CN112922773B - Potential energy recovery system and engineering equipment - Google Patents
Potential energy recovery system and engineering equipment Download PDFInfo
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- CN112922773B CN112922773B CN202110130583.XA CN202110130583A CN112922773B CN 112922773 B CN112922773 B CN 112922773B CN 202110130583 A CN202110130583 A CN 202110130583A CN 112922773 B CN112922773 B CN 112922773B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
- F03C1/00—Reciprocating-piston liquid engines
- F03C1/26—Reciprocating-piston liquid engines adapted for special use or combined with apparatus driven thereby
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/26—Control
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
- F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
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- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The application provides a potential energy recovery system and engineering equipment, and solves the problem that in the prior art, the response speed is low when the potential energy recovery system switches lifting and descending actions. A potential energy recovery system, comprising: the device comprises a storage battery, a first motor, a second motor, a pump, a motor, a reversing valve, a balance valve and a lifting oil cylinder. The first motor and the second motor are respectively and electrically connected with the storage battery, the first motor, the pump, the valve group and the lifting oil cylinder are sequentially connected, and the second motor, the valve group and the lifting oil cylinder are sequentially connected.
Description
Technical Field
The application relates to the technical field of engineering machinery, in particular to a potential energy recovery system and engineering equipment.
Background
The potential energy recovery system in the prior art generally utilizes a motor to switch the lifting and lowering actions by changing the rotation direction of the motor. However, the rotational inertia of the motor is large, so that the response speed is slow when the motion is switched, and the user experience satisfaction is affected.
Content of application
In view of this, the embodiment of the present application provides a potential energy recovery system and engineering equipment, so as to solve the problem that a response speed is slow when a potential energy recovery system switches between a lifting action and a lowering action in the prior art.
The present application provides in a first aspect a potential energy recovery system comprising: the device comprises a storage battery, a first motor, a second motor, a pump, a motor, a reversing valve, a balance valve and a lifting oil cylinder. The first motor and the second motor are respectively and electrically connected with the storage battery, the first motor, the pump, the reversing valve and the lifting oil cylinder are sequentially connected, and the second motor, the balance valve and the lifting oil cylinder are sequentially connected.
In one possible implementation, the pump comprises an electric proportional plunger pump, and the electric proportional plunger pump is connected with a rodless cavity of the lifting oil cylinder through a reversing valve. The potential energy recovery system further comprises a controller, wherein the controller is used for controlling the opening of the reversing valve according to the obtained ascending speed instruction, and controlling the flow of the electric proportional plunger pump to be matched with the opening according to the opening.
In one possible implementation, the reversing valve comprises an electrically proportional reversing valve; the controller is used for controlling the opening of the reversing valve according to the acquired ascending speed instruction and comprises the following steps: the controller is used for matching the flow corresponding to the ascending speed instruction according to the ascending speed instruction and outputting current matched with the flow to the electric proportional reversing valve so as to enable the electric proportional reversing valve to be switched to the opening degree.
In one possible implementation, the electro-proportional reversing valve is a three-position, four-way electro-proportional reversing valve.
In one possible implementation, the motor comprises an electric proportional piston motor, which is connected to the rodless cavity of the lift cylinder through a balancing valve. The controller is also used for controlling the balance valve to communicate the rodless cavity of the lifting oil cylinder with the electric proportional plunger motor according to the obtained descending speed instruction, and controlling the flow of the electric proportional plunger motor according to the descending speed instruction.
In one possible implementation, the balancing valve comprises a load holding valve.
In one possible implementation, the potential energy recovery system further comprises a control pump for pumping hydraulic oil in the oil tank out to an external control port of at least one of the electric proportional plunger pump and the electric proportional plunger motor.
In a possible realization mode, the oil outlet of the control pump is connected with the external control port of the electric proportional plunger motor through a one-way valve.
In a possible implementation manner, the hydraulic control system further comprises an oil tank, and at least one of the electric proportional reversing valve, the control pump, the electric proportional plunger motor and the electric proportional plunger pump is communicated with the oil tank.
In a second aspect, the present application provides an engineering plant comprising any one of the potential energy recovery systems described above.
According to the potential energy recovery system provided by the application, the first motor and the pump for ascending and the second motor and the motor for descending are independent, so that the problem that the response speed is low due to the fact that the rotating direction of the motors needs to be switched when ascending and descending actions are switched in the prior art is solved, and the response speed of action switching is improved.
