WO2002095240A1 - Circuit de commande hydraulique d'un equipement sur un engin de chantier - Google Patents

Circuit de commande hydraulique d'un equipement sur un engin de chantier Download PDF

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Publication number
WO2002095240A1
WO2002095240A1 PCT/JP2002/003410 JP0203410W WO02095240A1 WO 2002095240 A1 WO2002095240 A1 WO 2002095240A1 JP 0203410 W JP0203410 W JP 0203410W WO 02095240 A1 WO02095240 A1 WO 02095240A1
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WO
WIPO (PCT)
Prior art keywords
oil
oil passage
attachment
pump
valve
Prior art date
Application number
PCT/JP2002/003410
Other languages
English (en)
Japanese (ja)
Inventor
Hitoshi Iwasaki
Original Assignee
Shin Caterpillar Mitsubishi 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
Application filed by Shin Caterpillar Mitsubishi Ltd. filed Critical Shin Caterpillar Mitsubishi Ltd.
Publication of WO2002095240A1 publication Critical patent/WO2002095240A1/fr

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Classifications

    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E02F9/2239—Control of flow rate; Load sensing arrangements using two or more pumps with cross-assistance
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2285—Pilot-operated systems
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2292—Systems with two or more pumps
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2296—Systems with a variable displacement pump
    • 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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more 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
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/08—Servomotor systems incorporating electrically operated control means
    • F15B21/082—Servomotor systems incorporating electrically operated control means with different modes
    • 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
    • F15B2211/20546—Type of pump variable capacity
    • F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
    • 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
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3116—Neutral or centre positions the pump port being open in the centre position, e.g. so-called open centre
    • 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
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional control characterised by the type of actuation actuated by fluid pressure
    • 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
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • 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
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41527—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a directional control valve
    • F15B2211/41536—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a directional control valve being connected to multiple ports of an output member
    • 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
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41581—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a return line
    • 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
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/426—Flow control characterised by the type of actuation electrically or electronically
    • 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
    • F15B2211/40—Flow control
    • F15B2211/45—Control of bleed-off flow, e.g. control of bypass flow to the return line

