CN116379025A - Distributed closed pump control system and control method thereof - Google Patents

Distributed closed pump control system and control method thereof Download PDF

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Publication number
CN116379025A
CN116379025A CN202310356341.1A CN202310356341A CN116379025A CN 116379025 A CN116379025 A CN 116379025A CN 202310356341 A CN202310356341 A CN 202310356341A CN 116379025 A CN116379025 A CN 116379025A
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China
Prior art keywords
oil
hydraulic
valve
rod
way valve
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CN202310356341.1A
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Chinese (zh)
Inventor
丁孺琦
王伟
赵杨
蒋涵琦
郭言
董可
徐稷旺
蒋志勇
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Jiangsu Hengli Hydraulic Technology Co Ltd
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Jiangsu Hengli Hydraulic Technology Co Ltd
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Priority to CN202310356341.1A priority Critical patent/CN116379025A/en
Publication of CN116379025A publication Critical patent/CN116379025A/en
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    • 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
    • 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
    • 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
    • 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
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/26—Supply reservoir or sump assemblies
    • F15B1/265—Supply reservoir or sump assemblies with pressurised main reservoir
    • 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
    • F15B21/04—Special measures taken in connection with the properties of the fluid
    • F15B21/041—Removal or measurement of solid or liquid contamination, e.g. filtering
    • 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
    • F15B21/04—Special measures taken in connection with the properties of the fluid
    • F15B21/042—Controlling the temperature of the fluid
    • F15B21/0423—Cooling
    • 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
    • F15B2211/20576—Systems with pumps with multiple pumps

Abstract

The invention discloses a distributed closed pump control system and a control method thereof, wherein the distributed closed pump control system comprises: the device comprises a bucket rod closed pump control module, a movable arm closed pump control module, a pressurized oil tank, a filtering mechanism and a cooling mechanism, wherein one end of the filtering mechanism is communicated with an inlet of the cooling mechanism, an outlet of the cooling mechanism is communicated with an inlet of the pressurized oil tank, the bucket rod closed pump control module and the movable arm closed pump control module are all communicated with the other end of the filtering mechanism, and the bucket rod closed pump control module and the movable arm closed pump control module are all communicated with an outlet of the pressurized oil tank. According to the invention, through improvement of the loop, the bucket rod closed pump control module and the movable arm closed pump control module can share one pressurizing oil tank, one filtering mechanism and one cooling mechanism, so that the volume of the pump control system can be remarkably reduced, the system is convenient to flexibly arrange in the position of an excavator cabin and the like, the volume and the weight of the mechanical arm of the excavator can be reduced, and the cost is saved.

Description

Distributed closed pump control system and control method thereof
Technical Field
The invention relates to the technical field of hydraulic systems, in particular to a distributed closed pump control system and a control method thereof.
Background
At present, the hydraulic system is widely applied to engineering machinery, and most of the hydraulic systems in the engineering machinery adopt valve control systems. For example, hydraulic excavators are typical construction machines, and are widely used in the fields of construction, mining, and the like. At present, a hydraulic excavator widely adopts a constant-rotation-speed diesel engine to drive a variable hydraulic pump as a power source to provide high-pressure oil, distributes and transmits energy through a pipeline and a control valve, and drives and controls a plurality of hydraulic cylinders and hydraulic motors. The existing valve-controlled hydraulic system has at least the following disadvantages:
1. the flow distribution through the multi-way valve has larger throttling loss, and the wiring pipelines are more, so that the along-path pressure loss of the system is larger.
2. The efficiency of driving the hydraulic pump by the internal combustion engine is low.
3. The existing valve-controlled hydraulic system is integrated into a set of electrohydraulic actuators (EHA), and comprises an independent energy accumulator, a hydraulic cylinder, a motor, a control valve group and the like; that is, a valve-controlled hydraulic system needs to be equipped with an independent accumulator (the accumulator acts to compensate for cylinder asymmetric flow, hydraulic pump/cylinder leakage, etc.). This results in the volume, weight, of the electro-hydraulic actuator (EHA) as a whole becoming significant (the valve controlled hydraulic system occupies about 40% of the volume of EHA) and adding more load weight to the excavator arm.
Disclosure of Invention
The invention aims to solve the technical problems that: the technical problem of weight and volume increase of the mechanical arm caused by the existing valve-controlled hydraulic system is solved. The invention provides a distributed closed pump control system and a control method thereof, wherein a movable arm and a bucket rod closed pump control module share a pressurizing oil tank, a filtering mechanism and a cooling mechanism, so that the volume of the closed pump control system can be remarkably reduced, and the closed pump control system can be flexibly arranged in an excavating cabin, thereby reducing the weight of a mechanical arm.
The technical scheme adopted for solving the technical problems is as follows: a distributed closed pump control system comprising: the device comprises a bucket rod closed pump control module, a movable arm closed pump control module, a pressurized oil tank, a filtering mechanism and a cooling mechanism, wherein one end of the filtering mechanism is communicated with an inlet of the cooling mechanism, an outlet of the cooling mechanism is communicated with an inlet of the pressurized oil tank, the bucket rod closed pump control module and the movable arm closed pump control module are both communicated with the other end of the filtering mechanism, and the bucket rod closed pump control module and the movable arm closed pump control module are both communicated with an outlet of the pressurized oil tank.
