LU503234B1 - Mechanical boom potential energy recovery and reuse system - Google Patents

Mechanical boom potential energy recovery and reuse system Download PDF

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Publication number
LU503234B1
LU503234B1 LU503234A LU503234A LU503234B1 LU 503234 B1 LU503234 B1 LU 503234B1 LU 503234 A LU503234 A LU 503234A LU 503234 A LU503234 A LU 503234A LU 503234 B1 LU503234 B1 LU 503234B1
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LU
Luxembourg
Prior art keywords
port
oil
reversing valve
motor
hydraulic pump
Prior art date
Application number
LU503234A
Other languages
French (fr)
Inventor
Jiansong Li
Original Assignee
Xuzhou College Ind Technology
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Priority to LU503234A priority Critical patent/LU503234B1/en
Application granted granted Critical
Publication of LU503234B1 publication Critical patent/LU503234B1/en

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Classifications

    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2217—Hydraulic or pneumatic drives with energy recovery arrangements, e.g. using accumulators, flywheels
    • 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
    • F15B21/14—Energy-recuperation means
    • 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
    • E02F3/36—Component parts
    • E02F3/42—Drives for dippers, buckets, dipper-arms or bucket-arms
    • E02F3/43—Control of dipper or bucket position; Control of sequence of drive operations
    • E02F3/435—Control of dipper or bucket position; Control of sequence of drive operations for dipper-arms, backhoes or the like
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20561—Type of pump reversible
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20569—Type of pump capable of working as pump and motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/41—Flow control characterised by the positions of the valve element
    • F15B2211/411—Flow control characterised by the positions of the valve element the positions being discrete
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41572—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and an output member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41581—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/426—Flow control characterised by the type of actuation electrically or electronically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves
    • 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
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5157—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and a return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/61—Secondary circuits
    • F15B2211/611—Diverting circuits, e.g. for cooling or 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6306—Electronic controllers using input signals representing a pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6306—Electronic controllers using input signals representing a pressure
    • F15B2211/6309—Electronic controllers using input signals representing a pressure the pressure being a pressure source supply pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6306—Electronic controllers using input signals representing a pressure
    • F15B2211/6313—Electronic controllers using input signals representing a pressure the pressure being a load pressure
    • 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
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/88—Control measures for saving energy

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

Abstract

Potential energy recovery system, where the A and B ports of the reversing valve are respectively connected with the cavity oil ports A and B of the hydraulic cylinder; the A port and the port P of the hydraulic pump are respectively connected with the oil tank and the A port of the reversing valve; the P port of the reversing valve is simultaneously connected with the cavity oil port A and the A port of the reversing valve; the oil inlet A and the oil outlet B of the second check valve are respectively connected with the oil tank and the P port of the hydraulic pump; the output shaft of the hydraulic pump is connected with the spring device; the oil inlet A and the oil outlet B of the oil replenishing check valve are respectively connected with the oil tank and with the cavity oil port B.

