to the large-pressure side pressure chamber of the hydraulic cylinder, and the other port is a tank.
  • the pressure supplied from the first hydraulic pump to the large-capacity side for example, to the head side due to the volume difference.
  • Fluid shortage This shortage of the hydraulic fluid amount is determined by using the negative pressure in the rod-side supply / discharge path to suck the hydraulic fluid from the tank, instead of using the tank connected to the low-pressure side of the second hydraulic pump.
  • the hydraulic cylinder circuit forms a closed circuit, flow control can be performed without waste.
  • the first and second hydraulic pumps are constituted by fixed displacement pumps.
  • the rotation direction and the rotation speed of the electric motor it is possible to adjust the flow rate of the hydraulic fluid supplied to and discharged from the hydraulic cylinder.
  • one or both of the hydraulic pumps is constituted by a variable displacement pump.
  • a variable displacement pump By switching the capacity of the pump, it is possible to eliminate the excess and deficiency of the hydraulic fluid generated in the supply / discharge path during the expansion / contraction operation of the hydraulic cylinder.
  • the displacement of the variable displacement pump is controlled so that the excess flow always flows into the tank regardless of the operating direction of the hydraulic cylinder.
  • the return line for returning the surplus flow rate to the tank has a low-pressure pressure control valve so as to apply a back pressure to the return liquid.
  • the invention of claim 11 is one in which the two hydraulic pumps are constituted by tandem pumps, and space can be saved.
  • a hydraulic cylinder circuit according to the fifth aspect, wherein an operating means for operating the hydraulic cylinder, and a supply / discharge passage from the hydraulic pump to the hydraulic cylinder are cut off or communicated, A stop / hold valve for holding the hydraulic cylinder in a stopped state at a shutoff position, and a switching valve provided in a return fluid path connecting the supply / discharge path and the tank and having a shutoff position and a communication position, The direction of the external force acting on the pressure cylinder is detected, and the supply / discharge path on the side that does not carry the external force is communicated via the switching valve to communicate with the tank.
  • This can solve the problem that the cylinder speed fluctuates depending on the direction of the load acting on the hydraulic cylinder, even though the hydraulic cylinder is operated in one direction.
  • the invention according to claim 13 is the two-sided high-pressure pump, wherein the first hydraulic pump is a two-sided high-pressure pump through which hydraulic fluid flows in both directions through each port.
  • This port consists of a one-sided high-pressure pump that communicates with the tank and is always on the low-pressure side.
  • the switching valve is operated to switch at an external pipe pressure different from the self-pressure of the supply / discharge path.
  • FIG. 1 is a hydraulic circuit diagram showing a first embodiment of a hydraulic cylinder circuit according to the present invention.
  • FIG. 2 is a hydraulic circuit diagram showing a second embodiment of the present invention.
  • FIG. 3 is a hydraulic circuit diagram showing a third embodiment of the present invention.
  • FIG. 4 is a hydraulic circuit diagram showing a fourth embodiment of the present invention.
  • FIG. 5 is a hydraulic circuit diagram showing a fifth embodiment of the present invention.
  • FIG. 6 is a hydraulic circuit diagram showing a sixth embodiment of the present invention.
  • FIG. 7 is a circuit configuration diagram of a conventional factory drive unit.
  • FIG. 8 is a circuit diagram of another conventional actuator driving apparatus. BEST MODE FOR CARRYING OUT THE INVENTION
  • reference numeral 1 denotes an electric motor that uses a generator or a commercial power supply (not shown) as a power source.
  • the electric motor 1 causes first and second fixed-capacity hydraulic pumps (hydraulic pumps) 2 and 3 to operate. Driven.
  • the first hydraulic pump 2 is connected between the head side oil chamber (head side pressure chamber) 4a of the one-side rod type hydraulic cylinder (hydraulic cylinder) 4 and the tank T, and the second hydraulic pump 3 is Connected between rod side oil chamber 4b and tank T.