Definitions

  • the present invention belongs to the technical field of hydraulic control circuits for attachment in construction of hydraulic excavators and the like.
  • some hydraulic excavators and the like have various attachments, such as breakers and breaks, that can be attached and detached as work attachments, in addition to the normally used packets.
  • the knitting attachments can be classified into four types as shown in FIG. 9, for example, in terms of hydraulic control.
  • the first class of attachments suffices at the flow rate of the pump.
  • Double-acting type for example, a small breaker
  • the second attachment is a single-acting type (for example, a small breaker, etc.) that suffices for the flow rate of the pump
  • the third class attachment is two pumps.
  • Attachment of the fourth class is a double-acting type requiring a minute ⁇ : (for example, breaking of ⁇ M), and a single-acting type requiring a flow rate of two pumps (for example, a large breaker) Therefore, for each of the first to fourth ⁇ ! Attachments, separate hydraulic pressure will be applied.
  • a hydraulic control circuit for such an arrangement as shown in FIG. 7 is known.
  • reference numeral 10 denotes an attachment
  • reference numerals 11 and 12 denote a first and a second.
  • a main pump, 13 is a pipe pump
  • 14 is an oil tank
  • 16 is a valve control valve for controlling the supply and discharge of pressurized oil to the device 10
  • 30 is an operating device for the device.
  • Pilot valve that outputs pilot pressure to control valve 16 for operation based on the operation of 1; 25, 26 are first and second negative controls Relief valve for control, 24 for control valve for second center bypass arranged upstream of relief valve for second negative control 26, J and K for control pulp for attachment 16 and equipment 10
  • the first and second oil passages for connecting the oil inlet / outlet ports 10a and 10b to the control valve for supplying hydraulic oil from the first main pump 11 to the control valve for attachment
  • the first pump oil passage, L is the second pump oil passage for supplying the pressure oil from the second main pump 12 to the control valve 16 for attachment, and the M is output from the pilot port valve 30.
  • the second pump control oil passage for supplying the pie port pressure to the pie port 24b of the control valve 24 for the second sensor bypass, Q is the first oil passage for the first joint J Is a relief oil passage through which oil flows through the relief valve 39 to the oil tank 14 side.
  • Oil ⁇ evening Dzuchimento oil passage K is a discharge oil passage for supplying the oil tank 1 4 side.
  • 40 is a first switching valve for opening and closing the second pump oil passage L
  • 41 is a second switching valve for opening and closing the second pump control oil passage M
  • 42 is a third switching valve for opening and closing the relief oil passage Q.
  • a switching valve 43 is a fourth switching valve for opening and closing the discharge oil passage P, and the first to fourth switching valves 40 to 43 are manually operated pole valves as shown in FIG. Have been.
  • the pressure oil supplied to the attachment control valve 16 is only the pressure oil of the first main pump 11.
  • the first switching valve 40 opens, the hydraulic oil of both the first and second main pumps 11 and 12 is supplied to the control pulp 16 for attachment.
  • the second switching valve 41 closes the second pump control oil passage M, the flow control of the second main pump 12 is not performed based on the operation of the attachment operating tool 31, By opening the second switching valve 41, the negative control of the second main pump 12 can be performed.
  • the third and fourth switching valves 42 and 43 are closed, a double-acting valve is connected from the attachment control knob 16 via the first and second attachment oil passages K.
  • Pressure oil can be supplied to the attachment in both directions, but by opening the third switching valve 42, the relief of the oil passage on the pressure oil supply side of the single-acting attachment (oil passage J for the first attachment) is activated. By opening the fourth switching valve 43, the back pressure of the single-acting attachment can be reduced.
  • FIG. 7, 17 to 23 are various oils provided in the hydraulic excavator. This is a control valve that controls the supply and discharge of pressure oil to the pressure actuator. Also, in Fig. 7, 1 and 2, 2 and 2 are connected to each other. By the way, in the hydraulic control circuit of the equipment, in order to perform hydraulic control corresponding to each of the above-described first to fourth classification elements, all of the first to fourth switching valves are set to each ⁇ !
  • Fig. 9 in Part 3, in the case of a double-acting attachment (first class) that requires only one pump, the first to fourth switching valves are switched to the closed side.
  • second through which is sufficient for the flow rate of the number of pumps, switch the first and second switching valves to the closed side, and switch the third and fourth switching valves to the open side.
  • the double-acting attachment (third ⁇ ) that requires the flow rate of two pumps is equipped with a third and fourth directional control valve while switching the first and second directional control valves to the open side.