Description

DESCRIPTION LU503234
MECHANICAL BOOM POTENTIAL ENERGY RECOVERY AND REUSE
SYSTEM
TECHNICAL FIELD
The invention belongs to the technical field of hydraulic control, and in particular to a mechanical boom potential energy recovery and reuse system.
BACKGROUND
The excavator, as a kind of large-scale engineering machinery, its boom has great quality. At the same time, in the operation process of excavator, its boom moves up and down frequently, and the working device and load mass are usually great, so the boom will release a lot of potential energy in the falling process. Most of this energy is consumed at the throttle of the main hydraulic valve and converted into heat energy, which not only causes energy waste and system heating, but also easily reduces the service life of hydraulic components. Therefore, how to recovery the potential energy of the boom and realize the reuse of the recovered energy is of great significance for prolonging the service life of the hydraulic system and realizing the energy saving of the hydraulic system.
At present, the excavator boom potential energy recovery methods mainly include electric type and hydraulic type. Electric power mainly adopts the hydraulic motor and the generator as energy conversion elements, the storage battery and the super-capacitor as energy storage elements to realize energy conversion and recovery. However, the boom falls in a very short time, and usually the energy released in a few seconds is large, so the power is very large. The battery of the prior art cannot bear such a large charging power. However, super-capacitors are extremely expensive and occupy a large space, so the utility of electric type recovery method is not strong. Hydraulic energy recovery system takes the energy accumulator as the energy storage element. Its working principle is that when the gravitational potential energy of the system is recovered, it is stored in the hydraulic accumulator in the form of pressure energy of high-pressure oil. When energy is needed in the system, the stored oil is released to work in the hydraulic system. Hydraulic type recovery scheme makes use of the advantages of the energy accumulator, such as high power density and pressure shock absorption. However, the energy storage density of the energy accumulator is low, if MOf 503234 energy needs to be stored, a larger volume of the energy accumulator is needed, so that a larger space is occupied, and the installation of the energy accumulator is very inconvenient. In addition, the pressure in the accumulator will increase as the stored oil increases, which will affect the falling speed of the boom. In order to overcome the shortcomings of traditional energy storage components, research and development are needed.
SUMMARY
Aiming at the above problems existing in the prior art, the present invention provides a mechanical boom potential energy recovery and reuse system. The system adopts the spring as the energy storage element, which has strong practicability, small overall occupied space, and convenient installation process. In addition, in the process of lowering the boom, the potential energy of the boom can be converted into the potential energy of the spring and stored, thus avoiding the phenomenon of energy waste and temperature rise of hydraulic components caused by the conversion of boom potential energy into oil heat energy; in addition, when the boom needs to be lifted, the potential energy of the spring can be converted into the pressure of oil, which can assist the lifting action of the boom and reduce the power demand of the prime mover.
This system has a remarkable energy-saving effect.
In order to achieve the above purpose, the present invention provides a mechanical boom potential energy recovery and reuse system, which includes an oil source, a main reversing valve, a hydraulic cylinder, a hydraulic pump/motor, a first reversing valve, a second check valve, a first pressure sensor, a second pressure sensor, a controller, a spring device, an oil replenishing check valve and a braking device;
The oil source is connected with the P port of the main reversing valve through the first check valve, the A port of the main reversing valve is connected with the rodless cavity oil port A of the hydraulic cylinder through pipelines, and the B port of the main reversing valve is connected with the rod cavity oil port B of the hydraulic cylinder through pipelines respectively; the T port of the main reversing valve is connected with the oil tank through pipelines;
The A port of the hydraulic pump/motor is connected with the oil tank through pipelines, and the port P of the hydraulic pump/motor is connected with the A port of the first reversing valve; the P port of the first reversing valve is simultaneously connected with the rodless cavity oil port A of the hydraulic cylinder and the A port of the main reversing valve; LU503234
The oil inlet A of the second check valve is connected with the oil tank through pipelines, and the oil outlet B of the second check valve is connected with the P port of the hydraulic pump/motor through pipelines;
The first pressure sensor is connected to the rodless cavity oil port À of the hydraulic cylinder, and is used for collecting the pressure signal in the rodless cavity of the hydraulic cylinder in real time;