  • the rotation direction and the discharge amount of the two pumps 2 and 3 are controlled by controlling the rotation direction and the rotation speed of the electric motor 1 by a controller (not shown). As a result, the expansion and contraction operation direction and speed of the hydraulic cylinder (hydraulic cylinder) 4 are controlled.
  • the pump volumes Ql and Q2 of the two pumps 2 and 3 are given by the relationship with the cross-sectional areas Ah and Ar of the head-side and rod-side oil chambers 4a and 4b of the hydraulic cylinder 4.
  • Oil is returned to the tank.
  • the extension operation and the contraction operation of the hydraulic cylinder 4 are performed at the same speed if the pump rotation speed (motor rotation speed) is the same.
  • both pumps 2 and 3 are driven by separate electric motors 1A and 1B.
  • FIGS. 2 and 3 the same components as those in FIG. 1 are denoted by the same reference numerals, and description thereof will be omitted.
  • the relationship between the pump volumes Ql and q2 of both pumps 2 and 3 is shown.
  • the second embodiment has an advantage that the pump volume (pump size) can be freely selected.
  • the pump volume cannot always be obtained exactly as set. Even in such a case, an appropriate flow rate can be accurately obtained by adjusting the cylinder inflow and outflow flow rates according to the pump rotation speed as in the second embodiment.
  • FIG. 2 shows a case where a fixed displacement pump is used for both pumps 2 and 3, but a variable displacement pump may be used in order to increase the degree of freedom of flow rate adjustment.
  • variable displacement pumps are used for both pumps 2 and 3 on the premise of the configuration of the first embodiment in which both pumps 2 and 3 are driven by common electric motor 1.
  • the controller and pump regulator (not shown)
  • the pumps 2 and 3 are controlled in capacity so that the following relationship is obtained.
  • both pressures on the head side and the rod side of the hydraulic cylinder 4 are detected by pressure gauges 5 and 6 and input to the controller. May be controlled.
  • only one of the two pumps 2 and 3 may be of a variable displacement type, and the pump volume may be relatively controlled in relation to the discharge amount of the other pump.
  • FIG. 4 shows an example of application to construction machinery.
  • a second hydraulic pump is provided to supply the shortage of hydraulic oil, and the low-pressure side of the pump is used as a tank.
  • the connection improves self-priming.
  • the hydraulic cylinder circuit includes an engine 10 as a drive source, a generator 11 driven by the engine 10, a battery 12 storing electric power generated by the generator 11, An electric motor 14 which is rotated by electric power supplied from the battery 12 via the inverter 13, a first hydraulic pump (hydraulic pump) 15 and a second hydraulic pump ( (Hydraulic pump) 16.
  • the motor 14 can rotate in both forward and reverse directions, and can change the rotation speed.
  • the first hydraulic pump 15 and the second hydraulic pump 16 are each composed of a fixed displacement pump, and the discharge direction of the pressure oil changes according to the rotation direction of the electric motor 14, and the discharge amount changes according to the rotation speed. Things.
  • the first hydraulic pump 15 is a two-sided high-pressure pump in which hydraulic oil flows in both directions through both ports.
  • the second hydraulic pump 16 has one port on the high-pressure side and the other port on the other side. This is a one-sided high-pressure pump that communicates with the tank and is always on the low pressure side.
  • the first pump 15 and the second pump 16 are composed of tandem pumps, and the order is arbitrary. Usually, a large-capacity pump is arranged on the input shaft side. In the present embodiment, two pumps are arranged in line on the output shaft of the motor 14. However, the present invention is not limited to this. 6 may be arranged.
  • the first hydraulic pump 15 and the second hydraulic pump 16 and a hydraulic cylinder (hydraulic cylinder) 17 driven by pressurized oil discharged from these pumps 15 and 16 are connected to a supply / discharge passage 18 , 19 to form a hydraulic cylinder circuit 20.
  • the port H of the first hydraulic pump 15 is the head of the hydraulic cylinder 17
  • the port R is connected to the load side supply / discharge passage 19 and the port R is connected to the rod side supply / discharge passage 18 so that the pressure oil is sucked in from one port and discharged from the other port in accordance with the pump rotation direction. Has become.