Further, the arm closed pump control module includes: the hydraulic system comprises a first motor, a first hydraulic pump, a first overflow valve, a second overflow valve, a first one-way valve, a second one-way valve, a first stop valve, a bucket rod hydraulic cylinder, a fifth one-way valve and an eighth one-way valve;
the first motor is connected with the first hydraulic pump, and oil inlets of the first overflow valve and the second overflow valve are respectively communicated with an oil port A, B of the first hydraulic pump; the oil outlets of the first overflow valve and the second overflow valve are communicated with one end of the first stop valve;
the oil outlets of the first one-way valve and the second one-way valve are respectively communicated with a rod cavity and a rodless cavity of the bucket rod hydraulic cylinder; the oil inlets of the first check valve and the second check valve are communicated with one end of the first stop valve;
the oil inlet of the fifth one-way valve and the oil outlet of the eighth one-way valve are communicated with the other end of the first stop valve; an oil outlet of the fifth one-way valve is communicated with the filter mechanism, and an oil inlet of the eighth one-way valve is communicated with an outlet of the supercharged oil tank.
Further, the boom closed pump control module includes: the hydraulic system comprises a second motor, a second hydraulic pump, a third overflow valve, a fourth overflow valve, a third one-way valve, a fourth one-way valve, a second stop valve, a movable arm hydraulic cylinder, a sixth one-way valve and a seventh one-way valve;
the second motor is connected with the second hydraulic pump, and oil inlets of the third overflow valve and the fourth overflow valve are respectively communicated with an oil port A, B of the second hydraulic pump; the oil outlets of the third overflow valve and the fourth overflow valve are communicated with one end of the second stop valve;
the oil outlets of the third one-way valve and the fourth one-way valve are respectively communicated with a rod cavity and a rodless cavity of the movable arm hydraulic cylinder; the oil inlets of the third check valve and the fourth check valve are communicated with one end of the second stop valve;
the oil inlet of the sixth one-way valve and the oil outlet of the seventh one-way valve are communicated with the other end of the second stop valve; an oil outlet of the sixth one-way valve is communicated with the filter mechanism, and an oil inlet of the seventh one-way valve is communicated with an outlet of the supercharged oil tank.
Further, the arm closed pump control module further comprises: and one end of the third stop valve is connected with the first hydraulic pump, and the other end of the third stop valve is connected with the other end of the filtering mechanism.
Further, the boom closed pump control module further includes: and one end of the fourth stop valve is connected with the second hydraulic pump, and the other end of the fourth stop valve is connected with the other end of the filtering mechanism.
Further, the pressurized oil tank includes: the device comprises a shell and an air bag arranged in the shell, wherein an oil tank inlet and an oil tank outlet are respectively arranged at two ends of the shell; rated capacity of the pressurizing oil tank (3)Product of
Figure BDA0004163401390000031
Wherein DeltaV represents the volume change amount of the pressurized fuel tank (3), p 0 Represents the inflation pressure of the airbag (32), p 1 Represents the minimum operating pressure, p, of the pressurized fuel tank (3) 2 Represents the highest operating pressure of the pressurized fuel tank (3), and k represents the temperature influence index.
The invention also provides a control method of the distributed closed pump control system, which comprises the following steps:
s1, respectively controlling a bucket rod closed pump control module and a movable arm closed pump control module according to four-quadrant characteristics of a load;
s2, respectively supplementing oil or returning oil to the bucket rod closed pump control module and the movable arm closed pump control module through a pressurizing oil tank;
and S3, when oil returns, the oil returns to the supercharged oil tank through the filtering mechanism and the cooling mechanism in sequence.
Further, the retraction direction of the hydraulic rods of the first hydraulic pump and the second hydraulic pump is set as the positive speed direction, and the extension direction of the hydraulic rods is set as the positive force direction of the hydraulic cylinders; the working process of the bucket rod closed pump control module is as follows:
first quadrant operating mode: when the hydraulic rod of the bucket rod hydraulic cylinder stretches out, the direction of the hydraulic rod is opposite to the load stress, and at the moment, the first hydraulic pump is in a pumping mode; high-pressure oil flows from an A oil port of the first hydraulic pump to a rodless cavity of the bucket rod hydraulic cylinder, low-pressure oil with a rod cavity flows back to a B oil port of the first hydraulic pump, at the moment, the pressure of the rodless cavity is higher than that of the rod cavity, the high-pressure oil with the rodless cavity flows to a loop of the first one-way valve, the first one-way valve is opened, and at the moment, replenishment oil in the pressurizing oil tank flows to the B oil port of the first hydraulic pump through an eighth one-way valve, a first stop valve and a first one-way valve;
second quadrant operating mode: the hydraulic rod of the bucket rod hydraulic cylinder extends in the same direction as the load stress direction, and at the moment, the first hydraulic pump is in a motor mode; when a load pulls a hydraulic rod of the first hydraulic pump to extend, high-pressure oil in a rod cavity of the bucket rod hydraulic cylinder flows to an oil port B of the first hydraulic pump, and low-pressure oil flows from an oil port A of the first hydraulic pump to a rod-free cavity of the bucket rod hydraulic cylinder; at the moment, the pressure of the rod cavity is larger than that of the rodless cavity, high-pressure oil in the rod cavity flows to a loop of the second one-way valve, the second one-way valve is opened, and the replenishing oil in the pressurized oil tank flows to the rodless cavity of the bucket rod hydraulic cylinder through the eighth one-way valve, the first stop valve and the second one-way valve;
third quadrant operating mode: when the hydraulic rod of the bucket rod hydraulic cylinder is retracted, the direction of the hydraulic rod is opposite to the load stress, and at the moment, the first hydraulic pump is in a pumping mode; high-pressure oil flows from the B oil port of the first hydraulic pump to the rod cavity of the bucket rod hydraulic cylinder, low-pressure oil of the rodless cavity flows to the A oil port of the first hydraulic pump, at the moment, the pressure of the rod cavity is larger than that of the rodless cavity, the high-pressure oil of the rod cavity flows to a loop of the second one-way valve, the second one-way valve is opened, and redundant hydraulic oil of the rodless cavity returns to the pressurizing oil tank through the second one-way valve, the first stop valve, the fifth one-way valve, the filtering mechanism and the cooling mechanism;
fourth quadrant operating mode: the hydraulic rod of the bucket rod hydraulic cylinder is retracted in the same direction as the load bearing direction, and at the moment, the first hydraulic pump is in a motor mode; the hydraulic oil of the rodless cavity of the bucket rod hydraulic cylinder flows to the A oil port of the first hydraulic pump, the hydraulic oil of the hydraulic oil flows to the rod cavity of the bucket rod hydraulic cylinder from the B oil port of the first hydraulic pump, at the moment, the pressure of the rodless cavity is larger than that of the rod cavity, the hydraulic oil of the rodless cavity flows to a loop of the first one-way valve, the first one-way valve is opened, and redundant hydraulic oil in the rod cavity returns to the pressurizing oil tank through the first one-way valve, the first stop valve, the fifth one-way valve, the filtering mechanism and the cooling mechanism.
