WO2024159846A1 - 控制单元和液压系统及作业机械 - Google Patents

控制单元和液压系统及作业机械 Download PDF

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Publication number
WO2024159846A1
WO2024159846A1 PCT/CN2023/129962 CN2023129962W WO2024159846A1 WO 2024159846 A1 WO2024159846 A1 WO 2024159846A1 CN 2023129962 W CN2023129962 W CN 2023129962W WO 2024159846 A1 WO2024159846 A1 WO 2024159846A1
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WO
WIPO (PCT)
Prior art keywords
port
pressure
valve
control unit
oil
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2023/129962
Other languages
English (en)
French (fr)
Inventor
金高
杨耀祥
梁凯
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Sany Automobile Hoisting Machinery Co Ltd
Original Assignee
Sany Automobile Hoisting Machinery Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Sany Automobile Hoisting Machinery Co Ltd filed Critical Sany Automobile Hoisting Machinery Co Ltd
Priority to EP23919410.3A priority Critical patent/EP4624763A4/en
Publication of WO2024159846A1 publication Critical patent/WO2024159846A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
    • B66D1/28—Other constructional details
    • B66D1/40—Control devices
    • B66D1/42—Control devices non-automatic
    • B66D1/44—Control devices non-automatic pneumatic of hydraulic
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D5/00—Braking or detent devices characterised by application to lifting or hoisting gear, e.g. for controlling the lowering of loads
    • B66D5/02—Crane, lift hoist, or winch brakes operating on drums, barrels, or ropes
    • B66D5/24—Operating devices
    • B66D5/26—Operating devices pneumatic or hydraulic
    • 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
    • F15B13/025—Pressure reducing 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
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • 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
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool 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
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid 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
    • 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
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B2013/041—Valve members; Fluid interconnections therefor with two positions
    • 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
    • F15B2211/3052—Shuttle 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
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40507—Flow control characterised by the type of flow control means or valve with constant throttles or orifices
    • 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
    • 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
    • F15B2211/41563—Flow control characterised by the connections of the flow 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
    • F15B2211/40—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
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/428—Flow control characterised by the type of actuation actuated by fluid 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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50554—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure downstream of the pressure control means, e.g. pressure reducing valve
    • 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
    • F15B2211/50563—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
    • F15B2211/50581—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using counterbalance 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
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5158—Pressure control characterised by the connections of the pressure 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7058—Rotary output members
    • 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/715—Output members, e.g. hydraulic motors or cylinders or control therefor having braking means
    • 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/72—Output members, e.g. hydraulic motors or cylinders or control therefor having locking means

Definitions

  • the present application relates to the field of hydraulic technology, and in particular to a control unit, a hydraulic system and an operating machine.
  • cartridge valves with sequential pressure relief function are commonly used on winch balance valves.
  • the cartridge valves are often opened sequentially first and then pressure relief and relief.
  • This cartridge valve has high requirements on the size of the unloading groove and the matching of the valve core and the valve sleeve.
  • the winch hoisting load is slightly moved, the winch often shakes, which seriously affects the hoisting accuracy and safety.
  • the purpose of this application is to solve the problem of winch shaking in the micro-motion working condition of winch hoisting.
  • the embodiments of this application are committed to providing a control unit, a hydraulic system and an operating machine, which can reduce the shaking of the winch using the control unit in the micro-motion working condition.
  • the present application provides a control unit, the control unit having a P port leading to a pressure source, a T port leading to an oil tank, and a B port leading to an actuator unit, wherein the control unit includes a pressure reducing valve, a sequence valve, and a unloading damper connected between the P port and the B port, and the control unit is configured as follows: in an initial state, the pressure oil delivered from the P port is simultaneously delivered to the T port and the B port through the unloading damper; in a load state, the pressure oil delivered from the P port can be delivered to the B port from the inlet side of the unloading damper, and the B port is disconnected from the unloading damper; the control unit also includes a first pilot oil circuit and a second pilot oil circuit, wherein the first pilot oil circuit controls the action of the sequence valve so that the control unit switches between the initial state and the load state, and the second pilot oil circuit controls the action of the pressure reducing valve to control the input flow of the P port
  • two ends of the first pilot oil circuit are respectively connected to the control end of the sequence valve and the inlet of the unloading damper, and/or two ends of the second pilot oil circuit are respectively connected to the control end of the pressure reducing valve and the inlet of the unloading damper.
