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WO2025013962A1 - Engin de chantier - Google Patents

Engin de chantier Download PDF

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Publication number
WO2025013962A1
WO2025013962A1 PCT/KR2023/009756 KR2023009756W WO2025013962A1 WO 2025013962 A1 WO2025013962 A1 WO 2025013962A1 KR 2023009756 W KR2023009756 W KR 2023009756W WO 2025013962 A1 WO2025013962 A1 WO 2025013962A1
Authority
WO
WIPO (PCT)
Prior art keywords
control valve
value
valve
boom
boom actuator
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.)
Pending
Application number
PCT/KR2023/009756
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English (en)
Korean (ko)
Inventor
고진우
강상석
김태훈
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.)
Volvo Construction Equipment AB
Original Assignee
Volvo Construction Equipment AB
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 Volvo Construction Equipment AB filed Critical Volvo Construction Equipment AB
Priority to PCT/KR2023/009756 priority Critical patent/WO2025013962A1/fr
Publication of WO2025013962A1 publication Critical patent/WO2025013962A1/fr
Pending legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F3/00—Dredgers; Soil-shifting machines
    • E02F3/04—Dredgers; Soil-shifting machines mechanically-driven
    • E02F3/28—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets
    • E02F3/34—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets with bucket-arms, i.e. a pair of arms, e.g. manufacturing processes, form, geometry, material of bucket-arms directly pivoted on the frames of tractors or self-propelled machines
    • 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
    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors

Definitions

  • Various work machines are known that pressurize a fluid and perform work using the power obtained from the pressurized fluid.
  • Construction machines such as excavators and shovels are examples.
  • Some work machines have a work device including a boom, and the operator can perform work by raising and lowering the boom.
  • a working machine comprising: a boom actuator having a bottom chamber and a piston rod side chamber; an operating fluid pump supplying a pressurized operating fluid to the boom actuator; a tank receiving an exhaust operating fluid discharged from the boom actuator; a first control valve and a second control valve installed in parallel between the operating fluid pump and the tank and the boom actuator, respectively controlling a flow rate of the exhaust operating fluid discharged from the boom actuator; a first operator input device receiving a first value indicating a required opening degree of the valve, and a second operator input device receiving a second value indicating an adjustment value for adjusting the required opening degree, wherein the first control valve is opened and closed so that the opening degree depends on the first value, and the second control valve is opened and closed so that the opening degree depends on the first value and the second value.
  • the available range of the opening degree of the second control valve can be expandable during a boom down operation, and accordingly, the available range of the boom down speed can be expanded, thereby providing an advantage of being able to respond to various boom down speed demands of an operator.
  • the anti-drop valve is additionally provided between the boom actuator and the first control valve and the second control valve, and when the discharge working fluid is discharged from the bottom chamber during a boom down operation, the anti-drop valve can be opened and closed such that the opening degree depends on the first value and the second value.
  • the available range of opening degrees of the anti-drop valve can be adjusted to match the available range of opening degrees of the control valves, thereby providing an advantage in that the work machine can satisfy the specified boom down speed limitation condition even in an emergency situation, for example, in which a hose between the boom actuator and the control valves is broken.
  • the anti-drop valve may be formed integrally with or combined with the boom actuator.
  • the greater the opening degree required by the first value the greater the opening degree of the first control valve, the second control valve and the anti-drop valve may be opened, and the greater the opening degree required by the second value, the greater the opening degree of the second control valve and the anti-drop valve may be opened.
  • the degree of opening of the anti-drop valve is given such that V2 ⁇ a*V1, wherein V1 is an operating speed of the boom actuator when the flow path between the anti-drop valve and the first control valve and the second control valve is not damaged, V2 is an operating speed of the boom actuator when the flow path is damaged, and a > 1.
  • a may be 2.
  • a third proportional pressure reducing valve may additionally be included that generates a third pilot pressure dependent on the first value and the second value and provides the third pilot pressure to the anti-drop valve.
  • the method may further include a first proportional pressure reducing valve generating a first pilot pressure dependent on the first value and providing the first pilot pressure to the first control valve, a second proportional pressure reducing valve generating a second pilot pressure dependent on the first value and the second value and providing the second pilot pressure to the second control valve, a third proportional pressure reducing valve generating a third pilot pressure dependent on the first value and the second value and providing the third pilot pressure to the anti-drop valve, and a control unit receiving a first signal corresponding to the first value and a second signal corresponding to the second value from the first operator input device and the second operator device, respectively, and controlling the first proportional pressure reducing valve to generate the first pilot pressure, controlling the second proportional pressure reducing valve to generate the second pilot pressure, and controlling the third proportional pressure reducing valve to generate the third pilot pressure.
  • a first proportional pressure reducing valve generating a first pilot pressure dependent on the first value and providing the first pilot pressure to the first control valve
  • a second proportional pressure reducing valve generating a second
  • the system may further include a first proportional pressure reducing valve that generates a first pilot pressure dependent on the first value and provides the first pilot pressure to the first control valve, and a second proportional pressure reducing valve that generates a second pilot pressure dependent on the first value and the second value and provides the second pilot pressure to the second control valve.
  • the adjustment value may be given as a ratio of 0 to 1.
  • the first control valve has a neutral position, a first non-neutral position, and a second non-neutral position, and when in the second non-neutral position, the first control valve can send the exhaust working fluid discharged from the bottom chamber of the boom actuator to the tank for discharge and also to the piston rod side chamber for regeneration
  • the second control valve has a neutral position, a first non-neutral position, and a second non-neutral position, and when in the second non-neutral position, the second control valve can send the exhaust working fluid discharged from the bottom chamber of the boom actuator to the tank for discharge and also to the piston rod side chamber for regeneration.
  • a first flow path may be formed between the bottom chamber of the boom actuator and the first control valve and the second control valve, in which working fluids going to and/or from the first control valve and the second control valve join and flow together
  • a second flow path may be formed between the piston rod side chamber of the boom actuator and the first control valve and the second control valve, in which working fluids going to and/or from the first control valve and the second control valve join and flow together.
  • the boom actuator comprises two boom actuators
  • the working fluids going to and/or coming from the bottom chambers can join and flow together in the first flow path