Further, the working process of the movable arm closed pump control module is as follows:
first quadrant operating mode: when the hydraulic rod of the movable arm hydraulic cylinder stretches out, the direction of the hydraulic rod is opposite to the load stress, and at the moment, the second hydraulic pump is in a pumping mode; high-pressure oil flows from an A oil port of the second hydraulic pump to a rodless cavity of the movable arm hydraulic cylinder, low-pressure oil with a rod cavity flows back to a B oil port of the second hydraulic pump, at the moment, the pressure of the rodless cavity is larger than that of the rod cavity, the high-pressure oil with the rodless cavity flows to a loop of the third one-way valve, the third one-way valve is opened, and at the moment, replenishment oil in the pressurizing oil tank flows to the B oil port of the second hydraulic pump through the seventh one-way valve, the second stop valve and the third one-way valve;
fourth quadrant operating mode: the hydraulic rod of the movable arm hydraulic cylinder is retracted in the same direction as the load stress direction, and at the moment, the second hydraulic pump is in a motor mode; the high-pressure oil of the rodless cavity of the movable arm hydraulic cylinder flows to the A oil port of the second hydraulic pump, the low-pressure oil flows to the rod cavity of the movable arm hydraulic cylinder from the B oil port of the second hydraulic pump, at the moment, the pressure of the rodless cavity is larger than that of the rod cavity, the high-pressure oil of the rodless cavity flows to a loop of the third one-way valve, the third one-way valve is opened, and redundant hydraulic oil in the rod cavity returns to the pressurizing oil tank through the third one-way valve, the second stop valve, the sixth one-way valve, the filtering mechanism and the cooling mechanism.
The distributed closed pump control system and the control method thereof have the beneficial effects that through the improvement of a loop, the bucket rod closed pump control module and the movable arm closed pump control module can share one pressurizing oil tank, one filtering mechanism and one cooling mechanism, the volume of the pump control system can be obviously reduced, the system is convenient to flexibly arrange in the position of an excavating cabin and the like, the volume and the weight of an excavator mechanical arm can be reduced, and the cost is saved. Through the setting of four check valves, can realize the independent operation of oil supply return circuit, return circuit to, when the oil return, the fluid of backward flow must get back to in the supercharged oil tank through filtering mechanism, cooling body, can guarantee the cleanliness and the cooling of retrieving fluid. When the movable arm and the bucket rod need to be supplemented with oil, the hydraulic oil of the pressurizing oil tank is cooled, so that performance reduction and even damage of the system caused by overhigh oil temperature can be avoided.
Drawings
The invention will be further described with reference to the drawings and examples.
Fig. 1 is a block diagram of a distributed closed pump control system of the present invention.
Fig. 2 is a schematic structural diagram of the distributed closed pump control system of the present invention.
Fig. 3 is a schematic structural view of the pressurized fuel tank of the present invention.
FIG. 4 is a schematic diagram of a four-quadrant operating condition of the present invention.
In the figure:
1. a bucket rod closed pump control module; 101. a first motor; 102. a first hydraulic pump; 103. a first overflow valve; 104. a second overflow valve; 107. a first one-way valve; 108. a second one-way valve; 109. a first stop valve; 110. a bucket rod hydraulic cylinder; 111. a third stop valve; 61. a fifth check valve; 64. an eighth check valve;
2. a movable arm closed pump control module; 201. a second motor; 202. a second hydraulic pump; 203. a third overflow valve; 204. a fourth overflow valve; 207. a third one-way valve; 208. a fourth one-way valve; 209. a second shut-off valve; 210. a boom cylinder; 211. a fourth shut-off valve; 62. a sixth one-way valve; 63. a seventh one-way valve;
3. a pressurized oil tank; 31. a housing; 32. an air bag; 33. an oil tank inlet; 34. an outlet of the oil tank;
4. a filtering mechanism; 5. and a cooling mechanism.
Detailed Description
The invention will now be described in further detail with reference to the accompanying drawings. The drawings are simplified schematic representations which merely illustrate the basic structure of the invention and therefore show only the structures which are relevant to the invention.
In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings are merely for convenience in describing the present invention and simplifying the description, and do not indicate or imply that the device or element being referred to must have a specific orientation, be configured and operated in a specific orientation, and therefore should not be construed as limiting the present invention. Furthermore, features defining "first", "second" may include one or more such features, either explicitly or implicitly. In the description of the present invention, unless otherwise indicated, the meaning of "a plurality" is two or more.
In the description of the present invention, it should be noted that, unless explicitly specified and limited otherwise, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be either fixedly connected, detachably connected, or integrally connected, for example; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium, and can be communication between two elements. The specific meaning of the above terms in the present invention will be understood in specific cases by those of ordinary skill in the art.