The second pressure sensor is connected to the P port of the hydraulic pump/motor, and 1s used for collecting the pressure signal of the P port of the hydraulic pump/motor in real time;
The spring device consists of an outer shell fixedly connected with the excavator, a scrollable scroll spring arranged inside the outer shell, and a revolvable transmission shaft arranged in the center of the outer shell and connected with the scroll spring at the inner end;
The output shaft of the hydraulic pump/motor is connected with the transmission shaft of the rotation center of the spring device through a clutch;
The oil inlet À of the oil replenishing check valve is connected with the oil tank through pipelines, and the oil outlet B of the oil replenishing check valve is connected with the rod cavity oil port B of the hydraulic cylinder;
The braking device is arranged on the transmission shaft and used for braking or releasing the spring device in cooperation with the transmission shaft;
The controller 1s respectively connected with the main reversing valve, the first reversing valve, the hydraulic pump/motor, the clutch, the first pressure sensor, the second pressure sensor and the braking device.
Further, in order to ensure that the pressure of the P port of the hydraulic pump/motor is within a certain range, an overflow valve is further included. The T port of the overflow valve is connected with the oil tank through pipelines, and the P port of the overflow valve is connected with the P port of the hydraulic pump/motor through pipelines. The pressure of the overflow valve is higher than the highest working pressure of the oil source.
As a preference, the controller is a PLC controller.
As a preference, the first reversing valve is a two-position two-way solenoid directional valve, which works in the left position after being powered off, and works in the right position after being powered on. When working in the left position, the oil path between its port P and port A is disconnected, and when working in the right position, the oil path between its port P,50323 4 and port A is communicated.
As a preference, the main reversing valve is a three-position four-way solenoid directional valve. Its electromagnet Y 1b works in the left position after being powered on, its electromagnet
Y la works in the right position after being powered on, and its electromagnet Y la works in the middle position when being powered off. When working in the left position, the oil path between its port P and port A is connected, and the oil path between its port T and port B is communicated; when working in the right position, the oil path between port P and port B is connected, and the oil path between port T and port A is communicated, when working in the middle position, its port P, port A, port T and port B are not communicated with each other.
Further, in order to change the transmission ratio conveniently, a transmission is also connected between the hydraulic pump/motor and the clutch, and the transmission is connected with the controller.
In the invention, by setting the hydraulic pump/motor, connecting the rodless cavity of the hydraulic cylinder and the P port of the hydraulic pump/motor through the first reversing valve, and connecting the hydraulic pump/motor with the spring device through the clutch, the first reversing valve can be controlled to obtain electricity in the boom falling process, and then the energy of oil can be converted and stored in the spring device by the hydraulic pump/motor, thus effectively avoiding the energy waste in the boom falling process. Meanwhile, when the boom is lifted, the energy stored in the spring device can be used to drive the boom to lift. This scheme not only avoids the energy waste in the boom falling process, but also feeds the stored energy back to the hydraulic system again, so that when the boom needs to be lifted, the spring drives the hydraulic pump/motor to make the stored potential energy supplement to the hydraulic system in the form of pressure energy, thus meeting the requirements of the boom lifting process.
By arranging the braking device and the clutch, and connecting them with the controller, the actions of the braking device and the clutch can be more conveniently controlled in the charging and discharging process, and then the charging or discharging process can be accurately controlled. The system is simple in structure, easy to implement, and can reduce the power demand of the prime mover. At the same time, it can control the process of energy conversion or reuse more conveniently and efficiently, and has remarkable energy-saving effect.
BRIEF DESCRIPTION OF THE FIGURES LU503234
FIG. 1 is an assembly schematic diagram of the common engineering machinery boom and the hydraulic cylinder;
FIG. 2 is a hydraulic schematic diagram of the present invention;
FIG. 3 is a structural schematic diagram of a spring device involved in the present invention;
FIG. 4 is a simplified schematic diagram when the boom is lowered only under the control of the main reversing valve involved in the present invention;
FIG. 5 is a simplified schematic diagram when the hydraulic pump/motor performs energy recovery in the present invention;
FIG. 6 is a simplified schematic diagram when the boom involved in the present invention performs lifting movement only under the control of the main reversing valve;