  • the housing of the pressure reducing valve and the housing of the sequence valve are an integrated valve body, and the P port, the T port and the B port are formed on the valve body.
  • the valve core of the pressure reducing valve and the valve core of the sequence valve are a main valve core of an integrated structure
  • the unloading damping is formed on the main valve core
  • the valve body is provided with a valve body cavity
  • the main valve core is slidably arranged in the valve body cavity
  • the P port, T port and B port penetrate the wall of the valve body and are connected to the valve body cavity.
  • an axially extending central oil passage is provided on the main valve core, and the unloading damping includes a damping hole that penetrates the wall of the main valve core and passes through the central oil passage.
  • the main valve core is also provided with a pressure oil port that passes through the wall of the main valve core and connects to the central oil passage: in the initial state, the P port is connected to the T port and the B port at the same time through the pressure oil port and the central oil passage and then through the damping hole.
  • a pilot oil hole is formed on the main valve core, which passes through the wall of the main valve core and is connected to the central oil channel.
  • the damping hole is disconnected from the B port, and the P port is connected to the B port, wherein the pressure oil delivered from the P port passes through the pressure oil port along the central oil channel to the pilot oil hole to form a first pilot oil path.
  • the main valve core can move so that the pilot oil hole is connected to the B port to realize the switching of the control unit from the initial state to the load state.
  • a second aspect of the present application provides a hydraulic system, which includes the above-mentioned control unit and execution unit, wherein port B leads to the execution unit.
  • the actuator unit includes a motor and a brake of the brake motor
  • the B port leads to the brake cylinder of the brake
  • the hydraulic system also includes a first pipeline and a second pipeline
  • the motor has two oil ports, one of which is connected to the first main pressure port through the first pipeline, and the other is connected to the second main pressure oil port through the second pipeline
  • the P port connects the high pressure of the first pipeline and the second pipeline.
  • the hydraulic system further comprises a balancing valve, which is installed on one of the first pipeline and the second pipeline, and a control end of the balancing valve is connected to the other one.
  • a third aspect of the present application provides a working machine, which includes the above-mentioned hydraulic system.
  • the present application sets a unloading damping between the pressure reducing valve and the sequence valve, and sets it so that in the initial state, the pressure oil delivered from the P port is connected to the B port and the T port respectively after the unloading damping, so as to realize pressure reducing and overflow unloading.
  • the B port and the P port are directly connected to bypass the unloading damping to provide the required pressure for the execution unit.
  • the present application also controls the flow of the P port by controlling the pressure reducing valve through the first pilot oil circuit, and uses the second pilot oil circuit to control the action of the sequence valve to realize switching between the initial transition state and the load state. It can realize on-demand opening, first reducing pressure and overflowing, and then opening sequentially.
  • the outer casing can ensure the normal operation of the brake connected to the B port, thereby avoiding the occurrence of abnormal opening of the brake in the winch system due to the influence of the manufacturing precision of the control unit, thereby completely solving the problem of jitter of the winch system in the winch micro-motion working condition.
  • FIG1 is a schematic diagram of the working principle of a control unit provided in an embodiment of the present application.
  • FIG2 is a schematic diagram of the structure of a control unit provided in an embodiment of the present application.
  • FIG3 is a schematic structural diagram of the main valve core in FIG2 ;
  • FIG. 4 is a schematic diagram of a hydraulic system provided in an embodiment of the present application.