As shown in fig. 1 to 3, the distributed closed pump control system of the present invention includes: the bucket rod closed pump control module 1, the movable arm closed pump control module 2, the booster oil tank 3, the filtering mechanism 4 and the cooling mechanism 5, wherein one end of the filtering mechanism 4 is communicated with the inlet of the cooling mechanism 5, the outlet of the cooling mechanism 5 is communicated with the inlet of the booster oil tank 3, the bucket rod closed pump control module 1 and the movable arm closed pump control module 2 are all communicated with the other end of the filtering mechanism 4, and the bucket rod closed pump control module 1 and the movable arm closed pump control module 2 are all communicated with the outlet of the booster oil tank 3. According to the invention, the bucket rod closed pump control module 1 and the movable arm closed pump control module 2 share one pressurizing oil tank 3, the filtering mechanism 4 and the cooling mechanism 5, so that the volume of the closed pump control system can be remarkably reduced, and the closed pump control system can be flexibly arranged in an excavating cabin, thereby reducing the weight of the mechanical arm.
Specifically, the arm closed pump control module 1 includes: first motor 101, first hydraulic pump 102, first relief valve 103, second relief valve 104, first check valve 107, second check valve 108, first shutoff valve 109, arm cylinder 110, fifth check valve 61, and eighth check valve 64. The first motor 101 is connected with the first hydraulic pump 102, and oil inlets of the first overflow valve 103 and the second overflow valve 104 are respectively communicated with an oil port A, B of the first hydraulic pump 102; the oil outlets of the first overflow valve 103 and the second overflow valve 104 are communicated with one end of a first stop valve 109; the oil outlets of the first check valve 107 and the second check valve 108 are respectively communicated with a rod cavity and a rodless cavity of the bucket rod hydraulic cylinder 110; the oil inlets of the first check valve 107 and the second check valve 108 are communicated with one end of the first stop valve 109; the oil inlet of the fifth one-way valve 61 and the oil outlet of the eighth one-way valve 64 are communicated with the other end of the first stop valve 109; the oil outlet of the fifth one-way valve 61 is communicated with the filtering mechanism 4, and the oil inlet of the eighth one-way valve 64 is communicated with the outlet of the supercharged oil tank 3. The arm closed pump control module 1 further includes: and a third stop valve 111, one end of the third stop valve 111 is connected to the first hydraulic pump 102, and the other end of the third stop valve 111 is connected to the other end of the filter mechanism 4.
Specifically, the boom closed pump control module 2 includes: second motor 201, second hydraulic pump 202, third relief valve 203, fourth relief valve 204, third check valve 207, fourth check valve 208, second shutoff valve 209, boom cylinder 210, sixth check valve 62, and seventh check valve 63. The second motor 201 is connected with the second hydraulic pump 202, and oil inlets of the third overflow valve 203 and the fourth overflow valve 204 are respectively communicated with an oil port A, B of the second hydraulic pump 202; the oil outlets of the third overflow valve 203 and the fourth overflow valve 204 are communicated with one end of a second stop valve 209; the oil outlets of the third check valve 207 and the fourth check valve 208 are respectively communicated with a rod cavity and a rodless cavity of the movable arm hydraulic cylinder 210; the oil inlets of the third check valve 207 and the fourth check valve 208 are communicated with one end of the second stop valve 209; the oil inlet of the sixth one-way valve 62 and the oil outlet of the seventh one-way valve 63 are communicated with the other end of the second stop valve 209; the oil outlet of the sixth check valve 62 is communicated with the filtering mechanism 4, and the oil inlet of the seventh check valve 63 is communicated with the outlet of the pressurized oil tank 3. The boom closed pump control module 2 further includes: and a fourth shut-off valve 211, wherein one end of the fourth shut-off valve 211 is connected to the second hydraulic pump 202, and the other end of the fourth shut-off valve 211 is connected to the other end of the filter mechanism 4.
The hydraulic pump can be driven to operate, oil is sucked from the hydraulic oil tank, and pressure oil is discharged, so that the extension or retraction of the hydraulic cylinder is controlled. The overflow valve can enable redundant oil to overflow the oil return tank, and the pressure of the system is balanced. The one-way valve plays a one-way conduction role. The stop valve is used for switching on or switching off a loop, and can control the blocking or circulation of liquid.
The fifth check valve 61, the sixth check valve 62, the seventh check valve 63 and the eighth check valve 64 of the present invention can realize the separation operation of the oil supplementing loop and the oil returning loop, and the two loops do not collide, and during oil returning, the oil must be filtered by the filtering mechanism 4, cooled by the cooling mechanism 5 and returned to the supercharged oil tank 3. Therefore, the cleanliness and the temperature of the oil liquid which flows back can be ensured, and the influence on the normal operation of the system caused by the overhigh oil temperature in the system is prevented. In addition, the fifth check valve 61, the eighth check valve 64, the sixth check valve 62 and the seventh check valve 63 are arranged at positions close to the hydraulic pump, so that a pipeline between the check valve and the hydraulic pump can be shortened, hydraulic oil can not form stagnation in a loop, working hot oil can be smoothly discharged from the bucket rod closed pump control module 1 and the movable arm closed pump control module 2, and cooled oil can also smoothly enter the hydraulic pump.
Specifically, the pressurized oil tank 3 includes: the device comprises a shell 31 and an air bag 32 arranged in the shell 31, wherein an oil tank inlet 33 and an oil tank outlet 34 are respectively arranged at two ends of the shell 31; rated volume of pressurized fuel tank 3
Figure BDA0004163401390000091
Wherein DeltaV represents the volume change amount of the pressurized fuel tank 3, p 0 Representing the inflation pressure, p, of the balloon 32 1 Indicating the lowest operating pressure, p, of the pressurized fuel tank 3 2 The highest operating pressure of the pressurized fuel tank 3 is indicated, and k indicates the temperature influence index. For example, k=1 at isothermal and k=1.4 at adiabatic.