  • the port H of the second hydraulic pump 16 is connected to the head side supply / discharge path 19 serving as a pressure chamber having a larger volume, and the port R is connected to the tank T.
  • This port R is always used at low pressure, and is designed to have a large pipe diameter, reduce pressure loss, and enhance self-priming performance.
  • the hydraulic cylinder circuit 20 is provided with a hydraulic pilot type stop holding valve 21, 22 in each of the supply and discharge passages 18, 19 on the rod side (reduction side) and the head side (extension side) of the hydraulic cylinder circuit 20.
  • a hydraulic pilot type stop holding valve 21, 22 in each of the supply and discharge passages 18, 19 on the rod side (reduction side) and the head side (extension side) of the hydraulic cylinder circuit 20.
  • an overload relief valve 23 and low-pressure selection valves 24 and 25 are provided between the supply and discharge passages 18 and 19.
  • the low pressure selection valve 24 as a switching valve connected to the inlet side supply / discharge passage 18 switches between the shut-off position a and the communication position b, and switches to the communication position b. And the rod side supply / discharge passage 18 communicate with the tank T.
  • the low-pressure selection valve 25 connected to the head-side supply / discharge path 19 is configured to switch between the shut-off position c and the communication position d.
  • the drain side supply / discharge passage 19 communicates with the tank T.
  • These low-pressure selection valves 24 and 25 are controlled by a controller 26.
  • heads-side pressure of the hydraulic cylinder circuit 2 0 is applied to the controller 2 6 as P H is detected by the pressure sensor S.
  • mouth head side pressure is applied to the controller 2 6 as P R are detected by the pressure sensor S 2.
  • These pressure sensors d and S 2 are for detecting the direction of the load acting on the hydraulic cylinder 17.
  • F A H XP H — A R XP R
  • the two stop holding valves 21 and 22 are switched between a shut-off position for shutting off the supply and discharge passages 18 and 19 and a communication position opening for opening.
  • the outflow of pressurized oil from 17 (leak in pump 15) is stopped, and hydraulic cylinder 17 is kept stopped.
  • the pilot lines 28a and 28b connected to the pilot ports of the two stop holding valves 21 and 22 are electromagnetically switched stop / hold control valves 29a and 29b and the pilot line 3 It is connected to pilot pumps 31a and 3lb via 0a and 30b. Then, for example, when the stop / hold control valve 29a is switched from the cutoff position e to the communication position f, the pie port pressure is supplied from the pier port pump 31a. Upon receiving the pipe port pressure, the stop holding valve 21 is switched from the shut-off position to the communication position port.
  • the operation of the stop holding valve 22 is the same as the operation of the stop holding valve 21 described above.
  • the stop holding control valves 29 a and 29 b are controlled by the controller 26.
  • the controller 26 is provided with an operation unit (for example, a potentiometer) 27 as operation means.
  • an operation signal (command signal) is given from the operation section 27 to the controller 21.
  • the controller 26 mainly performs the following control.
  • the engine 10 is controlled via an engine controller (not shown) so that the engine 10 normally rotates in an energy-efficient rotation speed region.
  • a command signal is sent from the controller 26 to the electric motor 14 as a drive signal via the members 13 through 13.
  • the first and second hydraulic pumps 15 and 16 are driven by the rotation of the motor 14 in the command direction at the command speed.
  • the command signal is also sent as a pilot signal from the controller 26 to the stop holding control valves 29a and 29b, and the valves 29a and 29b are switched from the cutoff position e to the communication position f.
  • the mouth-side stop holding valve 21 is switched to the communication position opening.
  • the head-side stop / hold valve 22 switches to the communication position port, and the pressure oil flows through the hydraulic cylinder circuit 20, and the hydraulic cylinder 17 expands or contracts.