FIG. 7 is a simplified schematic diagram of the boom involved in the present invention performs lifting movement under the joint action of the main reversing valve and the hydraulic pump/motor.
In figures: 1 oil source, 2 first check valve, 3. main reversing valve, 4 hydraulic cylinder, 5. oil tank, 6 hydraulic pump/motor, 7 first reversing valve, 8 spring device, 9.clutch, 10.overflow valve, 11. second check valve, 12. first pressure sensor, 13. second pressure sensor, 14 braking device, 18. transmission, 19. oil replenishing check valve, 81. transmission shaft, 82. scroll spring, 100. boom, 200. turntable.
DESCRIPTION OF THE INVENTION
The present invention will be further explained below.
FIG. 1 is an assembly schematic diagram of the common engineering machinery boom 100 and the hydraulic cylinder 4, where the end of the boom 100 is hinged to a turntable 200, the base of the hydraulic cylinder 4 is hinged to the turntable 200, and the piston rod end of the hydraulic cylinder 4 is hinged to the middle of the boom 100.
As shown in FIG. 2 - FIG. 7, the present invention provides a mechanical boom potential energy recovery and reuse system, which includes an oil source 1, a main reversing valve 3, a hydraulic cylinder 4, a hydraulic pump/motor 6, a first reversing valve 7, a second check valve 11, a first pressure sensor 12, a second pressure sensor 13, a controller, a spring device 8, an oil replenishing check valve 19 and a brake device 14; LU503234
The oil source 1 provides hydraulic energy for the hydraulic system, generally consisting of the hydraulic pump and the prime mover (motor, engine, etc.). The oil source 1 is connected with the P port of the main reversing valve 3 through the first check valve 2, the A port of the main reversing valve 3 is connected with the rodless cavity oil port A of the hydraulic cylinder 4 through pipelines, and the B port of the main reversing valve 3 is connected with the rod cavity oil port B of the hydraulic cylinder 4 through pipelines respectively; the T port of the main reversing valve 3 is connected with the oil tank 5 through pipelines;
As an energy conversion element, the hydraulic pump/motor 6 can work in the hydraulic pump condition or motor condition according to the working condition. Under the condition that the rotation direction of its transmission shaft is certain, the oil inlet and oil outlet directions of the two oil ports can be changed by adjusting the angle of the swash plate. Its displacement can be adjusted by the electric signal output by a controller (not shown in the figure). Without the control signal input, the displacement of the hydraulic pump/motor 6 is zero. The A port of the hydraulic pump/motor 6 is connected with the oil tank 5 through pipelines, and the port P of the hydraulic pump/motor 6 is connected with the A port of the first reversing valve 7; the P port of the first reversing valve 7 is simultaneously connected with the rodless cavity oil port A of the hydraulic cylinder 4 and the A port of the main reversing valve 3; the first check valve 2 ensures the unidirectional flow of oil to the main reversing valve 3, and prevents the flow of oil in the reverse direction. The hydraulic cylinder 4 is used as the actuating mechanism, which controls the boom of the excavator to move down and up through the telescopic movement of its piston rod. The oil tank 5 provides a storage space for the oil of the system.
The oil inlet A of the second check valve 11 is connected with the oil tank 5 through pipelines, and its oil outlet B is connected with the P port of the hydraulic pump/motor 6 through pipelines; the second check valve 11 serves as an oil replenishing valve. For any possible reason, when the P port pressure of the hydraulic pump/motor 6 is lower than the pressure of the oil tank 5, the oil in the oil tank 5 enters the P port of the hydraulic pump/motor 6 through the second check valve 11 to prevent air suction and cavitation.
The first pressure sensor 12 is connected to the rodless cavity oil port A of the hydraulic cylinder 4, and is used for collecting the pressure signal in the rodless cavity of the hydraulic cylinder 4 in real time and sending it to the controller in real time;
The second pressure sensor 13 is connected to the P port of the hydraulic pump/motor Pus0323 4 and is used for collecting the pressure signal of the P port of the hydraulic pump/motor 6 in real time, and sending it to the controller in real time;
The spring device 8 consists of an outer shell fixedly connected with the excavator, a scrollable scroll spring 82 arranged inside the outer shell, and a revolvable transmission shaft 81 arranged in the center of the outer shell and connected with the scroll spring 82 at the inner end; the transmission shaft 81 is used for energy transmission, and the scroll spring 82 is used as the energy storage element of the system, and when it is scrolled, it can absorb and store a certain amount of energy; on the contrary, it can release some energy.
The output shaft of the hydraulic pump/motor 6 is connected with the transmission shaft of the rotation center of the spring device 8 through a clutch 9; the clutch 9 can connect or disconnect the hydraulic pump/motor 6 and the spring device 8 according to the control signal of the controller 15.