Drawings
Fig. 1 is a schematic structural diagram of a potential energy recovery system according to an embodiment of the present application.
Fig. 2 is a schematic structural diagram of a potential energy recovery system according to another embodiment of the present application.
Figure 3 is an enlarged view of the electro-proportional piston pump of the potential energy recovery system of figure 2.
Fig. 4 is an enlarged view of the electro-proportional piston motor in the potential energy recovery system of fig. 2.
Detailed Description
The technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the drawings in the embodiments of the present application, and it is obvious that the described embodiments are only a part of the embodiments of the present application, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present application.
Fig. 1 is a schematic structural diagram of a potential energy recovery system according to an embodiment of the present application. As shown in fig. 1, the potential energy recovery system 10 includes a storage battery 1, a first electric machine 2, a second electric machine 3, a pump 4, a motor 5, a reversing valve 6, a balancing valve 8, and a lift cylinder 7. The first motor 2 and the second motor 3 are respectively and electrically connected with the storage battery 1, the first motor 2, the pump 4, the reversing valve 6 and the lifting oil cylinder 7 are sequentially connected, and the second motor 3, the motor 5, the balance valve 8 and the lifting oil cylinder 7 are sequentially connected.
The pump 4 may be any variable displacement pump, such as an electro-proportional plunger pump or the like. The motor 5 includes an electric proportional plunger motor or a pilot operated plunger motor, etc.
When the lifting oil cylinder 7 rises, the storage battery 1 supplies power to the first motor 2, the first motor 2 drives the pump 4 to pump out pressure oil, and the pressure oil enters a rodless cavity of the lifting oil cylinder 7 through the reversing valve 6 to enable the lifting oil cylinder 7 to rise. When the lifting oil cylinder 7 descends, pressure oil in a rodless cavity of the lifting oil cylinder 7 enters the motor 5 through the balance valve 8 to drive the motor 5 to rotate, the motor 5 drives the second electric machine 3 to rotate, and the second electric machine 3 converts mechanical energy into electric energy to be stored in the storage battery 1. According to the potential energy recovery system 10 provided by the embodiment, the first motor 2 for ascending, the pump 4, the second motor 3 for descending and the motor 5 are independent, so that the problem of low response speed caused by the need of switching the rotation directions of the motors during ascending and descending actions in the prior art is solved, and the response speed of action switching is improved.
Fig. 2 is a schematic structural diagram of a potential energy recovery system according to another embodiment of the present application. As shown in fig. 2, the potential energy recovery system 10 includes a storage battery 1, a first electric machine 2, a second electric machine 3, an electric proportional plunger pump 40, an electric proportional plunger motor 50, an electric proportional directional valve 61, a load holding valve 62, and a lift cylinder 7. The first motor 2 and the second motor 3 are respectively and electrically connected with the storage battery 1, the first motor 2, the electric proportional plunger pump 40, the electric proportional reversing valve 61 and the lifting oil cylinder 7 are sequentially connected, and the second motor 3, the electric proportional plunger motor 50, the load holding valve 62 and the lifting oil cylinder 7 are sequentially connected.
The electro-proportional reversing valve 40 may be a three-position, four-way electro-hydraulic proportional reversing valve. Taking a spring centering type three-position four-way electro-hydraulic proportional reversing valve as an example, the working principle of the valve comprises the following steps: when the proportional electromagnets at the left end and the right end of the pilot valve are not electrified, the valve core of the pilot valve is in a middle position under the action of the centering spring, at the moment, control pressure oil from the oil port P cannot enter control cavities at the left end and the right end of the main valve core, and oil in the control cavities at the left end and the right end of the main valve flows back to the oil tank through the oil port T of the pilot valve through the middle position of the pilot valve. And the main valve core is positioned at the middle position accurately by the valve body under the action of centering springs at two ends, and all oil ports of the main valve core are not communicated at the moment. When the proportional electromagnet on the right side of the pilot valve is electrified, the valve core moves leftwards, control pressure oil from an oil port P of the main valve core enters a control cavity at the left end of the main valve through the pilot valve to push the main valve core to move leftwards, and at the moment, oil in a control cavity at the right end of the main valve core flows back to an oil tank through the pilot valve, so that the oil port P of the main valve is communicated with oil passages of an oil port A, an oil port B and an oil port T. On the contrary, when the proportional electromagnet on the left side of the pilot valve is electrified, the oil port P is communicated with the oil passage of the oil port B, and the oil port A is communicated with the oil passage of the oil port T.