  • the leakage 3 switching valve is configured using a manual poll valve, but a high-performance ball valve with little leakage and small pressure loss is expensive and hinders cost reduction. There was also a problem to be tested.
  • the present invention has been made in view of the above-described circumstances, and has been created for the purpose of solving these problems, and includes a hydraulically actuated actuator, and control of supply and discharge of hydraulic oil to the actuator.
  • Attachment control valve for performing pressure control, a first pump oil passage for supplying pressure oil from the first and second pumps to the attachment control valve, and a first pump oil passage for supplying pressure oil from the first pump to the attachment control valve.
  • the present invention also relates to an attachment which is operated by hydraulic pressure, a control valve for an attachment which controls supply and discharge of pressurized oil to the attachment, and a connection between the control vanolev for the attachment and an oil outlet of a frf self-attachment.
  • An oil pressure control circuit having a first and a second oil passage for an operation, the oil in the oil passage for the first attachment being supplied to the oil pressure control circuit for the attachment via a relief valve. Opening and closing of the relief oil passage and the discharge oil passage to provide a relief oil passage for flowing oil to the tank side and a discharge oil passage for flowing oil from the second alignment oil passage to the tank side. Can be performed based on the switching operation of one switching means. In this way, by switching one switching means, the hydraulic control circuit for supplying the hydraulic oil to the double-acting attachment and supplying the hydraulic oil to the single-acting attachment can be formed. By being able to make the change, the circuit change becomes easy and the occurrence of errors can be suppressed.
  • the present invention provides a hydraulically operated attachment, an alignment control valve for controlling hydraulic oil supply and discharge to the alignment, and a connection between the alignment control valve and an oil outlet of the alignment.
  • a hydraulic pump control circuit comprising: a second pump oil passage for supplying pressure oil from a second pump to the control hydraulic control circuit; The oil in the second pump control oil passage for controlling the flow rate of the oil and the oil in the first treatment oil passage
  • the second pump oil passage and the second pump are controlled based on the switching operation of the first switching means.
  • the opening and closing of both oil passages of the oil passage for use is performed, and the opening and closing of both oil passages of the relief oil passage and the discharge oil passage can be performed based on the switching operation of the second switching means.
  • the hydraulic control circuit can be changed as follows, and the pressure can be supplied to the double-acting element by switching the second switching means: Since the hydraulic control circuit can be changed, the circuit can be easily changed and the occurrence of a mistake can be suppressed.
  • the second pump control oil passage is a pie port oil passage for supplying pie port pressure to the flow control norb of the second pump based on the operation of the attachment operating tool;
  • the second pump oil passage is opened and closed by a second pump oil passage opening / closing valve that is operated by the pilot pressure supplied to the oil pump control oil passage, and the second pump oil passage and the second pump are opened.
  • the switching means for opening and closing both oil passages of the control oil passage can be constituted by a switching valve for opening and closing the second pump control oil passage.
  • the relief oil passage is opened and closed by a relief oil passage opening and closing valve operated by the nozzle port pressure
  • the discharge oil passage is opened and closed by a discharge oil passage opening and closing valve operated by the pilot pressure.
  • the switching means for opening and closing both the relief oil passage and the discharge oil passage can be constituted by a switching valve for switching the opening and closing of the pilot port pressure supply oil passage to the two on-off valves. Furthermore, by configuring the switching means with a manual spool valve that switches based on the switching operation of the operator, the cost can be reduced.
  • FIG. 1 is a perspective view of a hydraulic excavator.
  • FIG. 2 is a hydraulic control circuit diagram for the alignment.
  • Fig. 3 (A) is a plan view of the first and second switching valves, and (B) is a bottom view of the first and second switching valves.
  • Fig. 4 (A) is a front view of the first and second switching valves, and (B) is a side view of the first and second switching valves.
  • FIG. 5 (A) is an enlarged cross-sectional view of XX of FIG. 3 (A), and
  • FIG. 5 (B) is an enlarged cross-sectional view of YY of FIG. 3 (B).
  • FIG. 5 (A) is an enlarged cross-sectional view of XX of FIG. 3 (A)
  • FIG. 5 (B) is an enlarged cross-sectional view of YY of FIG. 3 (B).