  • the present application provides a control unit, the control unit having a P port leading to a pressure source, a T port leading to an oil tank, and a B port leading to an actuator unit, the control unit comprising a pressure reducing valve k1, a sequence valve k2, and a load unloading damper k3 connected between the P port and the B port, the control unit being configured as follows: in an initial state, the pressure oil delivered from the P port is simultaneously delivered to the T port and the B port via the load unloading damper k3.
  • the control unit having a P port leading to a pressure source, a T port leading to an oil tank, and a B port leading to an actuator unit, the control unit comprising a pressure reducing valve k1, a sequence valve k2, and a load unloading damper k3 connected between the P port and the B port, the control unit being configured as follows: in an initial state, the pressure oil delivered from the P port is simultaneously delivered to the T port and the B port via the load unloading damper k
  • the pressure oil delivered from the P port is simultaneously delivered to the T port via the load unloading damper k3 via the second oil circuit L2, and is simultaneously delivered to the T port via the third oil circuit L3.
  • the pressure oil delivered from the P port can be delivered to the B port from the inlet side of the unloading damper k3 in the load state, and the B port is disconnected from the unloading damper k3, and the pressure oil delivered from the P port flows along the first oil circuit L1 to the B port;
  • the control unit also includes a first pilot oil circuit d1 and a second pilot oil circuit d2, wherein the first pilot oil circuit d1 controls the action of the sequence valve k2 so that the control unit switches between the initial state and the load state, and the second pilot oil circuit d2 controls the action of the pressure reducing valve k1 to control the input flow of the P port.
  • the present application can realize opening on demand, first reducing pressure and overflowing, and then opening sequentially.
  • the brake 6 connected to the B port can be guaranteed to work normally, thereby completely solving the influence of the vibration caused by the overflow unloading, and effectively preventing the winch from shaking under the winch micro-motion working condition in the winch system.
  • the outlet of the unloading damper k3 is connected to the B port and the T port at the same time, so that the B port and the T port are also connected at this time, when the pressure of the P port gradually decreases, the sequence valve k2 is reset from the load state to the initial state, and the B port is connected to the T port, which can realize the rapid pressure relief of the control port and avoid action delay.
  • the sequence valve k2 has two working positions.
  • the B port is connected to the outlet of the pressure reducing valve k1 from the inlet side of the unloading damper k3.
  • the second working position k22 of the sequence valve k2 is connected, the pressure oil delivered from the P port is simultaneously delivered to the T port and the B port through the unloading damper k3.
  • the two ends of the first pilot oil circuit d1 are respectively connected to the control end of the sequence valve k2 and the inlet of the unloading damper k3, and the sequence valve k2 drives the valve core of the sequence valve k2 to move according to the inlet side pressure of the unloading damper k3 to achieve switching between the initial state and the load state, wherein the pressure at the inlet of the unloading damper k3 is consistent with the pressure at the outlet of the pressure reducing valve k1.
  • the two ends of the second pilot oil circuit d2 are respectively connected to the control end of the pressure reducing valve k1 and the inlet of the unloading damper k3. Since the inlet pressure of the unloading damper k3 is consistent with the outlet pressure of the pressure reducing valve k1, that is to say, the second pilot oil circuit d2 of the present application can adjust the inlet flow of the P port according to the outlet pressure of the pressure reducing valve k1, so that how much pressure the B port needs, how much pressure the P port can provide.
  • the pressure reducing valve k1 and/or the sequence valve k2 are provided with an oil drain hole, which is connected to the port T. As shown in FIG1 , the oil drain hole of the pressure reducing valve k1 is directly connected to the port T through the fourth oil path L4 and returns to the oil tank. The oil drain hole of the sequence valve k2 is directly connected to the port T and returns to the oil tank through the fifth oil path L5.
  • the pressure reducing valve k1, the sequence valve k2 and the unloading damper k3 can be configured as a plurality of independent valves and then connected via an external pipeline, or at least two of them can share a housing to form a valve group.