  • the working fluids going to and/or coming from the piston rod side chambers can join and flow together in the second flow path.
  • a method for controlling a working machine includes a boom actuator having a bottom chamber and a piston rod side chamber; an operating fluid pump supplying a pressurized operating fluid to the boom actuator; a tank receiving an exhaust operating fluid discharged from the boom actuator; a first control valve and a second control valve installed in parallel between the operating fluid pump and the tank and the boom actuator, respectively controlling a flow rate of the exhaust operating fluid discharged from the boom actuator; a first operator input device receiving a first value representing a required opening degree of the valve, and a second operator input device receiving a second value representing an adjustment value for adjusting the required opening degree, wherein the method controls the opening degree of the first control valve to be dependent on the first value, and controls the opening degree of the second control valve to be dependent on the first value and the second value.
  • FIG. 2 is a drawing showing a hydraulic circuit of a working machine according to an example of the present disclosure.
  • Figure 4 is a drawing showing changes in the opening areas of the first control valve and the second control valve according to changes in the displacement of the first operator input device.
  • Figure 6 is a drawing showing changes in the opening areas of the first control valve, the second control valve, and the anti-drop valve according to changes in the pilot pressure of the first operator input device.
  • the work machine may include a boom actuator, an operating fluid pump and tank (110), a control valve, a first operator input device (181), and a second operator input device (182).
  • the control valve may include at least a first control valve (141) and a second control valve (142).
  • the work machine may include an anti-drop valve (150).
  • the work machine may include a first proportional pressure reducing valve (191) that operates the first control valve (141), a second proportional pressure reducing valve (192) that operates the second control valve (142), and a third proportional pressure reducing valve (193) that operates the anti-drop valve (150).
  • the work machine may include a control unit (170).
  • the working fluid pumps may be provided in multiple numbers, and FIG.
  • the working fluids going to/from the bottom chambers (313b) can join and flow together in the first flow path (161), and between the piston rod side chambers (313a) of the two boom actuators and the first control valve (141) and the second control valve (142), the working fluids going to/from the piston rod side chambers (313a) can join and flow together in the second flow path (162).
  • first control valve (141) and the second control valve (142) can control the flow rates of the pressurized working fluid supplied to the boom actuator and the discharged working fluid discharged from the boom actuator, respectively.
  • the flow rates of the working fluid supplied to the bottom chamber (313b) and the flow rates of the working fluid discharged from the piston rod side chamber (313a) are controlled according to the size (displacement) of the stroke of the spool of the valve from the neutral position to the first non-neutral position, and thus the speed at which the boom is raised is controlled.
  • the flow rates of the working fluid supplied to the piston rod side chamber (313a) and the flow rates of the working fluid discharged from the bottom chamber (313b) are controlled according to the size (displacement) of the stroke of the spool of the valve from the neutral position to the second non-neutral position, and thus the speed at which the boom is lowered is controlled.
  • the second operator input device (182) can receive a second value from the operator, which represents an adjustment value for adjusting the required opening degree.
  • the second operator input device (182) can be provided in the form of a touch screen, for example, as shown in FIG. 3, but the present disclosure is not limited thereto and can be provided in various other forms.
  • the adjustment value can be given as a ratio of 0 to 1, for example, as a percentage, as shown in FIG. 3.
  • the first control valve (141) can be opened and closed so that the degree of opening (e.g., the opening area) depends on the first value.
  • the second control valve (142) can be opened and closed so that the degree of opening depends on the first value and the second value.
  • the anti-drop valve (150) can be opened and closed so that the opening degree depends on the first value and the second value.
  • the first control valve (141), the second control valve (142), and the anti-drop valve (150) may be controlled to open more widely as the first value input through the first operator input device (181) requires a greater opening degree.
  • the second control valve (142) and the anti-drop valve (150) may be controlled to open more widely as the second value input through the second operator input device (182) requires a greater opening degree.
  • the opening degree of the anti-drop valve (150) can be controlled so that V2 ⁇ a*V1.
  • V1 may be an operating speed of the boom actuator when the flow path between the anti-drop valve (150) and the first control valve (141) and the second control valve (142) is not damaged
  • V2 may be an operating speed of the boom actuator when the flow path is damaged.
  • the speed may be an average value of speeds measured for 2 seconds or more.
  • the anti-drop valve (150) may limit the flow rate discharged from the bottom chamber (313b) so that the boom down speed at that time does not become a times or more than the boom down speed when the flow path between the anti-drop valve (150) and the control valves is in a normal state when it is not damaged.
  • a is an integer greater than 1, for example, a can be 2.
  • the control unit (170) receives signals corresponding to the first value and the second value from the first operator input device (181) and the second operator input device (182), determines the opening degree of the first control valve (141), the second control valve (142), and the anti-drop valve (150), and controls the size of the electric signal value supplied to each proportional control pressure reducing valve to open and close each valve to the determined opening degree, and accordingly, the pressure of the pilot fluid supplied to the first control valve (141), the second control valve (142), and the anti-drop valve (150) from the first proportional control pressure reducing valve (191), the second proportional control pressure reducing valve (192), and the third proportional control pressure reducing valve (193) is controlled, and accordingly, the size of the stroke of the spools of the first control valve (141), the second control valve (142), and the anti-drop valve (150) can be controlled.