  • FIG. 6 is a diagram showing classifications of entertainment and switching positions of the first and second switching valves.
  • FIG. 7 is a hydraulic control circuit diagram for an attachment showing an example.
  • FIGS. 8 (A) and 8 (B) are plan views of the switching valve in the ⁇ * example, and
  • FIG. 9 is a front view in cross section.
  • FIG. 9 is a plan view showing the arrangement of the switching element and the first to fourth switching valves.
  • FIG. 5 is a diagram showing a switching position of the switch.
  • reference numeral 1 denotes a hydraulic excavator
  • the hydraulic excavator 1 includes a lower traveling body 2 of a crawler type, an upper revolving body 3 rotatably supported by the lower traveling body 2, and an upper revolving body 3
  • the boom 4 is supported so as to be able to swing up and down, a stick 5 is supported at the tip of the boom 4 so as to swing back and forth, and a bucket 6 attached to the tip of the stick 5 is provided.
  • various hydraulic actuators such as a left and right traveling motor (not shown), a swing motor (not shown), a boom cylinder 7, a stick cylinder 8, and a bucket cylinder 9 are provided.
  • various attachments 10 that are operated by hydraulic pressure such as breakers and ruptures can be mounted, and the hydraulic control for the hydraulic control 10 can be performed.
  • the present invention has been described.
  • the I3 arrangement 10 is classified into four as shown in FIG. 6, so that different hydraulic control can be performed for each classification.
  • the attachment 10 of the first category is a double-acting type which is sufficient for the flow rate of the main pump, which will be described later, and in which oil flows in both directions, and corresponds to, for example, a small crusher.
  • the second actuator 10 is a single-acting type in which the flow rate of the main pump is sufficient and the oil flows only in one direction, such as a small breaker.
  • the attachment 10 of the third category requires a flow rate of two main pumps and is a double-acting type in which oil flows in both directions.
  • the fourth ⁇ ! The attachment 10 requires a flow rate of two main pumps and is a single-acting type in which pressure oil flows only in one direction. For example, a large breaker or the like is applicable. Now, FIG.
  • FIG. 2 shows a hydraulic control circuit diagram of the attachment 10.
  • the control valve unit 15 includes a control valve 16 for an attachment which controls the supply and discharge of pressure oil to the attachment 10 and a control valve 16 for the hydraulic actuating unit of the above-mentioned type.
  • Fig. 2, 1 and 1, 2 and 2, 3 and 3, 4 and ⁇ ⁇ are connected.
  • A is the first sensor bypass passage
  • B is the second sensor bypass passage
  • the centrifugal bypass oil passage A controls the pressure oil from the first main pump 11 and controls the central lubrication passages 17 a, 17 a, 16, 18, 19, and 20.
  • This is an oil line that flows to the first negative control port, Reno ⁇ Rev 25, via 16a, 18a, 19a, 20a
  • the second oil bypass line B is the second main line.
  • the pressure oil from the pump 12 is passed through the center bypass valve passages 21a, 22a, 23a and 24a formed in the control valves 21 22 23 24. This is an oil passage for the negative control valve 26.
  • the second parallel oil passage D is an oil passage for supplying pressurized oil from the second main pump 12 to the control valves 21, 22, 23, and 24.
  • E is a tank oil passage, and the tank oil passage E is used to supply oil from the control valves 16 to 23 and the first and second negative control valves V 25 and 26. This is an oil passage for flowing into tank 14.
  • the pressure of the first and second center bypass oil passages B supplied to the BB-second negative control valves 25 and 26 is a negative control signal pressure as the first and second negative control lines F and G.
  • the flow rate variable means 27 reduces the pump discharge amount when the negative control signal pressure is high, and increases the pump discharge amount when the negative control signal pressure is low. It is configured to perform the flow control of 11 and 12.
  • the control valve 16 for attachment is a three-position switching valve having first and second pilot ports 16b and 16c, and is connected to both pilot ports 16b and 16c. In the state where the throttle pressure is not input, the hydraulic oil in the first oil bypass oil passage A flows downstream through the oil bypass valve line 16a, while the hydraulic oil is supplied to and discharged from the oil pump 10.
  • the pilot bypass pressure is input to the first pilot port 16b, thereby closing the center bypass valve line 16a and the pressure of the supply oil line H described later. It switches to the first pressure oil supply position X where oil is supplied to the first oil passage J and the oil in the second oil passage K is discharged to the oil passage E.
  • pilot pressure is supplied to port 16c, the center While closing the bypass valve line 16a, supply the pressure oil in the supply oil passage H to the second attachment oil passage K, and discharge the oil in the first attachment oil passage J to the tank oil passage E. It is configured to switch to the second pressure oil supply position Y.