  • the outer shell of the pressure reducing valve k1 and the outer shell of the sequence valve k2 are an integrated valve body 1, and the P port, the T port and the B port are formed on the valve body 1.
  • the valve body 1 can also share a common outer shell for the three.
  • the pressure reducing valve k1, the sequence valve k2 and the unloading damper k3 share a same valve body 1 as the outer shell
  • the valve core of the pressure reducing valve k1 and the valve core of the sequence valve k2 are a main valve core 2 of an integrated structure
  • the unloading damper k3 is formed on the main valve core 2
  • the valve body 1 has a valve body cavity 10
  • the main valve core 2 is slidably arranged in the valve body cavity 10
  • the P port, the T port and the B port penetrate the wall of the valve body 1 and are connected to the valve body cavity 10.
  • the main valve core 2 is provided with an axially extending central oil passage 2a, and the unloading damping k3 includes a damping hole 2b that penetrates the wall of the main valve core 2 and passes through the central oil passage 2a.
  • the main valve core 2 is also provided with a pressure oil port 2c that penetrates the wall of the main valve core 2 and communicates with the central oil passage 2a: in the initial state, the P port is connected to the T port and the B port at the same time through the pressure oil port 2c and the central oil passage 2a and then through the damping hole 2b.
  • a pressure spring 3 is provided at one end of the main valve core 2.
  • the P port is connected to the B and T ports through the damping hole 2b, and the pressure is first reduced and overflowed.
  • the main valve core 2 gradually moves toward the pressure spring 3 until the damping hole 2b and the B port are disconnected, and the B port and the P port are directly connected to achieve sequential opening, wherein the pressure provided from the P port is adapted to the pressure required for the opening of the main valve core 2.
  • the main valve core 2 moves to the limit position and cannot move further in the direction of the pressure spring 3, the P port and the pressure oil port 2c can be disconnected.
  • the arrangement of the pressure spring 3 is shown in Figure 2.
  • a valve seat 5 is provided in the valve body cavity 10.
  • the above-mentioned pressure spring 3 is also installed in the valve body cavity 10.
  • One end of the pressure spring 3 is installed on the valve seat 5, and the other end abuts against the main valve core 2.
  • the main valve core 2 is provided with a mounting rod 26.
  • the outer diameter of the mounting rod 26 is smaller than the inner diameter of the pressure spring 3.
  • the mounting rod 26 is passed through the center hole of the pressure spring 3.
  • the main valve core 2 is cylindrical, and a plurality of annular grooves and shoulders between two adjacent annular grooves are provided on the outer circumference of the main valve core 2.
  • the annular grooves allow the oil to be distributed 360° around the circumference of the main valve core 2, so that when controlling each oil circuit, it is only necessary to control the axial movement of the main valve core 2 in the valve body cavity 10.
  • the central oil passage 2 a is a blind hole, and the opening of the central oil passage 2 a is located at an end surface of the main valve core 2 away from the pressure spring 3 .
  • valve sleeve 11 has a first annular groove c1 opened on the inner surface of the valve sleeve 11, as shown in FIG2, the inner end of the B port opens on the bottom wall of the first annular groove c1, as shown in FIG2 and FIG3, the main valve core 2 is formed with a second annular groove c2 and a third annular groove c3 opened on the outer surface of the main valve core 2, and a first shoulder 21 is formed between the second annular groove c2 and the third annular groove c3, wherein the second annular groove c2 is located on the side of the first shoulder 21 close to the pressure spring 3, and the outer end of the damping hole 2b opens on the bottom wall of the second annular groove c2, and the main valve core 2 is also provided with a fourth annular groove c4 opened on the outer surface of the main valve core 2, and an axially extending groove channel 24a is provided on the fourth shoulder 24 between the fourth annular groove c4 and the second annular groove c2, and the damping
  • the damping hole 2 b can be connected to the fourth annular groove c4 and then to the T port through the groove channel 24 a .
