CN114576225A - Energy-saving hydraulic system - Google Patents

Energy-saving hydraulic system Download PDF

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Publication number
CN114576225A
CN114576225A CN202111431683.2A CN202111431683A CN114576225A CN 114576225 A CN114576225 A CN 114576225A CN 202111431683 A CN202111431683 A CN 202111431683A CN 114576225 A CN114576225 A CN 114576225A
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CN
China
Prior art keywords
valve
channel
pressure
interface
overflow
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
CN202111431683.2A
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Chinese (zh)
Inventor
宋武隆
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Wuhan Machinery Co ltd
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Wuhan Machinery Co ltd
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Filing date
Publication date
Application filed by Wuhan Machinery Co ltd filed Critical Wuhan Machinery Co ltd
Publication of CN114576225A publication Critical patent/CN114576225A/en
Pending legal-status Critical Current

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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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/024—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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/027—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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
    • 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
    • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
    • F15B20/007—Overload
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/044—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by electrically-controlled means, e.g. solenoids, torque-motors
    • F15B2013/0448—Actuation by solenoid and permanent magnet
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
    • Y02P80/00—Climate change mitigation technologies for sector-wide applications
    • Y02P80/10—Efficient use of energy, e.g. using compressed air or pressurized fluid as energy carrier

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

An energy-saving hydraulic system comprises a power pump, a hydraulic actuator, a control valve, a proportional solenoid valve, a main pipeline and an overflow unit. The main pipeline comprises a first overflow section and a second overflow section. The overflow unit includes a relief valve, a first diversion passage connected between the first overflow section and the relief valve, and a second diversion passage connected between the second overflow section and the relief valve. When the pressure difference between the first overflow section and the second overflow section reaches a pressure difference threshold value, the safety valve is triggered to be conducted, and therefore the working fluid is discharged. According to the invention, the safety valve can be triggered when the opening degree of the proportional electromagnetic valve is reduced through the second diversion channel, so that the load of the power pump is reduced, and the energy-saving effect is generated.