  • the supply oil passage H is an oil passage for supplying the pressure oil of the first parallel oil passage C to the attachment control valve 16 via the valve 28 (the oil passage is the first pump of the present invention).
  • the hydraulic oil of the second main pump 12 is supplied to the second pump oil passage opening / closing valves 35 and 35 described later.
  • the second oil passage L and the second oil passage L for supplying to the control valve 16 via the valve 29 are connected to the control valve 16 for the equipment.
  • the first and second attachment oil passages K are oil passages connected to the attachment 10, but the attachment 10 is a double-acting attachment, that is, the first and third classifications described above.
  • One of the oils of the first arrangement 10 is connected to one oil of the double-acting arrangement 10, an oil passage J for the first arrangement is connected to the outlet 10 a, and the other oil 3 ⁇ 4 ⁇
  • the second oil passage ⁇ is connected to the outlet 1 Ob.
  • the attachment 10 is a single-acting attachment, that is, the second and fourth ⁇ !
  • the oil inlet 10 a of the single-acting oil tank 10 is connected to the oil passage J for the first oil pump, and the oil outlet J is connected to the oil outlet 10 b.
  • the oil passage K for the second anchorage is connected.
  • control valve for the Bito-Nicenta bypass (corresponding to the flow control valve of the second pump of the present invention) 24 is a third-position fi3 ⁇ 4 which has first and second pilot ports 24 b and 24 c.
  • the center bypass valve line 24a is opened to open the second centrifugal bypass oil passage B
  • the pilot pressure is supplied to the first pipeline port 24 to close the valve passage 24 a for the above-mentioned pipeline. It is configured to switch to X.
  • the control valve 21, 22, 23, through which the second bypass oil passage B passes, the first and second bypass valve passages 21 a, 22 a, 23 a are open, and the second
  • the evening bypass control valve 24 is located at the neutral position N where the sensing bypass valve path 24 a is opened, it is guided to the flow rate variable means 27 via the second negative control line G described above.
  • the negative control signal pressure increases, and the second main pump 12 is controlled so that the pump discharge rate decreases.
  • the second control valve for second bypass 24 is located at the closed position X, the negative control signal pressure decreases, and the second main pump 12 increases the pump discharge amount. Is controlled as follows.
  • the control valve 24 for the second sensor bypass is used to control the supply of pressure oil to other hydraulic actuators when the pilot pressure is supplied to the second pilot port 24c.
  • the position is switched to the supply position Y, but this control is omitted.
  • reference numeral 30 designates a pit opening and a rev.
  • the pilot rev 30 is an attachment pedal (corresponding to the attachment operating tool of the present invention, but is not limited to the pedal but may be a lever operated by hand. 3) First, second, and third output ports 30a, 30b, and 30c that output the pilot pressure based on only the operation of 31 .
  • the pedal 31 for the actuator is operated only in the forward direction when the attachment 10 is a single-acting type: ⁇ , and is depressed in both directions when the T is a double-acting type.
  • One output port 30a is connected to the first pilot port 1 6b of the armor foot base lever 16 based on the fact that the operation pedal 31 has been depressed forward.
  • the second output port 3 Ob outputs pilot pressure to the second pilot port 16c of the attachment control valve 16 based on the depression of the attachment pedal 31 rearward.
  • the third output port 30c outputs the pipe pressure to the second pump control oil passage M, which will be described later, regardless of whether the attachment pedal 31 is tipped forward or backward. It is configured as follows.
  • the oil passage M for controlling the pump is connected to the pilot port pressure output from the third output port 30 c of the pilot valve 30 via the first switching valve 33 described later.
  • N is a single-acting pilot oil passage, and the single-acting pilot oil passage N transmits pilot pressure output from the pilot pump 13 through a second switching valve 34 described later.
  • This is an oil passage for supplying to the pilot port 36 a of the relief oil passage on-off valve 36 and the pilot port 37 a of the discharge oil passage on-off valve 37. As shown in FIGS.
  • the first and second switching valves 33, 34 are spool-type, three-port, two-way switching valves that are threaded in one valve body 38.
  • the switching valve 33 includes an input port 33 a connected to the third output port 30 c of the nozzle port valve 30, a tank port 33 b connected to the oil tank 14, and a second It has a first pilot port 24 b of the center bypass control valve 24 and an output port 33 c connected to the pie port 35 a of the second pump oil passage opening / closing valve 35.
  • the first switching valve 33 closes the input port 33a when the operator switches the lever 33d.