  • the second annular groove c2 in the initial state, is connected to the first annular groove c1, and the damping hole 2b is connected to the B port and the central oil passage 2a through the second annular groove c2 and the first annular groove c1, and thus can be connected to the P port through the pressure oil port 2c. That is, at this time, the P port is connected to the central oil passage 2a through the pressure oil port 2c, and then is simultaneously connected to the B port and the T port through the damping hole 2b, thereby realizing the pressure relief function of the present application.
  • a pilot oil hole 2d is formed on the main valve core 2, which passes through the wall of the main valve core 2 and is connected to the central oil passage 2a.
  • the damping hole 2b is disconnected from the B port, and the P port is connected to the B port.
  • the pressure oil delivered from the P port passes through the pressure oil port 2c along the central oil passage 2a to the pilot oil hole 2d to form the first pilot oil path d1 as shown in FIG1.
  • the main valve core 2 can move so that the pilot oil hole 2d is connected to the B port, so that the control unit is switched from the initial state to the load state.
  • a first inner shoulder 11b is formed on the side of the first annular groove c1 close to the pressure spring 3.
  • the first inner shoulder 11b is axially located in the middle of the second annular groove c2, so that the damping hole 2b can be connected to the B port through the second annular groove c2 and the first annular groove c1, and the damping hole 2b is connected to the T port through the groove channel 24a and then through the fourth annular groove c4, so as to achieve pressure relief.
  • the pressure in the central oil channel 2a also gradually increases, and the main valve core 2 is pushed to move in the direction of the pressure spring 3 under the action of the axial force, and the third shoulder 23 gradually approaches the first inner shoulder 11b until it abuts against the first inner shoulder 11b, so that the damping hole 2b and the first annular groove c1 are disconnected, and the pilot oil hole 2d is connected to the third annular groove c3 through the fifth annular groove c5.
  • the fifth annular groove c5 opens on the outer surface of the main valve core 2, and the outer end of the pilot oil hole 2d opens on the bottom wall of the fifth annular groove c5.
  • the first annular groove c1 forms a second inner shoulder 11d on the side close to the pressure oil port 2c.
  • the second inner shoulder 11d fits with the first shoulder 21, and the B port cannot be connected to the P port through the fifth annular groove c5, the pilot oil hole 2d and the central oil channel 2a.
  • the first shoulder 21 moves relative to the second inner shoulder 11d toward the pressure spring 3, and the second inner shoulder 11d and the first shoulder 21 gradually break away from contact, so that the fifth annular groove c5 is connected to the first annular groove c1, so that the P port can be connected to the B port through the pressure oil port 2c and the central oil channel 2a from the pilot oil hole 2d through the fifth annular groove c5 and then through the first annular groove c1 to form the first oil path L1 as shown in Figures 1 and 4, and at the same time, the third shoulder 23 and the first inner shoulder 11b fit together to separate the damping hole 2b and the B port.
  • the P port and the B port are directly connected from the inlet side of the damping hole 2b.
  • the damping hole 2h is only connected to the T port at this time, which can avoid the pressure shock caused by the pressure oil converging from the side of the B port close to the pressure spring 3 to the B port on the one hand, and converging from the side away from the pressure spring 4 to the B port on the other hand, and interfering with each other.
  • a fifth shoulder 25 is formed between the fourth annular groove c4 and the mounting rod 26, and the outer wall of the fifth shoulder 25 is in contact with the inner wall of the valve body cavity 10.
  • the fifth shoulder 25 is provided with an oil drain hole 25a axially penetrating the fifth shoulder 25, and the oil drain hole 25a is connected to the T port through the fourth annular groove c4 to achieve oil drain.
  • valve body 1 includes a valve sleeve 11 and a valve seat 12, one of the valve sleeve 11 and the valve seat 12 has an internal thread, and the other has an external thread, and the two are threadedly connected together.
  • valve sleeve 11 and the valve seat 12 located on the outside is also provided with an external thread to install the control unit of the present application on a mechanism using the control unit.