The oil inlet A of the oil replenishing check valve 19 is connected with the oil tank 5 through pipelines, and its oil outlet B is connected with the rod cavity oil port B of the hydraulic cylinder 4;
The braking device 14 is arranged on the transmission shaft 81, and used for braking or releasing the spring device 8 in cooperation with the transmission shaft 81, so as to control whether the spring device 8 exchanges energy with the outside.
The controller is respectively connected with the main reversing valve 3, the first reversing valve 7, the hydraulic pump/motor 6, the clutch 9, the first pressure sensor 12, the second pressure sensor 13 and the braking device 14.
In order to ensure that the pressure of the P port of the hydraulic pump/motor is within a certain range, an overflow valve 10 is further included. The T port of the overflow valve 10 is connected with the oil tank 5 through pipelines, and its P port is connected with the P port of the hydraulic pump/motor 6 through pipelines. The pressure of the overflow valve 10 is higher than the highest working pressure of the oil source 1. When the P port pressure of the hydraulic pump/motor 6 reaches the set value of the overflow valve 10, the overflow valve 10 connects the
P port of the hydraulic pump/motor 6 with the oil tank 5 to ensure that the P port pressure is within a certain range.
The controller is a PLC controller. As a preference, it also includes an operating handle, the operating handle connected with the controller and used to send a control signal to the processor 503234 according to the control of the operator,
As a preference, the first reversing valve 7 1s a two-position two-way solenoid directional valve, which works in the left position after being powered off, and works in the right position after being powered on. When working in the left position, the oil path between its port P and port À is disconnected, and when working in the right position, the oil path between its port P and port À is communicated. When the flow rate of the system 1s large, the first reversing valve 7 can be an electro-hydraulic directional control valve.
The main reversing valve 3 is an electromagnetic valve, which can control the flow direction of the oil through the energization of the electromagnet, so as to control the telescopic movement of the hydraulic cylinder. As a preference, the main reversing valve 3 is a three-position four-way solenoid directional valve. Its electromagnet Y1b works in the left position after being powered on, its electromagnet Yla works in the right position after being powered on, and its electromagnet Yla works in the middle position when being powered off.
When working in the left position, the oil path between its port P and port A is connected, and the oil path between its port T and port B is communicated; when working in the right position, the oil path between port P and port B is connected, and the oil path between port T and port À is communicated; when working in the middle position, its port P, port A, port T and port B are not communicated with each other.
In order to change the transmission ratio conveniently, a transmission is also connected between the hydraulic pump/motor 6 and the clutch 9, and the transmission is connected with the controller. The transmission can receive external control signals and adjust its transmission ratio.
By setting the hydraulic pump/motor, connecting the rodless cavity of the hydraulic cylinder and the P port of the hydraulic pump/motor through the first reversing valve, and connecting the hydraulic pump/motor with the spring device through the clutch, the first reversing valve can be controlled to obtain electricity in the boom falling process, and then the energy of oil can be converted and stored in the spring device by the hydraulic pump/motor, thus effectively avoiding the energy waste in the boom falling process. Meanwhile, when the boom is lifted, the energy stored in the spring device can be used to drive the boom to lift. This scheme not only avoids the energy waste in the boom falling process, but also feeds the stored energy back to the hydraulic system again, so that when the boom needs to be lifted, the spring drives the hydraulic pump/motor to make the stored potential energy supplement to the hydraulie,50323 4 system in the form of pressure energy, thus meeting the requirements of the boom lifting process.
By arranging the braking device and the clutch, and connecting them with the controller, the actions of the braking device and the clutch can be more conveniently controlled in the charging and discharging process, and then the charging or discharging process can be accurately controlled. The system is simple in structure, easy to implement, and can reduce the power demand of the prime mover. At the same time, it can control the process of energy conversion or reuse more conveniently and efficiently, and has remarkable energy-saving effect.
Working principle:
The system has the following working states: 1. Conventional boom lowering:
It is assumed that the piston cylinder of the hydraulic cylinder 4 has been extended at this time. When the boom is lowered, the operator sends the boom lowering signal through the operating handle. When the controller receives the boom lowering signal, it controls the electromagnet Y 1a of the main reversing valve 3 to be energized, and its port P to port B, port A to port T are connected. The oil from the oil source 1 enters the rod cavity of the hydraulic cylinder 4 through the right positions of the first check valve 2 and the main reversing valve 3.