  • the closed position X where the valve path from the output port 33 c to the tank port 33 b is to be closed, and the evening port 33 b is closed, and the input port 33 a to the output port 33 c It is configured to switch to the open position Y where the valve path opens.
  • the first switching valve 33 is in the closed position X
  • the first pilot port 24 of the second center bypass control valve 24 and the pilot port 35 of the second pump oil closing valve 35 are provided. Is connected to the oil tank 14, but when the first switching valve 33 is in the open position Y, the third output port 3 of the pierce pulp 30 is operated based on the operation of the attachment pedal 31.
  • the pilot port pressure output from 0c is applied to the first pilot port 24b of the control valve 24, and the pilot port 35 of the second pump oil passage open / close valve 35.
  • the second switching valve 34 includes a pump port 34 a connected to the W lot pump 13, a tank port 34 b connected to the oil tank 14, and a relief oil passage opening / closing valve 36. It has a pilot port 36a and an output port 34c connected to the pilot port 37a of the discharge oil passage opening / closing valve 37.
  • the second pump oil passage opening / closing valve 35 is arranged in the second pump oil passage L from the second main pump 12 to the attachment control valve 16 as described above.
  • the on-off valve 35 is a two-way reversing valve having a pilot port 35a, and closes the second pump oil line L when the pilot port pressure is not input to the pilot port 35a. It is located at position X, but there is no pipe pressure at W port 35 a. It is configured to be switched to an open position Y for opening the second pump oil passage L when input. And, when the second pump oil passage opening / closing valve 35 is located at the closed position X, the pressure oil from the second main pump 12 is supplied to the!
  • the supply oil is not supplied to the passage H, and only the pressure oil from the first main pump 11 is supplied to the supply oil passage H via the second parallel oil passage C. ing.
  • the second pump oil passage opening / closing valve 35 is at the open position Y, the pressure oil from the second main pump 12 is supplied via the second pump oil passage L!
  • the supply oil is supplied to the free passage H, so that the pressure oil of the first and second main pumps 11 and 12 is supplied to the supply oil passage H.
  • P is a discharge oil passage that branches off from the oil passage K for the tirl second arrangement and reaches the oil tank 14, and a leak discharge oil passage opening / closing valve 37 is arranged in the discharge oil passage P. It is established.
  • This discharge oil passage opening / closing valve 37 is a pilot operated M: valve, and when the pilot pressure is not input to the pilot port 37a, the oil from the second attachment oil passage K to the oil tank 14 is supplied. The flow is blocked, but the flow in the reverse direction is allowed, but it is in a one-way state. However, when the pilot pressure is input to the outlet port 37a, the oil passage for the second alignment is used. It is configured to be in a bidirectional state that allows the flow of oil from K to the oil tank 14 and the flow in the opposite direction.
  • the exhaust oil passage opening / closing valve 37 is equipped with a single-acting attachment 10 as will be described later: it is excellent in the back pressure of ⁇ , but instead of the oil passage opening / closing valve 37, An on-off valve similar to the second pump oil passage on-off valve 35 described above and a relief oil passage on-off valve 36 described later can also be used.
  • Q is a relief oil passage, and the relief oil passage Q branches off from the knitting first attachment oil passage J and merges into the second equipment oil passage K, and the second oil passage K It is formed so as to reach the oil tank 14 from the oil passage K via the self-discharging oil passage P. In this relief oil passage Q, the pressure of the first attachment oil passage K is set in advance.
  • the set pressure is set to limit the maximum BE force acting on a single-acting attachment, for example, a breaker
  • the oil in the oil passage J for the first attachment is discharged.
  • a relief valve 39 for flowing into the oil tank 14 and a relief oil passage opening / closing valve 36 are provided.
  • the tulB relief oil passage opening / closing valve 36 is a two-way reversing valve provided with a pilot port 36a.
  • the pilot port pressure is not input to the pilot port 36a, the relief valve is opened. Although it is located at the closed position X where the oil passage Q is closed, it is configured to switch to the open position Y where the relief oil passage Q is opened by inputting the pipe outlet pressure to the outlet port 36a. Have been.
  • the first and second switching valves 33, 34 are of a manual type that are switched by an operator's operation, as described above.
  • the hydraulic control for the attachment 10 can be changed based on the switching operation of 34. In the following description, it is assumed that the attachment 10 is operated independently and no other hydraulic actuating-evening operation is performed.
  • the first switching valve 33 is located at the closed position X, as described above, the first pilot port 24 b of the second control bypass pulp 24 b and the second pump oil