  • the valve sleeve 11 has an external thread
  • the valve seat 12 has an internal thread that matches the external thread of the valve sleeve 11.
  • the valve seat 12 also has an external thread to fix the control unit on other mechanisms.
  • control unit includes a sealing ring 4 sleeved on the outside of the control unit of the present invention to ensure the seal between the control unit and the above-mentioned mechanism.
  • the sealing ring 4 is sleeved on the outer periphery of the valve seat 12 .
  • the present application provides a hydraulic system, which includes the above control unit and an execution unit, wherein port B leads to the execution unit.
  • the hydraulic system has the technical advantages of the above control unit, which will not be described in detail here.
  • the execution unit includes a motor 7 and a brake 6 of the brake motor 7, the B port leads to the brake cylinder of the brake 6, the hydraulic system also includes a first pipeline g1 and a second pipeline g2, the motor 7 has two oil ports, one of which is connected to the second main pressure oil port B' through the first pipeline g1, and the other is connected to the first main pressure port A' through the second pipeline g2, and the P port is connected to the high pressure of the first pipeline g1 and the second pipeline g2.
  • the hydraulic system realizes pre-charging of part of the pressure oil to the brake 6 through the B port.
  • the P port is connected to the high pressure of the first main pressure port A' and the second main pressure oil port B' through a shuttle valve.
  • the hydraulic system further includes a balancing valve k5 , which is installed on one of the first pipeline g1 and the second pipeline g2 , and a control end of the balancing valve k5 is connected to the other one.
  • the pressure oil enters the motor 7 from the second main pressure oil port B' along the first pipeline g1, and a part of the pressure oil overcomes the spring pressure of the balance valve k5, pushes the valve stem of the balance valve k5 to open the balance valve k5, so that the second working position k52 of the balance valve k5 is connected, so that the second pipeline g2 is connected to the motor 7 and the first main pressure port A'.
  • a throttle valve is provided in the second working position k52 of the balance valve k5 to provide back pressure for the motor 7.
  • a one-way valve is provided in the first working position k51; under the action of the one-way valve, the first working position k51 of the balancing valve k5 is connected, so that the motor 7 is connected to the second main pressure port A’.
  • the P port of the control unit of the present application is always connected to the high pressure one of the first main pressure oil port A' and the second main pressure oil port B', and the B port is connected to the brake 6. This realizes overflow pressure reduction first and then sequentially opens the sequence valve k2 to pressurize the brake 6. This ensures the normal operation of the brake 6.
  • the hydraulic system of the present application can effectively solve the problem of hoisting vibration during micro-movement.
  • the main pressure oil enters the motor 7 from the first main pressure oil port A' through the second pipeline g2, and the motor 7 rotates forward.
  • a part of the pressure oil delivered from the first main pressure oil port A' enters the control unit of this application through the shuttle valve k4 and the P port.
  • the first station k21 of the sequence valve k2 is connected, and the pressure oil is delivered to the brake 6 through the B port.
  • the brake 6 opens, the motor 7 rotates forward, and the winch is hoisted.
  • the main pressure oil enters the motor 7 from the second main pressure oil port B' through the first pipeline g1, and a part of the pressure oil overcomes the spring pressure of the balancing valve k5, pushes open the valve stem of the balancing valve k5, and opens the balancing valve k5, so that the outlet of the motor 7 is connected with the first main pressure oil port A' through the second pipeline g2.
  • Another part of the pressure oil enters the control unit of the present application through the shuttle valve k4, and is reduced in pressure through the pressure reducing valve k1.
  • a part of the pressure oil after pressure reduction overflows through the unloading damper k3, a part of the overflowing pressure oil returns to the oil tank, and the other part is connected to the brake 6 through the sequence valve k2, so that a part of the pressure oil is pre-filled in the brake pipeline.
  • the motor 7 returns oil through the second pipeline g2 and the first main pressure oil port A', and the motor 7 reverses to achieve winch lowering.