The pressurizing oil tank 3 can be used for compensating asymmetric flow when the hydraulic cylinder extends and absorbing asymmetric flow when the hydraulic cylinder retracts, so that balance of system flow is realized; the flow rate of the system leakage can be supplemented. The air bag 32 of the pressurized oil tank 3 is filled with gas having a certain pressure, and the space between the housing 21 and the air bag 32 is used for containing oil. Rated volume V of pressurized tank 3 0 The size of (2) determines the volume of oil stored in the hydraulic pump, and if the volume is too small, the pressure is reduced too quickly to meet the working requirement. The operating parameters of the pressurized fuel tank 3 mainly include: inflation pressure p 0 Minimum operating pressure p 1 Maximum working pressure p 2 Rated capacityProduct V 0 . When the minimum working pressure value of the pressurized oil tank 3 is too small, after the loss of the path pressure of a loop, a valve, a joint and the like, negative pressure and cavitation can occur in an oil suction port of the pump, so that the service life of the pump is reduced, and the stable operation of the system is affected. The pressure of the system oil supply is generally 0.3MPa to 1MPa, so the lowest working pressure is p 1 > 0.3MPa to meet the minimum oil make-up pressure of the system. The installation space inside the hydraulic excavator is limited, and therefore, the size of the entire pressurized oil tank 3 cannot be too large, otherwise it is inconvenient to install. When the pressurized oil tank 3 is replenished with oil, the oil in the pressurized oil tank 3 needs to be conveyed to the hydraulic pump, and at this time, the volume of the air bag 32 is increased; when the pressurized oil tank 3 absorbs oil, the excess oil in the circuit needs to be sucked into the pressurized oil tank 3, and at this time, the volume of the air bag 32 is reduced. That is, the airbag 32 needs to be deformed frequently. In order to prevent the airbag 32 from being damaged by too great a deformation, the pressurized fuel tank 3 reaches the maximum operating pressure p 2 When the balloon 32 is contracted, the volume should be greater than 1/4 of the volume in the inflated state. Thereby, the highest operating pressure p of the pressurized fuel tank 3 2 And inflation pressure p 0 Should satisfy p 0 ＞0.25p 2 . For example, in the present invention, p 1 ＝0.5MPa，p 2 ＝1MPa，p 0 ＝0.9p 1 =0.45 MPa. The volume change DeltaV of the pressurizing oil tank 3 is calculated according to the volume difference of the rod cavity and the rodless cavity of the hydraulic cylinder,
Figure BDA0004163401390000101
d represents the diameter of the rod cavity, unit mm, and l represents the moving stroke of the hydraulic rod, unit m. For example, Δv=4.3l is calculated from the actual parameters. For example, the present system does not consider temperature effects, k=1.4. Thus, the rated volume V of the pressurized fuel tank 3 can be calculated based on the above data 0 =11.92L, whereby the rated volume of the pressurized fuel tank 3 can be designed to be 12L.
That is, the present invention comprehensively considers various aspects (aspects of meeting the minimum oil replenishing pressure of the system, meeting the installation space, prolonging the service life of the pressurized oil tank, etc.) in designing the pressurized oil tank 3, so as to seek an optimal design. In addition, the oil tank inlet 33 and the oil tank outlet 34 of the pressurized oil tank are respectively positioned at two ends of the shell 31, so that the recovered oil liquid can be cooled again to a certain extent after entering the pressurized oil tank 3. According to the scheme of sharing the pressurizing oil tank 3, independent oil supplementing and oil returning can be realized on the two modules of the bucket rod closed pump control module 1 and the movable arm closed pump control module 2, so that the flow of hydraulic oil in a system is balanced, and the discharge and suction flow of the pump is matched with the flow required by two chambers of the hydraulic cylinder.
The invention also provides a control method of the distributed closed pump control system, which comprises the following steps: s1, respectively controlling a bucket rod closed pump control module 1 and a movable arm closed pump control module 2 according to four-quadrant characteristics of a load;
s2, oil supplementing or oil returning is carried out on the bucket rod closed pump control module 1 and the movable arm closed pump control module 2 through the pressurizing oil tank 3 respectively; and S3, when oil returns, the oil returns to the supercharged oil tank 3 through the filtering mechanism 4 and the cooling mechanism 5 in sequence.
Because the bucket rod and the movable arm perform compound actions in the excavating process, the pressure of the two chambers of the hydraulic cylinder can be greatly changed due to the change of the load, and therefore, the hydraulic pump control system controls the pump control module according to the four-quadrant characteristic of the load, so that the hydraulic pump can be switched between a pump mode and a motor mode, and further, the discharge flow rate and the suction flow rate of the pump can be matched with the flow rate required by the two chambers of the hydraulic cylinder.
For example, the hydraulic rod retraction direction of the first hydraulic pump 102 and the second hydraulic pump 202 is set to be the positive speed direction, and the hydraulic rod extension direction is set to be the positive direction in which the hydraulic cylinder is forced.
As shown in fig. 4, the working process of the arm closed pump control module 1 is as follows:
first quadrant operating mode: when the hydraulic rod of the bucket rod hydraulic cylinder 110 extends, the direction of the load stress is opposite (namely, the bucket rod is blocked and resists the load extending), and at the moment, the first hydraulic pump 102 is in a pumping mode; high-pressure oil flows from an A oil port of the first hydraulic pump 102 to a rodless cavity of the bucket rod hydraulic cylinder 110, low-pressure oil with a rod cavity flows back to a B oil port of the first hydraulic pump 102, at the moment, the pressure of the rodless cavity is larger than that of the rod cavity, high-pressure oil with the rodless cavity flows to a loop of the first one-way valve 107, the first one-way valve 107 is opened, and at the moment, the replenishing oil in the pressurizing oil tank 3 flows to the B oil port of the first hydraulic pump 102 through the eighth one-way valve 64, the first stop valve 109 and the first one-way valve 107.