The load holding valve 62 comprises two working positions, one end of the load holding valve 62 is provided with an electromagnet, and the other end is provided with a return spring. When the electromagnet of the load holding valve 62 is energized, the load holding valve 62 is in the right position to connect the rodless chamber of the lift cylinder 7 with the electro-proportional plunger motor 50; when the solenoid of the load maintaining valve 62 is de-energized, the load maintaining valve 62 is in the left position to maintain the pressure of the oil in the rodless chamber of the lift cylinder 7.
In one embodiment, the potential energy recovery system 10 further comprises a control pump 9, the control pump 9 being configured to pump hydraulic oil in the tank out to an external control port of at least one of the electric proportional plunger pump 40 and the electric proportional plunger motor 50. In this case, at least one of the electric proportional plunger pump 40 and the electric proportional plunger motor 50 is supplied with oil by pressure, and is more stable than the self-oil-suction method.
The working process of the potential energy recovery system 10 comprises:
in standby mode, the electro-proportional plunger pump 40 is in a zero displacement operating state, the electro-proportional directional valve 61 is in a neutral position, the load holding valve 62 is in a left position, and the electro-proportional plunger motor 50 is in a zero displacement operating state.
When the lifting oil cylinder 7 rises, the storage battery 1 supplies power to the first motor 2, and the first motor 2 drives the electric proportional plunger pump 40 to rotate. The controller controls the opening degree of the electric proportional reversing valve 61 according to the obtained ascending speed instruction, and controls the flow rate of the electric proportional plunger pump 40 to be matched with the opening degree according to the opening degree of the electric proportional reversing valve 61. The hydraulic oil output by the electric proportional plunger pump 40 flows into the rodless cavity of the lift cylinder 7 through the electric proportional directional valve 61 to realize the lifting action of the lift cylinder 7.
Specifically, when the controller receives an ascending speed command input by an operator, the controller matches a flow rate corresponding to the ascending speed command, and outputs a current matching the flow rate to the electro-proportional directional valve 61, so that the electro-proportional directional valve 61 is switched to a corresponding opening degree. Meanwhile, the electro-proportional plunger pump 40 is controlled to operate in a positive displacement operation state. Since the flow rate output by the electrically proportional plunger pump 40 is equal to the product of the displacement volume thereof and the motor rotation speed, the controller synchronously controls the rotation speed of the first motor 2 and the displacement volume of the electrically proportional plunger pump 40 so that the product of the rotation speed of the first motor 2 and the displacement volume of the electrically proportional plunger pump 40 is equal to the flow rate corresponding to the rising speed command. The electric proportional plunger pump 40 is matched with the electric proportional reversing valve 61 to realize the lifting action of the lifting oil cylinder 7, and the flow of the electric proportional plunger pump 40 can be accurately adjusted according to the opening of the electric proportional reversing valve 61, so that the pressure loss of hydraulic oil is reduced.
When the lifting oil cylinder 7 is kept at the preset lifting position, the electric proportional plunger pump 40 is in a zero displacement working state, the electric proportional reversing valve 61 is in a middle position, the load keeping valve 62 is in a left position, and the electric proportional plunger motor 50 is in a zero displacement working state.
When the lifting oil cylinder 7 descends, the electric proportional plunger pump 40 is in a zero-displacement working state, and the electric proportional reversing valve 61 is in a neutral position. The controller controls the load holding valve 62 to switch to the right position according to the acquired descending speed instruction, so as to communicate the rodless cavity of the lift cylinder 7 with the electric proportional plunger motor 50. The hydraulic oil in the lift cylinder 7 flows into the electric proportional plunger motor 50 through the load hold valve 62 to drive the electric proportional plunger motor 50 to rotate. The controller is also used to control the flow of the electro-proportional plunger motor 50 according to the descent speed command. The electric proportional plunger motor 50 generates electricity and stores it in the battery 1.
Specifically, when the controller receives a lowering speed command input by the operator, the controller energizes the load holding valve 62 according to the lowering speed command, and switches the load holding valve 62 to the right position. Meanwhile, the controller matches the flow rate corresponding to the falling speed command, and synchronously controls the rotation speed of the second electric machine 3 and the displacement volume of the electro-proportional plunger motor 50 so that the product of the rotation speed of the second electric machine 3 and the displacement volume of the electro-proportional plunger motor 50 is equal to the flow rate corresponding to the falling speed command. The gravitational potential energy recovery is realized by adopting the electric proportional plunger motor 50, so that better micro-motion performance and quick response performance can be obtained.