  • the aim of the hydraulic cylinder circuit according to the fourth embodiment is to determine the capacities of the first hydraulic pump 15 and the second hydraulic pump 16 according to the cylinder head side area A H and the rod side area A R That is.
  • the flow rate should not be excessive or insufficient in the extension operation and the contraction operation of the hydraulic cylinder 17.
  • 1 Hydraulic pump 1 Assuming that the theoretical capacity Q1 of 5 is 30 cmVrev, the second hydraulic pump 1
  • the pressure oil that flows through the supply and exhaust passage 1 8, 1 9 according to the volume difference between the heads side area A H and rod de-side area A R of the hydraulic cylinder 1 7 flow Q H: Q R respectively If set, the hydraulic cylinder 17 can be efficiently driven by suppressing the loss of the circuit.
  • the second hydraulic pump 16 is provided so as to suck the pressurized oil from the tank T connected to the low-pressure side. It is possible to reduce the loss of the cylinder circuit.
  • a low-pressure selection valve 33 of a three-position switching type is used instead of the low-pressure selection valves 24 and 25 described above.
  • the low-pressure selection valve 33 has a neutral position g, a rod-side selection position h, and a head-side selection position i, and switches according to the operation of the operation lever 27a.
  • the low-pressure selection valves 24 and 25 shown in FIG. 4 can be configured by one switching valve, so that the circuit configuration can be simplified.
  • the configuration shown in FIG. 6 improves the efficiency of the hydraulic cylinder circuit.
  • a two-capacity switching hydraulic pump (hereinafter, referred to as a switching hydraulic pump) 34 as a variable displacement type is used in place of the second hydraulic pump 16 described above.
  • Mouth head side flow rate Q R is,
  • V H 21.2 cm / s ec
  • V R 23.9 cm / s ec
  • the second hydraulic pump is a two-capacity switching type switching hydraulic pump 34, and the switching hydraulic pump 34 is switched to a large capacity (25 cmV rev) at the time of extension operation, and at the time of contraction operation. It was configured to switch to small capacity (15 ciV rev).
  • the hydraulic cylinder circuit 20 always has an excess flow rate regardless of the extension and contraction operations of the hydraulic cylinder 17, and the excess flow rate can be returned to the tank T from the low-pressure selection valves 24 and 25.
  • the first hydraulic pump 15 may be a two-capacity switchable pump. Further, as long as the hydraulic pump is capable of switching the capacity, the present invention is not limited to the above two capacity, and a variable capacity hydraulic pump can also be used.
  • the low pressure selection valves 24, 25 are switched using the circuit pressure in the supply / discharge circuits 18, 19, the pilot check is performed during the lowering operation of the hydraulic cylinder 17.
  • the pressure oil in the supply / discharge path decreases by the stroke volume of the low-pressure selection valve, and the hydraulic cylinder 17 may contract with a shock.
  • the low pressure selection valves 24 and 25 are not operated by using the pressure oil of the supply and discharge passages 18 and 19, and the external piping port is not operated. The above-mentioned problem can be solved because of the cut-out method.
  • the hydraulic cylinder of the present invention is constituted by a hydraulic cylinder in the above embodiment, but is not limited to this and can be applied to a hydraulic cylinder.
  • the hydraulic cylinder circuit according to the present invention is useful as any hydraulic cylinder driving device that requires speed control of a molding machine, a machine tool, a press device, and the like. It is suitable for a hydraulic circuit that drives a pump and supplies hydraulic pressure to a hydraulic cylinder.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

L'invention concerne un circuit de vérin hydraulique pouvant actionner un vérin hydraulique de type à tige de manoeuvre à un seul côté en position allongée et en position rétractée à la même vitesse, par l'intermédiaire d'un système hybride commandant une pompe à l'aide d'un moteur. Ce circuit présente également une configuration simplifiée, qui se caractérise en ce qu'un fluide sous pression soit introduit et évacué depuis les deux chambres de pression (4a, 4b) côté charge et côté tige de manoeuvre dudit vérin hydraulique de type à tige de manoeuvre à un seul côté (4). Le fluide est fourni par les première et seconde pompes hydrauliques (2, 3) commandées par le moteur (1) à un débit correspondant au rapport de section des deux chambres de pression latérales (4a, 4b). Le vérin hydraulique peut être actionné en position allongée et en position rétractée à la même vitesse.