Second quadrant operating mode: when the hydraulic rod of the bucket rod hydraulic cylinder 110 extends, the direction of the load stress is the same (i.e. the bucket rod extends under the exceeding load), and at this time, the first hydraulic pump 102 is in a motor mode; when the load pulls the hydraulic rod of the first hydraulic pump 102 to extend, high-pressure oil in the rod cavity of the bucket rod hydraulic cylinder 110 flows to the oil port B of the first hydraulic pump 102, and low-pressure oil flows from the oil port A of the first hydraulic pump 102 to the rod-free cavity of the bucket rod hydraulic cylinder 110; at this time, the pressure of the rod-containing chamber is larger than the pressure of the rod-free chamber, the high-pressure oil in the rod-containing chamber flows to the circuit of the second check valve 108, the second check valve 108 is opened, and the replenishment oil in the pressurized oil tank 3 flows to the rod-free chamber of the arm cylinder 110 through the eighth check valve 64, the first check valve 109, and the second check valve 108.
Third quadrant operating mode: when the hydraulic rod of the arm hydraulic cylinder 110 is retracted, the direction of the load stress is opposite (namely, the arm is blocked and the load is prevented from retracting), and at this time, the first hydraulic pump 102 is in a pumping mode; the high-pressure oil flows from the port B of the first hydraulic pump 102 to the rod cavity of the arm hydraulic cylinder 110, the low-pressure oil of the rodless cavity flows to the port a of the first hydraulic pump 102, at this time, the pressure of the rod cavity is greater than that of the rodless cavity, the high-pressure oil of the rod cavity flows to the loop of the second check valve 108, the second check valve 108 is opened, and the redundant hydraulic oil of the rodless cavity returns to the pressurized oil tank 3 through the second check valve 108, the first stop valve 109, the fifth check valve 61, the filter mechanism 4 and the cooling mechanism 5.
Fourth quadrant operating mode: when the hydraulic rod of the bucket rod hydraulic cylinder 110 is retracted, the direction of the load stress is the same (i.e. the bucket rod is retracted by overrunning load), and at this time, the first hydraulic pump 102 is in a motor mode; the high-pressure oil of the rodless cavity of the arm hydraulic cylinder 110 flows to the port a of the first hydraulic pump 102, the low-pressure oil flows from the port B of the first hydraulic pump 102 to the rod-containing cavity of the arm hydraulic cylinder 110, at this time, the pressure of the rodless cavity is larger than that of the rod-containing cavity, the high-pressure oil of the rodless cavity flows to the loop of the first check valve 107, the first check valve 107 is opened, and the redundant hydraulic oil of the rod-containing cavity returns to the pressurized oil tank 3 through the first check valve 107, the first stop valve 109, the fifth stop valve 71, the fifth check valve 61, the filter mechanism 4 and the cooling mechanism 5.
Because the working condition of the movable arm is single relative to the bucket rod, the movable arm generally swings up and down in the actual working process, and therefore, the movement of the movable arm only involves two quadrants. The working process of the movable arm closed pump control module 2 is as follows: first quadrant operating mode: when the hydraulic rod of the boom cylinder 210 is extended, the direction of the load is opposite to that of the load (i.e. the boom is blocked and resists the extension of the load), and at this time, the second hydraulic pump 202 is in a pumping mode; high-pressure oil flows from the A port of the second hydraulic pump 202 to the rodless cavity of the boom cylinder 210, low-pressure oil with a rod cavity flows back to the B port of the second hydraulic pump 202, at this time, the pressure of the rodless cavity is larger than that of the rod cavity, high-pressure oil with the rodless cavity flows to the loop of the third one-way valve 207, the third one-way valve 207 is opened, and at this time, makeup oil in the pressurized oil tank 3 flows to the B port of the second hydraulic pump 202 through the seventh one-way valve 63, the second stop valve 209 and the third one-way valve 207.
Fourth quadrant operating mode: the hydraulic rod of the boom cylinder 210 is retracted in the same direction as the load force (i.e., the boom is retracted under an overrunning load), and at this time, the second hydraulic pump 202 is in the motor mode; the high-pressure oil of the rodless cavity of the boom cylinder 210 flows to the port a of the second hydraulic pump 202, the low-pressure oil flows from the port B of the second hydraulic pump 202 to the rod-containing cavity of the boom cylinder 210, at this time, the pressure of the rodless cavity is greater than that of the rod-containing cavity, the high-pressure oil of the rodless cavity flows to the circuit of the third check valve 207, the third check valve 207 is opened, and the surplus hydraulic oil of the rod-containing cavity returns to the pressurized oil tank 3 through the third check valve 207, the second stop valve 209, the sixth check valve 62, the filter mechanism 4, and the cooling mechanism 5.
In summary, according to the distributed closed pump control system and the control method thereof, through improvement of the loop, the bucket rod closed pump control module 1 and the movable arm closed pump control module 2 can share one pressurizing oil tank 3, the filtering mechanism 4 and the cooling mechanism 5, so that the volume of the pump control system can be remarkably reduced, the system is convenient to flexibly arrange in the position of an excavating cabin and the like, the volume and the weight of an excavator mechanical arm can be reduced, and the cost is saved. The four check valves are arranged, so that independent operation of an oil supplementing loop and an oil returning loop can be realized, the fifth check valve 61, the eighth check valve 64, the sixth check valve 62 and the seventh check valve 63 are arranged at positions close to the hydraulic pump, and pipelines between the check valves and the hydraulic pump can be shortened, so that hydraulic oil cannot form stagnation in the loop, working hot oil can be smoothly discharged from the bucket rod closed pump control module 1 and the movable arm closed pump control module 2, and cooled oil can also smoothly enter the hydraulic pump; and in the oil return, the oil liquid which flows back must pass through the filtering mechanism 4 and the cooling mechanism 5 and return to the supercharged oil tank 3, so that the cleanliness of the recovered oil liquid and the cooling and the temperature reduction can be ensured. When the movable arm and the bucket rod need to be supplemented with oil, the hydraulic oil of the pressurizing oil tank 3 is cooled, so that performance reduction and even damage of the system caused by overhigh oil temperature can be avoided.