Figure 3 is an enlarged view of the electro-proportional piston pump of the potential energy recovery system of figure 2. As shown in fig. 3, the electro-proportional plunger pump 40 includes a first variable plunger pump 41 and a first integrated control system for controlling the first variable plunger pump 41. The first variable displacement piston pump 41 includes a first swash plate 411, the first swash plate 411 is mounted inside the first variable displacement piston pump 41, an inclination angle thereof determines a displacement amount of the first variable displacement piston pump 41, and the first variable displacement piston pump 41 has an oil inlet and an oil outlet. The first integrated control system includes a first connecting rod 421, a second connecting rod 422, a first variable cylinder 423, a second variable cylinder 424, an integrated control assembly, and a control oil passage 426. The first link 421 and the second link 422 are respectively hinged to both ends of the first swash plate 411. The first link 421 is connected to the first variable cylinder 423 as a piston of the first variable cylinder 423, and the second link 422 is connected to the second variable cylinder 424 as a piston of the second variable cylinder 424. Under the differential action of the first variable cylinder 423 and the second variable cylinder 424, the inclination angle of the first swash plate 311 is changed, thereby changing the displacement volume of the first variable displacement piston pump 41. The first variable cylinder 423 always opens the high-pressure oil at the oil outlet of the first variable displacement plunger pump 41 or the control oil at the external control port. The first integrated control assembly is connected with the first variable cylinder 423 and the oil outlet of the first variable plunger pump 41 through a control oil path 426, and the first integrated control assembly is connected with the first connecting rod 421. The second variable cylinder 424 is connected with the first integrated control assembly through a control oil path 426. The first integrated control assembly is also connected with an oil return way.
The first integrated control assembly includes a valve body and first electric proportional control valve 4251, hydraulic control valve 4252 and first pressure cutoff control valve 4253, and first feedback rod 4254, which are located in the valve body. One end of the first feedback rod 4254 is inserted into the valve body and connected to the electric proportional control valve 4251, and the other end is connected to the first link 421. The first feedback rod 4254 moves under the driving of the first connecting rod 421, and the first connecting rod 421 senses the displacement change of the first variable displacement plunger pump 41 in real time. An end of the first electro-proportional control valve 4251 remote from the first feedback rod 4254 is mounted with a proportional solenoid, and an end of the first electro-proportional control valve 4251 facing the first feedback rod 4254 is connected with the first feedback rod 4254 through a feedback spring, and at the same time, the first electro-proportional control valve 4251 has an electro-proportional control adjusting spring. The oil return passage is connected to the first electric proportional control valve 4251. The hydraulic control valve 4252 is disposed in parallel with the first electro-proportional control valve 4251, and movement of the first feedback rod 4254 toward the first electro-proportional control valve 4251 pushes the hydraulic control valve 4252, thereby changing the state of the hydraulic control valve 4252. The first pressure cutoff control valve 4253 has an adjustment spring, and the opening pressure of the first pressure cutoff control valve 4253 can be set by adjusting the adjustment spring of the first pressure cutoff control valve 4253. When the pressure at the oil outlet a of the first variable displacement plunger pump 41 reaches the opening pressure, the first pressure cutoff control valve 4253 opens, and the first variable displacement plunger pump 41 is in the zero displacement operating state.
A second end of the first electro-proportional control valve 4251 is connected to an oil outlet of the first variable displacement piston pump 41 through an oil passage, and a first end of the first electro-proportional control valve 4251 is connected to a second end of the first pressure cutoff control valve 4253 through an oil passage. The second end of the first pressure cut-off control valve 4253 is also connected with the oil outlet of the first variable displacement plunger pump 41 through an oil path, the outer control port of the first pressure cut-off control valve 4253 is connected with the oil outlet of the first variable displacement plunger pump 41 through an oil path, and the first end of the first pressure cut-off control valve 4253 is connected with the second end of the hydraulic control valve 4252 through an oil path. A second end of the hydraulic control valve 4252 is connected to an oil outlet of the first variable displacement plunger pump 41 through an oil passage, and a second end of the hydraulic control valve 4252 is connected to the second variable displacement cylinder 424 through a control oil passage 426. The first electro-proportional control valve 4251, the first pressure cutoff control valve 4253, and the hydraulic control valve 4252 each have a left position and a right position. The first electro-proportional control valve 4251, the first pressure cutoff control valve 4253, and the hydraulic control valve 4252 may change the communication state of the respective first and second end oil passages by switching the left and right positions. By changing the left and right position combination of the first electric proportional control valve 4251, the first pressure cut-off control valve 4253 and the hydraulic control valve 4252, the flow direction of an oil path in the integrated control assembly can be changed, and displacement control and cut-off control functions are realized.