The oil in the rodless cavity of the hydraulic cylinder 4 flows back to the oil tank 5 through the right position of the main reversing valve 3. Therefore, the piston rod of the hydraulic cylinder 4 retracts and the boom falls. At this time, the flow rate of the system is completely controlled by the main reversing valve 3, and then the speed of the boom 100 is controlled, as shown in FIG. 4. 2. Energy recovery:
If the boom needs to be lowered, the operator sends out an energy recovery signal through the operating handle. When the controller receives the energy recovery signal, it controls the first reversing valve 7 to be energized, the clutch 9 to be engaged, the braking device 11 to be released, and the displacement of the hydraulic pump/motor 6 to be adjusted. At this time, the simplified system principle is shown in FIG, 5. The piston rod of hydraulic cylinder 5 retracts under the action of the gravity of the boom. The rodless cavity discharges oil, the rod cavity intakes oil. The oil discharged from the rodless cavity flows back to the oil tank through the hydraulic pump/motor 6. At this time, the hydraulic pump/motor 6 works in the hydraulic motor mode, and the output mechanical energy scroll s the scroll spring 82 through the transmission shaft 81, converting the hydraulic energy into the potential energy of the scroll spring 82. The 50323 4 larger the displacement of the hydraulic pump/motor 6, the more flow passes through, and the larger its driving torque, the more power it will recover. The oil in the oil tank 5 enters the rod cavity of the hydraulic cylinder 4 through the oil replenishing check valve 19 to prevent air suction.
When the boom 100 needs to stop moving, the operator sends out a boom stop signal through the operating handle. When the controller receives the boom stop signal, it controls the first reversing valve 7 to lose power. The hydraulic pump/motor 6 will continue to rotate for a period of time under its own inertia. At this time, it is the hydraulic pump condition, the oil in the oil tank 5 enters the P port of the hydraulic pump/motor 6 through the second check valve 11, and finally flows back to the oil tank 5. Because of its small inertia, the hydraulic pump/motor 6 will soon stop rotating. When the clutch 9 is disconnected, the braking device 11 brakes the transmission shaft 81, and the recovered energy is stored in the form of potential energy by the spring 82.
According to the need, the displacement of the hydraulic pump/motor 6 and the transmission ratio of the transmission 18 are controlled so that the spring 82 generates appropriate resistance to realize the recovery of the potential energy of the boom 100.
In the above process, the piston rod of the hydraulic cylinder 4 retracts, so the boom falls. 3. Boom lifting process:
With reference to FIG. 6, when the boom is lifted, the operator sends out a boom lifting signal through the operating handle. When the controller receives the boom lifting signal, it controls the electromagnet Ylb of the main reversing valve 3 to be energized, and the high-pressure oil of the oil source 1 enters the rodless cavity of the hydraulic cylinder 4 through the left position of the main reversing valve 3. The oil in the rod cavity of the hydraulic cylinder 4 flows back to the oil tank 5 through port B to port T of the main reversing valve 3. Therefore, the piston rod of the hydraulic cylinder 4 extends and the boom is lifted. At this time, the flow of the system, that is, the moving speed of the boom 100, is completely controlled by the main reversing valve 3. 4. Energy reuse process:
With reference to FIG. 7, at this time, it is necessary for the spring device 8 to release a part of energy and output it in the form of high-pressure oil, together with the high-pressure oil from the oil source 1, to push the hydraulic cylinder 4 to move. When the energy needs to be reuse, 50323 4 the operator sends the energy reuse signal through the operating handle, when the controller receives the energy reuse, controls the first reversing valve 7 to be energized, and the clutch 9 is engaged at the same time. The braking device 11 releases the transmission shaft 81 and connects it with the shaft of the hydraulic pump/motor 6. At this time, the hydraulic pump/motor 6 is driven by the spring 82 to rotate and work in the pump condition, the port A becomes the oil suction port and the port P becomes the high-pressure oil port. The oil discharged from the hydraulic pump/motor 6 passes through the right position of the first reversing valve 7 and enters the rodless cavity of the hydraulic cylinder 4, so that the piston rod of the hydraulic cylinder 4 extends out. In order to ensure that the running speed of the hydraulic cylinder 4 changes smoothly, the displacement of the hydraulic pump/motor 6 and the transmission ratio of the gearbox 18 need to be controlled as required. The oil in the rod cavity of hydraulic cylinder 4 passes through port B to port T through the left of main reversing valve 3, and is discharged back to oil tank 5.
In the above process, the piston rod of the hydraulic cylinder 4 is extended, so the boom is lifted.