  • the pilot port 35 a of the closed valve 35 is in communication with the oil tank 14, and the control valve 24 for the second sensor bypass is located at the neutral position N, and the second pump oil passage
  • the on-off valve 35 is located in the closed position X.
  • the second control valve 24 is switched to the closed position X, and the second pump oil passage opening / closing valve 35 is switched to the open position Y.
  • the first and second main pumps 11 and 12 are connected to the supply oil passage H for supplying pressure oil to the attachment control valve 16.
  • the second main pump 12 is controlled so as to increase the pump discharge amount while the pressure oil from 12 is supplied.
  • the pilot port 36a of the relief oil passage opening / closing valve 36 and the piping of the discharge oil passage opening / closing valve 37 as described above.
  • the outlet port 37 a is in communication with the oil tank 14, so that the relief oil passage opening / closing valve 36 is located at the closed position X, and the discharge oil passage closing valve 37 is in a one-way state. Accordingly, oil discharge from the first and second alignment oil passages K to the oil tank 14 via the relief oil passage 0 and the discharge oil passage P is prevented.
  • the oil discharged from b or 10a passes through the second or first attachment oil passage, J, to the attachment control valve 16 and then from the attachment control valve 16 to the tank.
  • the oil is discharged to oil tank 14 via oil passage E.
  • the pilot pressure from the pilot pump 13 causes the pilot port 36 a of the relief oil passage opening / closing valve 36 and the pilot port 36 a and The oil is supplied to the pilot port 37 a of the discharge oil passage opening / closing valve 37, whereby the relief oil passage closing valve 36 is located at the open position Y, and the discharge oil passage opening / closing valve 37 is in a two-way state.
  • the pressure of the hydraulic oil in the oil passage J is set to the relief valve 39.
  • the pressurized oil is discharged to the oil tank 14 via the relief oil passage, the second attachment oil passage, and the discharge oil passage P, and the maximum pressure supplied to the attachment 10 is reduced.
  • the pressure can be limited to the set pressure of the relief valve 39.
  • the second switching valve 34 in the closed position X, only the pressurized oil from the first main pump 11 is supplied to the attachment 10, and the pressurized oil is supplied in both directions.
  • a hydraulic control circuit for the expression unit is formed.
  • the attachment 10 is achieved by positioning the first switching valve 33 at the closed position X and the second switching valve 34 at the open position Y.
  • a hydraulic control circuit for a single-acting arrangement capable of supplying only the pressure oil from the first main pump 11 and operating the relief and reducing the back pressure is formed. You.
  • the first switching valve 33 is located at the open position Y and the second switching valve 34 is located at the closed position X, so that A hydraulic control circuit for a double-acting attachment that supplies hydraulic oil from the first and second main pumps 11 and 12 and supplies hydraulic oil in both directions is formed.
  • the attachment 10 is made by positioning the first switching valve 33 at the open position Y and the second switching valve 34 at the open position Y.
  • a single-acting gear pump that can supply hydraulic oil from the first and second main pumps 11 and 12 and can operate the relief and reduce the back pressure Hydraulic control circuit for the vehicle is formed.
  • the change of the hydraulic control circuit corresponding to the instruments 10 of the four categories I & I can be performed by switching the first and second two manual switching valves 33, 34.
  • the circuit can be easily changed when the attachment 10 is replaced, and the occurrence of a mistake during the switching operation can be suppressed.
  • the first and second switching valves 33, 34 are As described above, since it is a spool type, there is an advantage that cost can be reduced as compared with the ball valve used. Note that the present invention is not limited to the above-described embodiment of course, and in the above-described embodiment, the first and second switching valves 33 and 34 are of a manual type.
  • the switching valves 33, 34 may be configured by, for example, electromagnetic valves that are switched based on the operation of a selector switch disposed in a driver's seat.
  • the flow rate of the first pump alone is sufficient, for example, during the combined operation of the hydraulic actuator and other attachments supplied with pressure oil from the first pump. If not, it is a matter of course that the second pump can be configured to supply pressure oil to the attachment.
  • the present invention relates to a case in which a hydraulic control circuit is changed to accommodate various types of attachments with different hydraulic controls, such as attachments with different required flow rates and single-acting and double-acting attachments, when mounting the attachment. Widely applicable.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Operation Control Of Excavators (AREA)