PCT/JP2001/005828 2000-07-10 2001-07-05 Circuit de verin hydraulique Ceased WO2002004820A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2000-207985 2000-07-10
JP2000207985A JP2002021807A (ja) 2000-07-10 2000-07-10 電動液圧駆動装置及びアクチュエータ駆動装置
JP2000226655A JP2002039110A (ja) 2000-07-27 2000-07-27 油圧シリンダ回路
JP2000-226655 2000-07-27

Publications (1)

Publication Number Publication Date
WO2002004820A1 true WO2002004820A1 (fr) 2002-01-17

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2001/005828 Ceased WO2002004820A1 (fr) 2000-07-10 2001-07-05 Circuit de verin hydraulique

Country Status (1)

Country Link
WO (1) WO2002004820A1 (fr)

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2004040065A1 (fr) * 2002-10-28 2004-05-13 Bosch Rexroth Ag Dispositif d'amortissement
WO2004067969A1 (fr) * 2003-01-29 2004-08-12 Cnh Baumaschinen Gmbh Systeme hydraulique pour entrainements lineaires commandes par des elements deplaceurs
GB2409241A (en) * 2003-12-17 2005-06-22 Thales Uk Plc Differential actuator with fluid transfer across piston for vehicle simulator
JP2008522117A (ja) * 2004-12-01 2008-06-26 ハルデックス・ハイドローリクス・コーポレーション 油圧駆動システム
DE102008039011A1 (de) * 2008-08-21 2010-02-25 MAE Maschinen- und Apparatebau Götzen GmbH & Co. KG Druckspeicherlose hydraulische Antriebsanordnung sowie Verfahren zum druckspeicherlosen hydraulischen Antreiben eines Verbrauchers
WO2011072502A1 (fr) * 2009-12-18 2011-06-23 沈阳东北电力调节技术有限公司 Actionneur électro-hydraulique intégré
WO2011072503A1 (fr) * 2009-12-18 2011-06-23 沈阳东北电力调节技术有限公司 Servo-actionneur électro-hydraulique intégré
WO2012110259A1 (fr) 2011-02-18 2012-08-23 M A E Maschinen- Und Apparatebau Götzen Gmbh Système d'entraînement hydraulique sans accumulateur de pression pour un consommateur et comprenant un consommateur, en particulier pour des presses, et procédé permettant de faire fonctionner un tel système d'entraînement hydraulique sans accumulateur de pression
DE102011056894B4 (de) * 2011-05-06 2013-09-05 Bucher Hydraulics Gmbh Hydraulischer Linearantrieb
CN104093995A (zh) * 2012-01-31 2014-10-08 日立建机株式会社 液压闭合回路系统
WO2014183941A1 (fr) * 2013-05-13 2014-11-20 Robert Bosch Gmbh Mécanisme d'entraînement à vitesse de rotation variable muni de deux pompes et d'un cylindre différentiel
DE102010020690B4 (de) 2010-05-15 2018-08-23 Robert Bosch Gmbh Hydraulisches Antriebssystem
WO2018177640A1 (fr) * 2017-03-29 2018-10-04 Voith Patent Gmbh Dispositif de régulation d'une machine hydraulique
WO2020035391A1 (fr) * 2018-08-16 2020-02-20 Moog Italiana S.R.L. Système de commande d'axe de pompe numérique

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JP2006504014A (ja) * 2002-10-28 2006-02-02 ボッシュ レックスロート アクチエンゲゼルシャフト 制動装置
WO2004040065A1 (fr) * 2002-10-28 2004-05-13 Bosch Rexroth Ag Dispositif d'amortissement
US7543449B2 (en) 2003-01-29 2009-06-09 Cnh America Llc Hydraulic system for linear drives controlled by a displacer element