Description

Energy-saving hydraulic system
Technical Field
The present invention relates to an actuating assembly, and more particularly to an energy efficient hydraulic system.
Background
Referring to fig. 1, a conventional hydraulic system includes a power pump 91, a hydraulic cylinder 92, a control valve 93 disposed between the power pump 91 and the hydraulic cylinder 92 for controlling the hydraulic cylinder 92 to operate, a proportional solenoid valve 94 disposed between the power pump 91 and the control valve 93 for adjusting a flow rate, a safety valve 95 disposed between the power pump 91 and the proportional solenoid valve 94, and a pipeline 96 communicated with the power pump 91, the hydraulic cylinder 92, the control valve 93, the proportional solenoid valve 94, and the safety valve 95. Working fluid passes along the line 96 from the power pump 91 through the relief valve 95, the proportional solenoid valve 94 and the control valve 93 to the hydraulic cylinder 92 in sequence. By controlling the control valve 93, an operator can control the actuation of the hydraulic cylinder 92 and link other mechanical structures to achieve an actuation function. By controlling the proportional solenoid valve 94, the operator can further control the flow into the hydraulic cylinder 92, and thus the speed and force at which the hydraulic cylinder 92 is actuated. When the pressure in the line 96 becomes excessive and reaches a relief threshold, the relief valve 95 is triggered to open, allowing working fluid to be discharged from the relief valve 95 to prevent the power pump 91 or the hydraulic cylinder 92 from being damaged by excessive load.
However, in the process of controlling the proportional solenoid valve 94, if the opening degree of the proportional solenoid valve 94 is decreased, the flow rate passing through the proportional solenoid valve 94 is also decreased. This will cause the pressure upstream of the proportional solenoid valve 94 to rise accordingly. However, the increased pressure does not necessarily exceed the relief threshold, and therefore the relief valve 95 is not necessarily triggered immediately. The relief valve 95 is triggered until the pressure rises to the relief threshold. In this case, the power pump 91 is still subjected to high loads, which, although not damaging, is rather energy-consuming.
Disclosure of Invention
The invention aims to provide an energy-saving hydraulic system which reduces load and saves energy.
The invention relates to an energy-saving hydraulic system which comprises a power pump, a hydraulic actuator, a control valve, a proportional solenoid valve, a main pipeline and an overflow unit.
The power pump is used to drive a working fluid. The hydraulic actuator is supplied with the working fluid and generates an actuating function. The control valve is arranged between the power pump and the hydraulic actuator and used for controlling the hydraulic actuator to act. The proportional solenoid valve is disposed between the power pump and the hydraulic actuator and is used to regulate flow. The main pipeline is communicated with the power pump, the hydraulic actuator, the control valve and the proportional solenoid valve and comprises a first overflow section connected between the power pump and the proportional solenoid valve and a second overflow section connected between the proportional solenoid valve and the control valve.
The overflow unit includes a safety valve, a first diversion channel connected between the first overflow section and the safety valve, a second diversion channel connected between the second overflow section and the safety valve, a first drain channel connected to the safety valve and used for draining, a second drain channel connected between the second diversion channel and the first drain channel, and a check valve disposed in the second drain channel. The relief valve has a first port connected to the first diversion channel and a second port connected to the second diversion channel.
When the pressure in the first overflow section reaches a first overflow threshold value, the safety valve is triggered to be conducted, so that the working fluid flows into the first drainage channel from the first diversion channel and is drained. When the pressure in the second overflow section reaches a second overflow threshold value, the check valve is triggered to be conducted, so that the working fluid flows into the second drainage channel and the first drainage channel from the second diversion channel and is discharged, and the pressure at the second interface is reduced. When the pressure difference between the pressure at the first interface and the pressure at the second interface reaches a pressure difference threshold value, the safety valve is triggered to conduct, so that the working fluid flows into the first drainage channel through the first diversion channel and is drained out.
In the energy-saving hydraulic system, the safety valve further comprises a valve body, a water drainage port which is arranged on one side opposite to the first port and is connected with the first water drainage channel, a valve inner channel which is connected between the first port and the water drainage port, a pressure detection channel which is connected between the first port and the valve inner channel, a first stop group and a second stop group. The valve body defines the first interface, the second interface, the drainage interface, the valve inner channel and the pressure detecting channel. The in-valve passage has a first flow-splitting section and a second flow-splitting section. The first shunt section is adjacent to and communicated with the pressure detection channel. The second flow-dividing section is spaced apart from the first flow-dividing section and is not communicated with the pressure-detecting channel. The first blocking group is arranged at the junction of the first shunt section and the pressure detecting channel. The second stop group is arranged on the second flow dividing section and is partially embedded in the valve body.