Abstract

L'invention concerne un circuit de commande hydraulique qui peut être facilement modifié par remplacement d'un équipement, sur un engin de chantier. Ce circuit de commande hydraulique est conçu de telle sorte qu'un deuxième circuit d'huile L, amenant de l'huile comprimée d'une deuxième pompe principale (12) à une vanne de commande (16) pour l'équipement, et un deuxième circuit d'huile M, servant à commander le débit du flux de la deuxième pompe principale, s'ouvrent/se ferment par commutation d'un premier robinet de changement de régime (33). Selon l'invention, un circuit d'huile de décharge Q, pour transporter l'huile d'un premier circuit d'huile d'équipement J vers le côté réservoir (14), ainsi qu'un circuit d'huile de décharge P, pour transporter l'huile d'un deuxième circuit d'huile d'équipement K vers le côté réservoir, s'ouvrent/se ferment par commutation d'un deuxième robinet de changement de régime (34).
PCT/JP2002/003410 2001-05-18 2002-04-04 Circuit de commande hydraulique d'un equipement sur un engin de chantier WO2002095240A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2001149654A JP2002339908A (ja) 2001-05-18 2001-05-18 建設機械におけるアタッチメント用油圧制御回路
JP2001-149654 2001-05-18

Publications (1)

Publication Number Publication Date
WO2002095240A1 true WO2002095240A1 (fr) 2002-11-28

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PCT/JP2002/003410 WO2002095240A1 (fr) 2001-05-18 2002-04-04 Circuit de commande hydraulique d'un equipement sur un engin de chantier

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WO (1) WO2002095240A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014056592A1 (fr) * 2012-10-10 2014-04-17 Robert Bosch Gmbh Bloc de soupapes à centre ouvert pourvu de deux raccordements de pompe et de tiroirs auxiliaires associés sur les tiroirs principaux
CN107882791A (zh) * 2017-11-06 2018-04-06 钟爱生 多缸压力机液压控制系统及其控制方法
CN114321107A (zh) * 2021-11-12 2022-04-12 武汉船用机械有限责任公司 液压控制驱动系统
WO2022223151A1 (fr) * 2021-04-22 2022-10-27 Caterpillar Sarl Système de commande hydraulique dans des machines de travail

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100605012B1 (ko) 2004-12-29 2006-07-28 두산인프라코어 주식회사 스키드 스티어로더의 어태치먼트 작동용 유압라인의잔류압력 제거장치
JP4873945B2 (ja) * 2005-12-15 2012-02-08 日立建機株式会社 油圧作業機械の流量制御装置
JP5067290B2 (ja) * 2008-07-15 2012-11-07 コベルコ建機株式会社 作業機械
JP2011047211A (ja) * 2009-08-27 2011-03-10 Hitachi Constr Mach Co Ltd 建設機械のアタッチメント駆動装置
KR20210143749A (ko) * 2019-03-30 2021-11-29 스미토모 겐키 가부시키가이샤 쇼벨, 정보처리장치

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS56164205A (en) * 1980-05-19 1981-12-17 Hitachi Constr Mach Co Ltd Hydraulic pressure circuit for hydraulic-pressure-operated apparatus
JPS61126388A (ja) * 1984-11-21 1986-06-13 Yunitsuku:Kk 油圧式クレーンの速度制御方法
JPH0449196A (ja) * 1990-06-15 1992-02-18 Toshiba Mach Co Ltd クレーン用油圧回路
JPH0971963A (ja) * 1995-09-04 1997-03-18 Shin Caterpillar Mitsubishi Ltd アームの掘削力可変装置

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS56164205A (en) * 1980-05-19 1981-12-17 Hitachi Constr Mach Co Ltd Hydraulic pressure circuit for hydraulic-pressure-operated apparatus
JPS61126388A (ja) * 1984-11-21 1986-06-13 Yunitsuku:Kk 油圧式クレーンの速度制御方法
JPH0449196A (ja) * 1990-06-15 1992-02-18 Toshiba Mach Co Ltd クレーン用油圧回路
JPH0971963A (ja) * 1995-09-04 1997-03-18 Shin Caterpillar Mitsubishi Ltd アームの掘削力可変装置

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014056592A1 (fr) * 2012-10-10 2014-04-17 Robert Bosch Gmbh Bloc de soupapes à centre ouvert pourvu de deux raccordements de pompe et de tiroirs auxiliaires associés sur les tiroirs principaux
CN107882791A (zh) * 2017-11-06 2018-04-06 钟爱生 多缸压力机液压控制系统及其控制方法
CN107882791B (zh) * 2017-11-06 2019-05-28 钟爱生 多缸压力机液压控制系统及其控制方法
WO2022223151A1 (fr) * 2021-04-22 2022-10-27 Caterpillar Sarl Système de commande hydraulique dans des machines de travail
CN114321107A (zh) * 2021-11-12 2022-04-12 武汉船用机械有限责任公司 液压控制驱动系统
CN114321107B (zh) * 2021-11-12 2023-08-18 武汉船用机械有限责任公司 液压控制驱动系统

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