  • the control unit (170) does not provide an electric signal to the first proportional control pressure reducing valve (191), the second proportional control pressure reducing valve (192), and the third proportional control pressure reducing valve (193). Therefore, the first proportional control pressure reducing valve (191), the second proportional control pressure reducing valve (192), and the third proportional control pressure reducing valve (193) are in a neutral position by the force of the spring, and the pilot fluid is not supplied to the spools of the first control valve (141), the second control valve (142), and the anti-drop valve (150).
  • the first control valve (141) and the second control valve (142) are in a neutral position, the anti-drop valve (150) is in a closed position, and the pressurized operating fluid supplied from the first operating fluid pump (131) and the second operating fluid pump (132) passes through the first control valve (141) and the second control valve (142) through the central bypass passage.
  • the anti-drop valve (150) is in a closed position by the force of the spring, thereby performing the function of preventing the boom from falling due to its own weight.
  • the anti-drop valve (150) may include a spool (151) and a poppet (152).
  • the control unit (170) When a boom-up operation request is input to the first operator input device (181), the control unit (170) provides an electric signal to the fourth proportional control pressure reducing valve (194) and the fifth proportional control pressure reducing valve (195). Accordingly, the fourth proportional control pressure reducing valve (194) and the fifth proportional control pressure reducing valve (195) move to a non-neutral position against the force of the spring, and the pilot fluid is supplied to the first control valve (141) and the second control valve (142). As a result, the first control valve (141) and the second control valve (142) move to the first non-neutral position.
  • the working fluid supplied from the first working fluid pump (131) is supplied to the bottom chamber (313b) of the boom actuator through the check valve of the first control valve (141) and the anti-drop valve (150), and the working fluid supplied from the second working fluid pump (132) is supplied to the bottom chamber (313b) of the boom actuator through the check valve of the second control valve (142) and the anti-drop valve (150).
  • the working fluid discharged from the piston rod side chamber (313a) of the boom actuator returns to the tank (110) through the first control valve (141).
  • the first control valve (141) and the second control valve (142) can be opened and closed so that the opening degree depends on the first value.
  • the combined opening area of the first control valve (141) and the second control valve (142) can be designed to be the same as the opening area of the single control valve.
  • the control unit (170) When a boom down operation request is input to the first operator input device (181), the control unit (170) provides an electric signal to the first proportional control pressure reducing valve (191), the second proportional control pressure reducing valve (192), and the third proportional control pressure reducing valve (193). Accordingly, the first proportional control pressure reducing valve (191), the second proportional control pressure reducing valve (192), and the third proportional control pressure reducing valve (193) move to a non-neutral position against the force of the spring, and the pilot fluid is supplied to the first control valve (141), the second control valve (142), and the anti-drop valve (150).
  • the first control valve (141) and the second control valve (142) move to the second non-neutral position, and the anti-drop valve (150) moves to an open position against the force of the spring to allow the passage of the operating fluid.
  • the boom down is performed by its own weight alone (the hydraulic circuit structure within the first control valve (141) that causes the boom down by supplying the working fluid supplied from the working fluid pump to the piston rod side chamber (313a) is not illustrated)
  • the working fluid discharged from the bottom chamber (313b) is sent to the first control valve (141) and the second control valve (142) via the anti-drop valve (150).
  • the first control valve (141) and the second control valve (142) return the working fluid discharged from the bottom chamber (313b) to the tank (110) and simultaneously send it to the piston rod side chamber (313a) to perform regeneration.
  • the first control valve (141) is opened and closed so that the opening degree depends on the first value
  • the second control valve (142) is opened and closed so that the opening degree (the opening degree of the opening through which the combined flow rate of the working fluid passes before being divided into the working fluid returned to the tank (110) and the working fluid regenerated to the piston rod side chamber (313a)) depends on the first value and the second value
  • the anti-drop valve (150) is opened and closed so that the opening degree depends on the first value and the second value.
  • the spool (151) of the anti-drop valve (150) When the pilot pressure is applied to the spool (151) of the anti-drop valve (150), the spool (151) opens, and the working fluid of the bottom chamber (313b) of the boom actuator sequentially passes through the opened poppet (152) and the opened spool (151) to be discharged.
  • Figure 4 is a drawing showing changes in the opening areas of the first control valve (141) and the second control valve (142) according to changes in the displacement of the first operator input device (181).
  • the horizontal axis of FIG. 4 represents the displacement of the first operator input device (181)
  • the vertical axis represents the open area of the valves.
  • the open area (b) of the first control valve (141) may be designed to be smaller than the open area (a) of a single control valve of a conventional work machine
  • the open area (c) of the second control valve (142) may be designed to be smaller than the open area (b) of the first control valve (141) when the adjustment value is set to 100%