In the energy-saving hydraulic system, the first stop group of the safety valve is provided with a first stop piece protruding from the pressure detection channel into the first branch section, an abutting piece arranged in the pressure detection channel and adjacent to the second interface, and a first spring connected between the first stop piece and the abutting piece. The abutting piece is fixed on the valve body and is provided with a through hole which is communicated from one side of the second interface to one side of the first stopping piece. When the pressure difference between the pressure at the first interface and the pressure at the second interface reaches the pressure difference threshold, the first spring is compressed and causes the first stopper to retract into the pressure detection channel.
In the energy-saving hydraulic system, the second stopping group of the safety valve is provided with a second stopping piece protruding from the valve body into the second flow dividing section, and a second spring connected between the second stopping piece and the valve body. When the pressure in the first spill segment reaches the first spill threshold, the second spring is compressed and retracts the second stop into the valve body.
According to the energy-saving hydraulic system, the overflow unit further comprises a throttling valve arranged in the second diversion channel.
According to the energy-saving hydraulic system, the hydraulic actuator is a hydraulic cylinder.
According to the energy-saving hydraulic system, the control valve is a three-position four-way valve.
The invention has the beneficial effects that: the pressure of the second overflow section is guided to the check valve and the second interface through the second diversion channel, so that the safety valve can be triggered when the opening degree of the proportional solenoid valve is reduced, the load of the power pump is reduced, and the energy-saving effect is achieved.
Drawings
FIG. 1 is a schematic diagram of a prior art hydraulic system;
FIG. 2 is a schematic structural diagram of an embodiment of the energy-saving hydraulic system of the present invention;
FIG. 3 is a timing chart of an energization amount of a proportional solenoid valve of the embodiment;
fig. 4 is a schematic structural view of a safety valve of the embodiment.
Detailed Description
The present invention will be described in detail below with reference to the accompanying drawings and examples.
Referring to fig. 2 and 3, an embodiment of the energy-saving hydraulic system of the present invention includes a power pump 1, a hydraulic actuator 2, a control valve 3, a proportional solenoid valve 4, a main line 5, and an overflow unit 6.
The power pump 1 is used to drive a working fluid (not shown in the drawings). The hydraulic actuator 2 is supplied with the working fluid and performs an actuation function. The control valve 3 is disposed between the power pump 1 and the hydraulic actuator 2 and is used for controlling the hydraulic actuator 2 to move. The proportional solenoid valve 4 is disposed between the power pump 1 and the hydraulic actuator 2 and is used to regulate the flow rate. The main pipeline 5 is communicated with the power pump 1, the hydraulic actuator 2, the control valve 3 and the proportional solenoid valve 4, and comprises a first overflow section 51 connected between the power pump 1 and the proportional solenoid valve 4 and a second overflow section 52 connected between the proportional solenoid valve 4 and the control valve 3.
It should be noted that the hydraulic actuator 2 is a hydraulic cylinder and the control valve 3 is a three-position four-way valve in the present embodiment, but this is only an example, and those skilled in the art can adopt different component configurations to achieve the actuating function according to the requirement, and should not be limited to this.
The overflow unit 6 includes a relief valve 61, a first diversion channel 63 connected between the first overflow section 51 and the relief valve 61, a second diversion channel 64 connected between the second overflow section 52 and the relief valve 61, a first drainage channel 65 connected to the relief valve 61 and used for draining water, a second drainage channel 66 connected between the second diversion channel 64 and the first drainage channel 65, a check valve 67 disposed in the second drainage channel 66, and a throttle valve 68 disposed in the second diversion channel 64.
Referring further to fig. 4, the safety valve 61 has a valve body 611, a first port 612 connected to the first diversion channel 63, a second port 613 connected to the second diversion channel 64, a drain port 614 disposed at a side opposite to the first port 612 and connected to the first drain channel 65, an in-valve channel 615 connected between the first port 612 and the drain port 614, a pressure sensing channel 616 connected between the first port 612 and the in-valve channel 615, a first stopping set 617, and a second stopping set 618.