In order to more clearly illustrate the displacement adjustment process of the electro-proportional piston pump 40, it is described below in different cases from different operating states. The minimum displacement of the first variable displacement piston pump 41 is set to Y, and the corresponding control current is set to X. The acting force of the feedback spring on the right side of the first electric proportional control valve 4251 is Fs, the acting force of the electric proportional control adjusting spring is Ft, the thrust of the proportional electromagnet on the left side is F, and the directions of Fs and Ft are opposite to the direction of F. When the control current is X, the thrust of the proportional electromagnet 221 is Fx, and Fx = Fs + Ft.
In order to realize that the displacement of the first variable displacement plunger pump 41 is the set minimum flow Y, the control input current is less than or equal to X, the thrust F of the proportional electromagnet is less than the resultant force of Fs and Ft, the first electric proportional control valve 4251 is in the right position, and the hydraulic control valve 4252 is in the right position; high-pressure oil at the oil outlet of the first variable displacement plunger pump 41 or control oil at an external control port flows into the second variable displacement cylinder 424 through the first integrated control assembly and the control oil path 426; under the differential action of the second variable cylinder 424 and the first variable cylinder 423, the first swash plate 411 rotates clockwise, the displacement of the first variable displacement piston pump 41 is reduced, the first connecting rod 421 drives the first feedback rod 4254 to push the hydraulic control valve 4252, so that the hydraulic control valve 4252 is switched to the left position, the oil flowing to the second variable cylinder 424 is intercepted by the hydraulic control valve 4252, and the displacement of the first variable displacement piston pump 41 is at the set minimum flow Y; since the oil flowing to the second variable cylinder 424 is intercepted by the hydraulic control valve 4252, the second variable cylinder 424 is unloaded, the first swash plate 411 rotates counterclockwise under the differential action of the first variable cylinder 423 and the second variable cylinder 424, the displacement of the first variable displacement piston pump 41 is increased, the first connecting rod 421 drives the first feedback rod 4254 to move away from the hydraulic control valve 4252, the hydraulic control valve 4252 returns to the right position, the oil enters the second variable cylinder 424 again, and the displacement of the first variable displacement piston pump 41 is reduced. The above-described process is repeated to realize that the first variable displacement plunger pump 41 maintains the minimum set displacement Y under the control of the hydraulic control valve 4252.
In the case of a failure of the proportional solenoid or a failure of the current input device of the host system, the thrust F of the proportional solenoid is 0, and the first variable displacement plunger pump 41 can be controlled to maintain the minimum displacement by the hydraulic control valve 4252. Since the minimum set displacement is set by adjusting the hydraulic control valve 4252, it can be set according to the minimum displacement required for the operation of the main machine. When the proportional electromagnet suddenly fails, the displacement of the first variable displacement plunger pump 41 will not decrease to 0, but will be maintained at the minimum set displacement Y, and the main machine will still work, effectively improving the safety.
To achieve the electric proportional positive displacement control of the first variable displacement plunger pump 41, the control current X1 is set, X1 being greater than X. When the control current is X1, the thrust Fx1 of the proportional electromagnet is greater than the resultant force of Fs and Ft, the proportional electromagnet pushes the first electric proportional control valve 4251 to be in the left position, and oil in the second variable cylinder 424 flows back to achieve unloading; under the differential action of the second variable cylinder 424 and the first variable cylinder 423, the displacement of the variable displacement piston pump 41 is increased, the first connecting rod 421 drives the first feedback rod 4254 to push the first electric proportional control valve 4251, and the feedback spring is compressed, so that Fs is gradually increased until the resultant force of Fs and Ft is greater than Fx1, and the first electric proportional control valve 4251 is pushed to be switched to the right position; the oil flows into the second variable cylinder 424, the displacement of the first variable plunger pump 41 is reduced under the differential action of the second variable cylinder 424 and the first variable cylinder 423, the first connecting rod 421 drives the first feedback rod 4254 to move in the reverse direction away from the first electric proportional control valve 4251, the compression on the feedback spring is released, fs is gradually reduced until the resultant force of Fs and Ft is smaller than Fx1, and the proportional electromagnet pushes the first electric proportional control valve 4251 to return to the left position. The above processes are performed in a reciprocating manner, so that the displacement dynamic balance control of the first variable displacement plunger pump 41 under the control current X1 is realized, namely, the electric proportional positive displacement control is realized.