WO2004067969A1 (fr) * 2003-01-29 2004-08-12 Cnh Baumaschinen Gmbh Systeme hydraulique pour entrainements lineaires commandes par des elements deplaceurs
GB2409241A (en) * 2003-12-17 2005-06-22 Thales Uk Plc Differential actuator with fluid transfer across piston for vehicle simulator
GB2409241B (en) * 2003-12-17 2007-07-25 Thales Uk Plc Apparatus and methods for actuation
JP2012197944A (ja) * 2004-12-01 2012-10-18 Concentric Rockford Inc 油圧駆動システム
US8196397B2 (en) 2004-12-01 2012-06-12 Concentric Rockford, Inc. Hydraulic drive system
JP2008522117A (ja) * 2004-12-01 2008-06-26 ハルデックス・ハイドローリクス・コーポレーション 油圧駆動システム
US8596055B2 (en) 2004-12-01 2013-12-03 Concentric Rockford Inc. Hydraulic drive system
EP2732959A2 (fr) 2008-08-21 2014-05-21 Mae Maschinen- Und Apparatebau Götzen Gmbh&Co. Kg Agencement d'entraînement hydraulique sans accumulateur de pression pour et avec un consommateur, notamment pour presse hydraulique, et procédé d'entraînement hydraulique sans accumulateur de pression d'un consommateur
DE102008039011B4 (de) * 2008-08-21 2020-01-16 MAE Maschinen- u. Apparatebau Götzen GmbH Druckspeicherlose hydraulische Antriebsanordnung sowie Verfahren zum druckspeicherlosen hydraulischen Antreiben eines Verbrauchers
DE102008039011A1 (de) * 2008-08-21 2010-02-25 MAE Maschinen- und Apparatebau Götzen GmbH & Co. KG Druckspeicherlose hydraulische Antriebsanordnung sowie Verfahren zum druckspeicherlosen hydraulischen Antreiben eines Verbrauchers
WO2011072502A1 (fr) * 2009-12-18 2011-06-23 沈阳东北电力调节技术有限公司 Actionneur électro-hydraulique intégré
WO2011072503A1 (fr) * 2009-12-18 2011-06-23 沈阳东北电力调节技术有限公司 Servo-actionneur électro-hydraulique intégré
DE102010020690B4 (de) 2010-05-15 2018-08-23 Robert Bosch Gmbh Hydraulisches Antriebssystem
WO2012110259A1 (fr) 2011-02-18 2012-08-23 M A E Maschinen- Und Apparatebau Götzen Gmbh Système d'entraînement hydraulique sans accumulateur de pression pour un consommateur et comprenant un consommateur, en particulier pour des presses, et procédé permettant de faire fonctionner un tel système d'entraînement hydraulique sans accumulateur de pression
DE102011056894B4 (de) * 2011-05-06 2013-09-05 Bucher Hydraulics Gmbh Hydraulischer Linearantrieb
CN104093995A (zh) * 2012-01-31 2014-10-08 日立建机株式会社 液压闭合回路系统
CN104093995B (zh) * 2012-01-31 2016-01-27 日立建机株式会社 液压闭合回路系统
WO2014183941A1 (fr) * 2013-05-13 2014-11-20 Robert Bosch Gmbh Mécanisme d'entraînement à vitesse de rotation variable muni de deux pompes et d'un cylindre différentiel
WO2018177640A1 (fr) * 2017-03-29 2018-10-04 Voith Patent Gmbh Dispositif de régulation d'une machine hydraulique
CN110446859A (zh) * 2017-03-29 2019-11-12 福伊特专利有限公司 用于调节液压机器的设备
US10808734B2 (en) 2017-03-29 2020-10-20 Voith Patent Gmbh Apparatus for controlling a hydraulic machine
WO2020035391A1 (fr) * 2018-08-16 2020-02-20 Moog Italiana S.R.L. Système de commande d'axe de pompe numérique

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