The valve body 611 defines the first port 612, the second port 613, the drain port 614, the in-valve channel 615, and the pressure sensing channel 616. The valve inner passage 615 has a first flow-splitting section 619 and a second flow-splitting section 620. The first shunt segment 619 is adjacent to and in communication with the pressure sensing passage 616. The second flow-dividing segment 620 is spaced apart from the first flow-dividing segment 619 and is not communicated with the pressure detecting channel 616. The first stopping set 617 is disposed at a junction of the first shunting section 619 and the pressure detecting channel 616. The second stop set 618 is disposed on the second flow splitting section 620 and partially embedded in the valve body 611.
The first stopping set 617 has a first stopping member 621 protruding from the pressure detecting channel 616 into the first shunting section 619, an abutting member 622 disposed in the pressure detecting channel 616 and adjacent to the second port 613, and a first spring 623 connected between the first stopping member 621 and the abutting member 622. The abutting member 622 is fixed to the valve body 611 and has a through hole 624 communicating from one side of the second port 613 to one side of the first stopping member 621. The second stop set 618 has a second stop 625 protruding from the valve body 611 into the second flow-dividing section 620, and a second spring 626 connected between the second stop 625 and the valve body 611.
Since the first diversion channel 63 is connected between the first overflow section 51 and the relief valve 61, the pressure in the first overflow section 51 is directed to the first port 612. When the pressure in the first spill segment 51 reaches a first spill threshold, the second stopper 625 is subjected to the pressure from the first port 612, causing the second spring 626 to be compressed and causing the second stopper 625 to retract into the valve body 611. The working fluid may pass through the second flow leg 620 and reach the drain interface 614. In other words, the relief valve 61 is triggered to open at this time, so that the working fluid can flow into the first drain passage 65 from the first diversion passage 63 and be discharged. Thus, it is avoided that the pressure of the main line 5 is too high and the power pump 1 or the hydraulic cylinder is damaged due to an excessive load. It is worth mentioning that in the present embodiment, the first overflow threshold depends on the rigidity of the second spring 626. Therefore, the second spring 626 with a desired rigidity can be freely selected to set the first overflow threshold value when the present embodiment is applied.
When the opening degree of the proportional solenoid valve 4 is decreased, the flow rate passing through the proportional solenoid valve 4 is also decreased. This will result in a pressure difference between the first overflow section 51 and the second overflow section 52. At this time, if the pressure in the second relief section 52 reaches a second relief threshold value, the check valve 67 is triggered to conduct, so that the working fluid flows into the second drain channel 66 and the first drain channel 65 from the second diversion channel 64 and is discharged, and the pressure at the second port 613 is reduced.
Since the abutting member 622 has the through hole 624, the pressure at the second port 613 is guided to the first stopper 621. When the pressure difference between the pressure at the first port 612 and the pressure at the second port 613 reaches a pressure difference threshold, the first stopper 621 receives the pressure from the first port 612 and overcomes the pressure from the second port 613 and the stiffness of the first spring 623, so that the first spring 623 is compressed and the first stopper 621 is retracted into the pressure detecting passage 616. At this point, the working fluid may pass through the first flow-splitting segment 619 and reach the drain interface 614. In other words, the relief valve 61 is triggered to open at this time, so that the working fluid can flow into the first drain passage 65 from the first diversion passage 63 and be discharged. In this way, when the opening degree of the proportional solenoid valve 4 is decreased, the safety valve 61 can be triggered to conduct, so as to reduce the load of the power pump 1, thereby generating the energy saving effect.
It is noted that since the pressure at the first port 612 is from the first overflow section 51 at the upstream and the pressure at the second port 613 is from the second overflow section 52 at the downstream, the pressure at the first port 612 is inevitably greater than the pressure at the second port 613. The key points are that: whether the pressure difference between the pressure at the first port 612 and the pressure at the second port 613 can overcome the stiffness of the first spring 623. Therefore, in the present embodiment, the pressure difference threshold depends on the rigidity of the first spring 623, and the first spring 623 with the rigidity meeting the requirement can be freely selected to set the pressure difference threshold.
In addition, the throttle valve 68 can stabilize the flow rate in the second diversion passage 64, preventing the check valve 67 from being triggered to conduct due to a momentary pressure fluctuation.
In summary, the energy-saving hydraulic system according to the present invention guides the pressure of the second relief section 52 to the check valve 67 and the second port 613 through the second diversion channel 64, so that the relief valve 61 can be triggered when the opening degree of the proportional solenoid valve 4 is decreased, the load of the power pump 1 is reduced, and the energy-saving effect is generated, thereby achieving the objective of the present invention.