In order to realize the pressure cutoff control of the first variable displacement plunger pump 41, the opening pressure of the first pressure cutoff control valve 4253 is set by adjusting the adjustment spring of the first pressure cutoff control valve 4253. When the pressure at the oil outlet of the first variable displacement piston pump 41 reaches the opening pressure, the hydraulic pressure received by the first pressure cut-off control valve 4253 is greater than the acting force of the adjusting spring, the first pressure cut-off control valve 4253 is switched from the right position to the left position, the high-pressure oil at the oil outlet of the first variable displacement piston pump 41 enters the second variable displacement cylinder 424 through the first pressure cut-off control valve 4253 and the hydraulic control valve 4252, and the first variable displacement piston pump 41 is variable to the zero displacement under the differential action of the second variable displacement cylinder 424 and the first variable displacement cylinder 423, so that the pressure cut-off control is realized.
Figure 4 is an enlarged view of the electro-proportional plunger motor in the potential energy recovery system of figure 2. As shown in fig. 4, the electric proportional plunger motor 50 includes a second variable plunger pump 51 and a second integrated control system for controlling the second variable plunger pump 51. The second variable displacement piston pump 51 includes a second swash plate 511. The second integrated control system includes a third link 521, a third variable cylinder 522, and a second integrated control assembly. The third connecting rod 521 is connected to the third variable cylinder 522 as a piston of the third variable cylinder 522, and one end of the third connecting rod 521 remote from the third variable cylinder 522 is connected to the second swash plate 511. The rod chamber of the third variable cylinder 522 is normally open to the external control port of the second variable displacement piston pump 51 and the rodless chamber of the third variable cylinder 522 is connected to the oil tank through a second integrated control assembly.
Specifically, the second integrated control assembly includes a second feedback rod 5231, a second electro-proportional control valve 5232 and a second pressure cutoff control valve 5233. One end of the second feedback rod 5231 is connected to the third link 521, and the other end of the second feedback rod 5231 is connected to the second electro-proportional control valve 5232 through a feedback spring. A first end of the second electro-proportional control valve 5232 is connected to an oil outlet of the second variable displacement plunger pump 51 through an oil passage, and a second end of the second electro-proportional control valve 5232 is connected to a first end of the second pressure cutoff control valve 5233 through an oil passage. A second end of the second pressure cutoff control valve 5233 is connected to the rodless chamber of the third variable cylinder 522 through an oil passage. The second electro-proportional control valve 5232 and the second pressure cutoff control valve 5233 each have a left position and a right position, and the second electro-proportional control valve 5232 and the second pressure cutoff control valve 5233 can change the communication state of the respective first-end and second-end oil passages by switching the left position and the right position.
The application also provides engineering equipment comprising the potential energy recovery system provided by any one of the above embodiments.
The foregoing description has been presented for purposes of illustration and description. Furthermore, the description is not intended to limit embodiments of the application to the form disclosed herein. While a number of example aspects and embodiments have been discussed above, those of skill in the art will recognize certain variations, modifications, alterations, additions and sub-combinations thereof.
Claims (9)
1. A potential energy recovery system, comprising: the device comprises a storage battery, a first motor, a second motor, a pump, a motor, a reversing valve, a balance valve, a lifting oil cylinder and a controller;
the first motor and the second motor are respectively and electrically connected with the storage battery, the first motor, the pump, the reversing valve and the lifting oil cylinder are sequentially connected, and the second motor, the balance valve and the lifting oil cylinder are sequentially connected;
the motor comprises an electric proportional plunger motor, and the electric proportional plunger motor is connected with a rodless cavity of the lifting oil cylinder through the balance valve; the controller is used for controlling the balance valve to communicate the rodless cavity of the lifting oil cylinder with the electric proportional plunger motor according to the obtained descending speed instruction, and controlling the flow of the electric proportional plunger motor according to the descending speed instruction.