With the above-described preferred embodiments according to the present invention as an illustration, the above-described descriptions can be used by persons skilled in the relevant art to make various changes and modifications without departing from the scope of the technical idea of the present invention. The technical scope of the present invention is not limited to the description, but must be determined as the scope of the claims.

Claims (9)

1. A distributed closed pump control system, comprising:
bucket rod closed pump accuse module (1), swing arm closed pump accuse module (2), supercharged oil tank (3), filtering mechanism (4) and cooling body (5), the one end of filtering body (4) with the import of cooling body (5) is linked together, the export of cooling body (5) with the import of supercharged oil tank (3) is linked together, bucket rod closed pump accuse module (1), swing arm closed pump accuse module (2) all with the other end of filtering body (4) is linked together, bucket rod closed pump accuse module (1), swing arm closed pump accuse module (2) all with the export of supercharged oil tank (3) is linked together.
2. A distributed closed pump control system according to claim 1, wherein the stick closed pump control module (1) comprises: a first motor (101), a first hydraulic pump (102), a first relief valve (103), a second relief valve (104), a first check valve (107), a second check valve (108), a first stop valve (109), a arm cylinder (110), a fifth check valve (61), and an eighth check valve (64);
the first motor (101) is connected with the first hydraulic pump (102), and oil inlets of the first overflow valve (103) and the second overflow valve (104) are respectively communicated with a A, B oil port of the first hydraulic pump (102); the oil outlets of the first overflow valve (103) and the second overflow valve (104) are communicated with one end of the first stop valve (109);
the oil outlets of the first one-way valve (107) and the second one-way valve (108) are respectively communicated with a rod cavity and a rodless cavity of the bucket rod hydraulic cylinder (110); the oil inlets of the first check valve (107) and the second check valve (108) are communicated with one end of the first stop valve (109);
the oil inlet of the fifth one-way valve (61) and the oil outlet of the eighth one-way valve (64) are communicated with the other end of the first stop valve (109); an oil outlet of the fifth one-way valve (61) is communicated with the filtering mechanism (4), and an oil inlet of the eighth one-way valve (64) is communicated with an outlet of the pressurizing oil tank (3).
3. A distributed closed pump control system according to claim 2, wherein the boom closed pump control module (2) comprises: a second motor (201), a second hydraulic pump (202), a third overflow valve (203), a fourth overflow valve (204), a third check valve (207), a fourth check valve (208), a second stop valve (209), a boom cylinder (210), a sixth check valve (62), and a seventh check valve (63);
the second motor (201) is connected with the second hydraulic pump (202), and oil inlets of the third overflow valve (203) and the fourth overflow valve (204) are respectively communicated with a A, B oil port of the second hydraulic pump (202); the oil outlets of the third overflow valve (203) and the fourth overflow valve (204) are communicated with one end of the second stop valve (209);
the oil outlets of the third check valve (207) and the fourth check valve (208) are respectively communicated with a rod cavity and a rodless cavity of the movable arm hydraulic cylinder (210); the oil inlets of the third check valve (207) and the fourth check valve (208) are communicated with one end of the second stop valve (209);
the oil inlet of the sixth one-way valve (62) and the oil outlet of the seventh one-way valve (63) are communicated with the other end of the second stop valve (209); an oil outlet of the sixth one-way valve (62) is communicated with the filtering mechanism (4), and an oil inlet of the seventh one-way valve (63) is communicated with an outlet of the pressurizing oil tank (3).
4. A distributed closed pump control system according to claim 2, wherein the stick closed pump control module (1) further comprises: and a third stop valve (111), wherein one end of the third stop valve (111) is connected with the first hydraulic pump (102), and the other end of the third stop valve (111) is connected with the other end of the filter mechanism (4).
5. A distributed closed pump control system according to claim 3, wherein the boom closed pump control module (2) further comprises: and a fourth stop valve (211), wherein one end of the fourth stop valve (211) is connected with the second hydraulic pump (202), and the other end of the fourth stop valve (211) is connected with the other end of the filter mechanism (4).
6. A distributed closed pump control system according to claim 3, wherein the pressurized oil tank (3) comprises: the device comprises a shell (31) and an air bag (32) arranged in the shell (31), wherein an oil tank inlet (33) and an oil tank outlet (34) are respectively arranged at two ends of the shell (31); rated volume of the pressurized oil tank (3)
Figure FDA0004163401360000031
Wherein DeltaV represents the volume change amount of the pressurized fuel tank (3), p 0 Represents the inflation pressure of the airbag (32), p 1 Represents the minimum operating pressure, p, of the pressurized fuel tank (3) 2 Represents the highest operating pressure of the pressurized fuel tank (3), and k represents the temperature influence index.
7. A control method of a distributed closed pump control system according to any one of claims 1 to 6, comprising the steps of:
s1, respectively controlling a bucket rod closed pump control module (1) and a movable arm closed pump control module (2) according to four-quadrant characteristics of a load;
s2, respectively supplementing oil or returning oil to the bucket rod closed pump control module (1) and the movable arm closed pump control module (2) through a pressurizing oil tank (3);
and S3, when oil returns, the oil returns to the supercharged oil tank (3) through the filtering mechanism (4) and the cooling mechanism (5) in sequence.