Claims (7)

1. An energy-saving hydraulic system comprises a power pump, a hydraulic actuator, a control valve, a proportional solenoid valve, a main pipeline and an overflow unit; the method is characterized in that:
the power pump is used for driving working fluid;
the hydraulic actuator is used for the working fluid to flow in and generate an actuating function;
the control valve is arranged between the power pump and the hydraulic actuator and is used for controlling the hydraulic actuator to act;
the proportional solenoid valve is arranged between the power pump and the hydraulic actuator and is used for regulating the flow;
the main pipeline is communicated with the power pump, the hydraulic actuator, the control valve and the proportional solenoid valve, and comprises a first overflow section connected between the power pump and the proportional solenoid valve and a second overflow section connected between the proportional solenoid valve and the control valve;
the overflow unit comprises a safety valve, a first diversion channel connected between the first overflow section and the safety valve, a second diversion channel connected between the second overflow section and the safety valve, a first drainage channel connected to the safety valve and used for draining water, a second drainage channel connected between the second diversion channel and the first drainage channel, and a check valve arranged in the second drainage channel, wherein the safety valve is provided with a first interface connected with the first diversion channel and a second interface connected with the second diversion channel, when the pressure in the first overflow section reaches a first overflow threshold value, the safety valve is triggered to be conducted, so that the working fluid flows into the first drainage channel from the first diversion channel and is drained out, when the pressure in the second overflow section reaches a second overflow threshold value, the check valve is triggered to conduct, so that the working fluid flows into the second drainage channel and the first drainage channel from the second diversion channel and is discharged, the pressure at the second interface is reduced, and when the pressure difference between the pressure at the first interface and the pressure at the second interface reaches a pressure difference threshold value, the safety valve is triggered to conduct, so that the working fluid flows into the first drainage channel through the first diversion channel and is discharged.
2. The economized hydraulic system of claim 1, wherein: the safety valve is also provided with a valve body, a water drainage interface which is arranged on one side opposite to the first interface and is connected with the first water drainage channel, a valve inner channel which is connected between the first interface and the water drainage interface, a pressure detection channel which is connected between the first interface and the valve inner channel, a first stop group and a second stop group, the valve body defines the first interface, the second interface, the drainage interface, the valve inner channel and the pressure detecting channel, the valve inner channel is provided with a first flow dividing section and a second flow dividing section, the first flow dividing section is adjacent to and communicated with the pressure detecting channel, the second flow-dividing section is spaced apart from the first flow-dividing section and is not communicated with the pressure-detecting channel, the first stop group is arranged at the junction of the first shunt section and the pressure detecting channel, and the second stop group is arranged at the second shunt section and is partially embedded in the valve body.
3. The economized hydraulic system of claim 2, wherein: the first stop group of the safety valve is provided with a first stop piece protruding from the pressure detection channel into the first shunting section, an abutting piece arranged in the pressure detection channel and adjacent to the second interface, and a first spring connected between the first stop piece and the abutting piece, wherein the abutting piece is fixed on the valve body and is provided with a through hole communicated from one side of the second interface to one side of the first stop piece, and when the pressure difference between the pressure at the first interface and the pressure at the second interface reaches the pressure difference threshold value, the first spring is compressed and enables the first stop piece to retract into the pressure detection channel.
4. The economized hydraulic system of claim 2, wherein: the second stop group of the safety valve is provided with a second stop piece protruding from the valve body into the second branch section and a second spring connected between the second stop piece and the valve body, and when the pressure in the first overflow section reaches the first overflow threshold value, the second spring is compressed and enables the second stop piece to retract into the valve body.
5. The economized hydraulic system of claim 1, wherein: the overflow unit further comprises a throttle valve arranged in the second diversion channel.
6. The energy efficient hydraulic system of claim 1, wherein: the hydraulic actuator is a hydraulic cylinder.
7. The economized hydraulic system of claim 1, wherein: the control valve is a three-position four-way valve.
CN202111431683.2A 2020-12-02 2021-11-29 Energy-saving hydraulic system Pending CN114576225A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
TW109142497 2020-12-02
TW109142497A TWI755182B (en) 2020-12-02 2020-12-02 Energy-saving hydraulic system

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CN114576225A true CN114576225A (en) 2022-06-03

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TW (1) TWI755182B (en)

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5368943B2 (en) * 2009-11-10 2013-12-18 川崎重工業株式会社 Hydraulic control device
JP6569852B2 (en) * 2015-06-25 2019-09-04 ヤンマー株式会社 Hydraulic device
CN210531261U (en) * 2019-09-30 2020-05-15 广东联城住工装备信息科技有限公司 Hydraulic control system for vibration station and vibration table

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TWI755182B (en) 2022-02-11

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