Claims (6)

CLAIMS LU503234
1. A mechanical boom potential energy recovery and reuse system, characterized by comprising an oil source (1), a main reversing valve (3), a hydraulic cylinder (4), a hydraulic pump/motor (6), a first reversing valve (7), a second check valve (11), a first pressure sensor (12), a second pressure sensor (13) and a controller, the oil source (1) is connected with the P port of the main reversing valve (3) through the first check valve (2), the À port of the main reversing valve (3) is connected with the rodless cavity oil port A of the hydraulic cylinder (4) through pipelines, and the B port of the main reversing valve (3) is connected with the rod cavity oil port B of the hydraulic cylinder (4) through pipelines respectively; the T port of the main reversing valve (3) is connected with the oil tank (5) through pipelines; the A port of the hydraulic pump/motor (6) is connected with the oil tank (5) through pipelines, and the port P of the hydraulic pump/motor (6) is connected with the A port of the first reversing valve (7); the P port of the first reversing valve (7) is simultaneously connected with the rodless cavity oil port A of the hydraulic cylinder (4) and the A port of the main reversing valve (3); the oil inlet A of the second check valve (11) is connected with the oil tank (5) through pipelines, and its oil outlet B is connected with the P port of the hydraulic pump/motor (6) through pipelines; the first pressure sensor (12) is connected to the rodless cavity oil port A of the hydraulic cylinder (4), and is used for collecting the pressure signal in the rodless cavity of the hydraulic cylinder (4) in real time; the second pressure sensor (13) is connected to the P port of the hydraulic pump/motor (6), and is used for collecting the pressure signal of the P port of the hydraulic pump/motor (6) in real time; characterized by further comprising a spring device (8), an oil replenishing check valve (19) and a brake device (14); the spring device (8) consists of an outer shell fixedly connected with the excavator, a scrollable scroll spring (82) arranged inside the outer shell, and a revolvable transmission shaft (81) arranged in the center of the outer shell and connected with the scroll spring (82) at the inner end; the output shaft of the hydraulic pump/motor (6) is connected with the transmission shaft of the rotation center of the spring device (8) through a clutch (9); LU503234 the oil inlet A of the oil replenishing check valve (19) is connected with the oil tank (5) through pipelines, and its oil outlet B is connected with the rod cavity oil port B of the hydraulic cylinder (4); the braking device (14) is arranged on the transmission shaft (81), and used for braking or releasing the spring device (8) in cooperation with the transmission shaft (81); the controller is respectively connected with the main reversing valve (3), the first reversing valve (7), the hydraulic pump/motor (6), the clutch (9), the first pressure sensor (12), the second pressure sensor (13) and the braking device (14).
2. The mechanical boom potential energy recovery and reuse system according to claim 1, characterized by further comprising an overflow valve (10), the T port of the overflow valve (10) is connected with the oil tank (5) through pipelines, and its P port is connected with the P port of the hydraulic pump/motor (6) through pipelines; the pressure of the overflow valve (10) is higher than the highest working pressure of the oil source (1).
3. The mechanical boom potential energy recovery and reuse system according to claim 1 or 2, characterized in that the controller is a PLC controller.
4. The mechanical boom potential energy recovery and reuse system according to claim 1 or 2, characterized in that the first reversing valve (7) is a two-position two-way solenoid directional valve, which works in the left position after being powered off, and works in the right position after being powered on; when working in the left position, the oil path between its port P and port A is disconnected, and when working in the right position, the oil path between its port P and port A is communicated.
5. The mechanical boom potential energy recovery and reuse system according to claim 4, characterized in that the main reversing valve (3) is a three-position four-way solenoid directional valve; its electromagnet Y1b works in the left position after being powered on, its electromagnet Y 1a works in the right position after being powered on, and its electromagnet Y la works in the middle position when being powered off; when working in the left position, the oil path between its port P and port A is connected, and the oil path between its port T and port B is communicated; when working in the right position, the oil path between port P and port B is connected, and the oil path between port T and port A is communicated; when working in the middle position, its port P, port A, port T and port B are not communicated with each other.
6. The mechanical boom potential energy recovery and reuse system according to claim DU50323 4 characterized in that a transmission is also connected between the hydraulic pump/motor (6) and the clutch (9), and the transmission is connected with the controller; the transmission can receive external control signals and adjust its transmission ratio.
LU503234A 2022-12-21 2022-12-21 Mechanical boom potential energy recovery and reuse system LU503234B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
LU503234A LU503234B1 (en) 2022-12-21 2022-12-21 Mechanical boom potential energy recovery and reuse system

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
LU503234A LU503234B1 (en) 2022-12-21 2022-12-21 Mechanical boom potential energy recovery and reuse system

Publications (1)

Publication Number Publication Date
LU503234B1 true LU503234B1 (en) 2023-06-22

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Family Applications (1)

Application Number Title Priority Date Filing Date
LU503234A LU503234B1 (en) 2022-12-21 2022-12-21 Mechanical boom potential energy recovery and reuse system

Country Status (1)

Country Link
LU (1) LU503234B1 (en)

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Effective date: 20230622