8. The control method according to claim 7, wherein the hydraulic rod retraction direction of the first hydraulic pump (102) and the second hydraulic pump (202) is set to be a positive speed direction, and the hydraulic rod extension direction is set to be a positive direction in which the hydraulic cylinder is forced; the working process of the bucket rod closed pump control module (1) is as follows:
first quadrant operating mode: when the hydraulic rod of the bucket rod hydraulic cylinder (110) stretches out, the direction of the hydraulic rod is opposite to the load stress, and at the moment, the first hydraulic pump (102) is in a pumping mode; the high-pressure oil flows from an A oil port of the first hydraulic pump (102) to a rodless cavity of the bucket rod hydraulic cylinder (110), the low-pressure oil with the rod cavity flows back to a B oil port of the first hydraulic pump (102), at the moment, the pressure of the rodless cavity is larger than that of the rod cavity, the high-pressure oil with the rod cavity flows to a loop of the first one-way valve (107), the first one-way valve (107) is opened, and at the moment, the replenishing oil in the pressurizing oil tank (3) flows to the B oil port of the first hydraulic pump (102) through an eighth one-way valve (64), a first stop valve (109) and the first one-way valve (107);
second quadrant operating mode: the hydraulic rod of the bucket rod hydraulic cylinder (110) is in the same direction as the load stress when extending, and at the moment, the first hydraulic pump (102) is in a motor mode; when a load pulls a hydraulic rod of the first hydraulic pump (102) to extend, high-pressure oil with a rod cavity of the bucket rod hydraulic cylinder (110) flows to an oil port B of the first hydraulic pump (102), and low-pressure oil flows to a rod-free cavity of the bucket rod hydraulic cylinder (110) from an oil port A of the first hydraulic pump (102); at the moment, the pressure of the rod cavity is larger than that of the rodless cavity, high-pressure oil in the rod cavity flows to a loop of the second one-way valve (108), the second one-way valve (108) is opened, and the replenishing oil in the pressurized oil tank (3) flows to the rodless cavity of the bucket rod hydraulic cylinder (110) through the eighth one-way valve (64), the first stop valve (109) and the second one-way valve (108);
third quadrant operating mode: when the hydraulic rod of the bucket rod hydraulic cylinder (110) is retracted, the direction of the hydraulic rod is opposite to the load stress, and at the moment, the first hydraulic pump (102) is in a pumping mode; the high-pressure oil flows from the B oil port of the first hydraulic pump (102) to the rod cavity of the bucket rod hydraulic cylinder (110), the low-pressure oil of the rodless cavity flows to the A oil port of the first hydraulic pump (102), at the moment, the pressure of the rod cavity is higher than that of the rodless cavity, the high-pressure oil of the rod cavity flows to a loop of the second one-way valve (108), the second one-way valve (108) is opened, and the redundant hydraulic oil of the rodless cavity returns to the pressurizing oil tank (3) through the second one-way valve (108), the first stop valve (109), the fifth one-way valve (61), the filtering mechanism (4) and the cooling mechanism (5);
fourth quadrant operating mode: the hydraulic rod of the bucket rod hydraulic cylinder (110) is retracted in the same direction as the load bearing direction, and at the moment, the first hydraulic pump (102) is in a motor mode; the hydraulic oil with the high pressure of the rodless cavity of the bucket rod hydraulic cylinder (110) flows to the A oil port of the first hydraulic pump (102), the hydraulic oil with the low pressure flows to the rod cavity of the bucket rod hydraulic cylinder (110) from the B oil port of the first hydraulic pump (102), at the moment, the pressure of the rodless cavity is larger than that of the rod cavity, the high pressure of the rodless cavity flows to a loop of the first check valve (107), the first check valve (107) is opened, and the redundant hydraulic oil with the rod cavity flows to the loop of the first check valve (107), the first check valve (109), the fifth check valve (61), the filtering mechanism (4) and the cooling mechanism (5) to return to the pressurizing oil tank (3).
9. The control method according to claim 8, characterized in that the working process of the boom closed pump control module (2) is:
first quadrant operating mode: when the hydraulic rod of the movable arm hydraulic cylinder (210) stretches out, the direction of the load stress is opposite, and at the moment, the second hydraulic pump (202) is in a pumping mode; high-pressure oil flows from an A oil port of the second hydraulic pump (202) to a rodless cavity of the movable arm hydraulic cylinder (210), low-pressure oil with a rod cavity flows back to a B oil port of the second hydraulic pump (202), at the moment, the pressure of the rodless cavity is higher than that of the rod cavity, the high-pressure oil with the rodless cavity flows to a loop of the third one-way valve (207), the third one-way valve (207) is opened, and at the moment, the replenishing oil in the pressurizing oil tank (3) flows to the B oil port of the second hydraulic pump (202) through a seventh one-way valve (63), a second stop valve (209) and the third one-way valve (207);
fourth quadrant operating mode: the hydraulic rod of the movable arm hydraulic cylinder (210) is retracted in the same direction as the load bearing direction, and at the moment, the second hydraulic pump (202) is in a motor mode; the high-pressure oil of the rodless cavity of the movable arm hydraulic cylinder (210) flows to the A oil port of the second hydraulic pump (202), the low-pressure oil flows to the rod cavity of the movable arm hydraulic cylinder (210) from the B oil port of the second hydraulic pump (202), at the moment, the pressure of the rodless cavity is larger than that of the rod cavity, the high-pressure oil of the rodless cavity flows to a loop of the third one-way valve (207), the third one-way valve (207) is opened, and the redundant hydraulic oil in the rod cavity flows to the booster oil tank (3) through the third one-way valve (207), the second stop valve (209), the sixth one-way valve (62), the filtering mechanism (4) and the cooling mechanism (5).
CN202310356341.1A 2023-04-06 2023-04-06 Distributed closed pump control system and control method thereof Pending CN116379025A (en)

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