2. The potential energy recovery system of claim 1, wherein the pump comprises an electro-proportional plunger pump connected to the rodless chamber of the lift cylinder through the reversing valve;
the controller is further used for controlling the opening of the reversing valve according to the obtained ascending speed instruction, and controlling the flow of the electric proportional plunger pump to be matched with the opening according to the opening.
3. The potential energy recovery system of claim 2, wherein the reversing valve comprises an electro-proportional reversing valve; the controller is used for controlling the opening degree of the reversing valve according to the acquired ascending speed instruction and comprises the following steps:
and the controller is used for matching the flow corresponding to the ascending speed instruction according to the ascending speed instruction and outputting a current matched with the flow corresponding to the ascending speed instruction to the electric proportional reversing valve so as to switch the electric proportional reversing valve to the opening degree.
4. The potential energy recovery system of claim 3, wherein the electro-proportional reversing valve is a three-position, four-way electro-proportional reversing valve.
5. The potential energy recovery system of claim 1, wherein the balancing valve comprises a load holding valve.
6. The potential energy recovery system of claim 3, further comprising a control pump and a tank, the control pump for pumping hydraulic oil from the tank to an external control port of at least one of the electrically proportional plunger pump and the electrically proportional plunger motor.
7. The potential energy recovery system of claim 6, wherein an oil outlet of the control pump is connected to the external control port of the electro-proportional plunger motor through a one-way valve.
8. The potential energy recovery system of claim 6, wherein at least one of the electro-proportional reversing valve, the control pump, the electro-proportional plunger motor, and the electro-proportional plunger pump is in communication with the oil tank.
9. An engineering plant, characterized in that it comprises a potential energy recovery system according to any one of claims 1-8.
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| CN202110130583.XA CN112922773B (en) | 2021-01-29 | 2021-01-29 | Potential energy recovery system and engineering equipment |
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| CN202110130583.XA CN112922773B (en) | 2021-01-29 | 2021-01-29 | Potential energy recovery system and engineering equipment |
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| CN112922773B true CN112922773B (en) | 2023-02-28 |
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Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103183296A (en) * | 2013-04-16 | 2013-07-03 | 安徽合力股份有限公司 | Pump motor cataclinal power generation control system |
| CN104879349A (en) * | 2015-04-13 | 2015-09-02 | 徐州重型机械有限公司 | Hydraulic system for energy recovery and utilization and engineering machinery vehicle |
| CN106996400A (en) * | 2017-05-03 | 2017-08-01 | 中冶南方工程技术有限公司 | A kind of RH steel ladle jacking hydraulic systems of proportioning pump and proportional valve control |
| CN107630847A (en) * | 2017-09-15 | 2018-01-26 | 太原理工大学 | Electric ratio pressure continuously regulates and controls hydraulic motor/pump |
| CN108569655A (en) * | 2017-09-15 | 2018-09-25 | 中国国际海运集装箱(集团)股份有限公司 | A kind of lifting hydraulic control system, control method and connecting bridge |
| CN110966151A (en) * | 2019-12-25 | 2020-04-07 | 三一海洋重工有限公司 | Potential energy recovery system and control method thereof |
-
2021
- 2021-01-29 CN CN202110130583.XA patent/CN112922773B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103183296A (en) * | 2013-04-16 | 2013-07-03 | 安徽合力股份有限公司 | Pump motor cataclinal power generation control system |
| CN104879349A (en) * | 2015-04-13 | 2015-09-02 | 徐州重型机械有限公司 | Hydraulic system for energy recovery and utilization and engineering machinery vehicle |
| CN106996400A (en) * | 2017-05-03 | 2017-08-01 | 中冶南方工程技术有限公司 | A kind of RH steel ladle jacking hydraulic systems of proportioning pump and proportional valve control |
| CN107630847A (en) * | 2017-09-15 | 2018-01-26 | 太原理工大学 | Electric ratio pressure continuously regulates and controls hydraulic motor/pump |
| CN108569655A (en) * | 2017-09-15 | 2018-09-25 | 中国国际海运集装箱(集团)股份有限公司 | A kind of lifting hydraulic control system, control method and connecting bridge |
| CN110966151A (en) * | 2019-12-25 | 2020-04-07 | 三一海洋重工有限公司 | Potential energy recovery system and control method thereof |
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| CN112922773A (en) | 2021-06-08 |
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