  • (d) shows the open area of the second control valve (142) when the adjustment value is set to 50%. That is, for the displacement of the same first operator input device (181), the opening degree of the single control valve among the first control valve (141) and the second control valve (142) can be designed to be the largest, and the second control valve (142) to be the smallest.
  • Figure 5 is a drawing showing the change in the opening area according to the change in the stroke of the second control valve (142).
  • the horizontal axis of FIG. 5 represents the size of the stroke of the second control valve (142), and the vertical axis represents the open area of the second control valve (142). As illustrated, according to some examples, the open area of the second control valve (142) may non-linearly increase as its stroke increases.
  • point a) in the drawing represents the size of the stroke of the second control valve (142) when the adjustment value is set to 100%
  • point b) represents the size of the stroke of the second control valve (142) when the adjustment value is set to 50%
  • point c) represents the size of the stroke of the second control valve (142) when the adjustment value is set to 0%.
  • Figure 6 is a drawing showing changes in the opening areas of the first control valve (141), the second control valve (142), and the anti-drop valve (150) according to changes in the pilot pressure of the first operator input device (181).
  • the horizontal axis of Fig. 6 represents time, and the vertical axis represents pressure and open area.
  • the displacement of the first operator input device (181) is increased to increase the size of the first value, and accordingly, the open areas of each of the first control valve (141), the second control valve (142), and the boom down holding valve (150) increase.
  • the larger the set adjustment value the larger the open area of the first control valve (141) + the open area of the second control valve (142).
  • the larger the set adjustment value the larger the open area of the anti-drop valve (150).
  • a) represents the size of the first value
  • b) represents the opening area of the first control valve (141) + the opening area of the second control valve (142) when the adjustment value is 0%
  • c) represents the opening area of the first control valve (141) + the opening area of the second control valve (142) when the adjustment value is 50%
  • d) represents the opening area of the first control valve (141) + the opening area of the second control valve (142) when the adjustment value is 100%
  • e) represents the opening area of the anti-drop valve (150) when the adjustment value is 0%
  • f) represents the opening area of the anti-drop valve (150) when the adjustment value is 50%
  • g) represents the opening area of the anti-drop valve (150) when the adjustment value is 100%.
  • the present disclosure relates to a method for controlling a working machine, wherein the working machine comprises: a boom actuator having a bottom chamber and a piston rod side chamber; an operating fluid pump for supplying a pressurized operating fluid to the boom actuator; a tank for receiving the discharged operating fluid discharged from the boom actuator; a first control valve and a second control valve which are installed in parallel between the operating fluid pump and the tank and the boom actuator, respectively, for controlling the flow rate of the discharged operating fluid discharged from the boom actuator; a first operator input device for receiving a first value representing a desired opening degree of the valve, and a second operator input device for receiving a second value representing an adjustment value for adjusting the desired opening degree, and the method can provide a method for controlling a working machine by controlling the opening degree of the first control valve to be dependent on the first value, and controlling the opening degree of the second control valve to be dependent on the first value and the second value.
  • the above method can control the opening degree of the anti-drop valve to be dependent on the first value and the second value during a boom down operation in which the exhaust working fluid is discharged from the bottom chamber.
  • control unit including a processing circuit configured to perform the method described above, and a computer program including program code for performing the method described above when executed on the processing circuit of a computer or a control unit.
  • the processing circuit is provided using one or more combinations of a suitable central processing unit (CPU), a multiprocessor, a microcontroller, a digital signal processor (DSP), etc., capable of executing software instructions stored in a computer program product, for example in the form of a storage medium.
  • the processing circuit can further be provided as at least one application-specific integrated circuit (ASIC) or a field programmable gate array (FPGA).
  • ASIC application-specific integrated circuit
  • FPGA field programmable gate array
  • the processing circuit is configured to cause the control unit to perform a set of operations or steps, such as the methods described above.
  • the storage medium may store the set of operations
  • the processing circuit may be configured to retrieve the set of operations from the storage medium, such that the control unit performs the set of operations.
  • the set of operations may be provided as a set of executable instructions. Accordingly, the processing circuit is arranged to perform the methods disclosed herein.
  • the storage medium may also include persistent storage, which may be, for example, one or a combination of magnetic memory, optical memory, solid state memory, or further remotely mounted memory.
  • the control unit may further comprise an interface for communicating with external devices.
  • the interface may comprise a suitable number of ports for wireline or wireless communication and one or more transmitters and receivers comprising analog and digital components.
  • the processing circuit controls the general operation of the control unit, for example, by sending data and control signals to the interface and storage medium, receiving data and reports from the interface, and retrieving data and commands from the storage medium.
  • the relevant functions of the control node, as well as other components, are omitted so as not to obscure the concepts presented herein.
  • the computer-readable medium and the program code together can form a computer program product.

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

Abstract

La présente invention concerne un engin de chantier qui comprend : des vérins de flèche ayant chacun une chambre inférieure et une chambre latérale de tige de piston ; des pompes à fluide hydraulique pour alimenter en fluide de fonctionnement sous pression les vérins de flèche ; des réservoirs pour recevoir le fluide de fonctionnement évacué des vérins de flèche ; une première soupape de commande et une seconde soupape de commande qui sont disposées en parallèle entre les pompes à fluide hydraulique, les réservoirs et les vérins de flèche, et qui commandent le débit du fluide de fonctionnement évacué des vérins de flèche ; un premier dispositif d'entrée de fonctionnement pour recevoir une première valeur indiquant le degré d'ouverture requis de la soupape ; et un second dispositif d'entrée de fonctionnement pour recevoir une seconde valeur indiquant une valeur de réglage pour régler le degré d'ouverture requis. La première soupape de commande peut être ouverte et fermée de telle sorte que son degré d'ouverture dépend de la première valeur, et la seconde soupape de commande peut être ouverte et fermée de telle sorte que son degré d'ouverture dépend de la première valeur et de la seconde valeur. L'engin de chantier peut en outre comprendre des soupapes de sécurité disposées entre le vérin de flèche et la première soupape de commande et entre le vérin de flèche et la seconde soupape de commande. Lors d'une action de descente de flèche, au cours de laquelle le fluide de fonctionnement est évacué de la chambre inférieure, la soupape de sécurité peut être ouverte et fermée de telle sorte que son degré d'ouverture dépend de la première valeur et de la seconde valeur.
PCT/KR2023/009756 2023-07-10 2023-07-10 Engin de chantier Pending WO2025013962A1 (fr)

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Application Number Priority Date Filing Date Title
PCT/KR2023/009756 WO2025013962A1 (fr) 2023-07-10 2023-07-10 Engin de chantier

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/KR2023/009756 WO2025013962A1 (fr) 2023-07-10 2023-07-10 Engin de chantier

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WO2025013962A1 true WO2025013962A1 (fr) 2025-01-16

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20010010461A (ko) * 1999-07-20 2001-02-15 토니헬샴 안티 드롭 밸브가 일체된 방향 전환 밸브
JP2002227233A (ja) * 2001-02-06 2002-08-14 Shin Caterpillar Mitsubishi Ltd 作業機械におけるブームシリンダの油圧制御回路
KR20160101942A (ko) * 2013-12-26 2016-08-26 두산인프라코어 주식회사 건설기계의 유압시스템 및 유압시스템의 제어방법
JP2017106227A (ja) * 2015-12-09 2017-06-15 住友重機械工業株式会社 ショベル
CN115853846A (zh) * 2022-12-05 2023-03-28 广西柳工机械股份有限公司 升降液压系统和装载机

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20010010461A (ko) * 1999-07-20 2001-02-15 토니헬샴 안티 드롭 밸브가 일체된 방향 전환 밸브
JP2002227233A (ja) * 2001-02-06 2002-08-14 Shin Caterpillar Mitsubishi Ltd 作業機械におけるブームシリンダの油圧制御回路
KR20160101942A (ko) * 2013-12-26 2016-08-26 두산인프라코어 주식회사 건설기계의 유압시스템 및 유압시스템의 제어방법
JP2017106227A (ja) * 2015-12-09 2017-06-15 住友重機械工業株式会社 ショベル
CN115853846A (zh) * 2022-12-05 2023-03-28 广西柳工机械股份有限公司 升降液压系统和装载机

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