  • the third aspect of the present application provides an operating machine, the operating machine comprising the above-mentioned hydraulic system.
  • the operating machine has the technical advantages of the hydraulic system, which will not be described in detail here.
  • the operating machine also includes a pump, which has two inlets, one of which is an inlet and the other is a non-outlet.
  • the inlet and outlet of the pump are connected to the two oil ports of the motor 7 through the first main pressure port A' and the second main pressure oil port B' respectively.
  • multiple means two or more.
  • At least one of the following or similar expressions refers to any combination of these items, including any combination of single items or plural items.
  • at least one of a, b, or c can mean: a, b, c, a-b, a-c, b-c, or a-b-c, where a, b, and c can be single or multiple.
  • the size of the serial numbers of the above-mentioned processes does not mean the order of execution.
  • the execution order of each process should be determined by its function and internal logic, and should not constitute any limitation on the implementation process of the embodiments of the present application.

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Abstract

一种控制单元和液压系统及作业机械,其中控制单元具有P口、T口及B口及连接在P口和B口间的减压阀（k1）和顺序阀（k2）及卸荷阻尼（k3），控制单元设置为：在初始状态，从P口输送的压力油经卸荷阻尼（k3）同时输向T口和B口；在负载状态，从P口输送的压力油能够从卸荷阻尼（k3）的进口侧输向B口，并且，B口与卸荷阻尼（k3）断开；控制单元还包括第一先导油路（d1）和第二先导油路（d2），其中，第一先导油路（d1）控制顺序阀（k2）动作使得控制单元在初始转态和负载状态间切换，第二先导油路（d2）控制减压阀（k1）动作以控制P口的输入流量，可以实现按需开启，先减压溢流，后顺序开启，从而解决卷扬系统在卷扬微动作工况中的抖动。

Description

控制单元和液压系统及作业机械
本申请要求于2023年1月31日申请的、申请号为202310098584.X的中国专利申请的优先权，其全部内容通过引用结合在本申请中。
技术领域
本申请涉及液压技术领域，具体涉及一种控制单元和液压系统及作业机械。
 背景技术
目前，在工程机械中，普遍应用在卷扬平衡阀上的具有顺序减压溢流功能的插装阀，该插装阀往往是先顺序开启，后减压溢流。这种插装阀对卸荷槽尺寸及阀芯与阀套配合要求高，当卷扬吊载微动作工况，常出现卷扬抖动现象，严重影响吊载精度和安全。
为了解决卷扬吊载在微动作工况中卷扬抖动的问题。因此需要研究一种新的阀组，该阀组能够降低使用该阀组的卷扬在微动作工况中抖动。
 技术问题
本申请的目的是为了解决卷扬吊载微动作工况中卷扬抖动的问题。有鉴于此，本申请实施例致力于提供一种控制单元和液压系统及作业机械，该控制单元能够降低使用该控制单元的卷扬在微动作工况中抖动。
 技术解决方案
为了解决上述问题，第一方面，本申请提供一种控制单元，控制单元具有通往压力源的P口、通往油箱的T口及通往执行单元的B口，其中，控制单元包括连接在P口和B口间的减压阀和顺序阀及卸荷阻尼，控制单元设置为：在初始状态，从P口输送的压力油经卸荷阻尼同时输向T口和B口；在负载状态，从P口输送的压力油能够从卸荷阻尼的进口侧输向B口，并且，B口与卸荷阻尼断开；控制单元还包括第一先导油路和第二先导油路，其中，第一先导油路控制顺序阀动作使得控制单元在初始转态和负载状态间切换，第二先导油路控制减压阀动作以控制P口的输入流量。
在一实施例中，第一先导油路的两端分别连接顺序阀的控制端和卸荷阻尼的进口，和/或，第二先导油路的两端分别连接减压阀的控制端和卸荷阻尼的进口。
在一实施例中，减压阀的外壳和顺序阀的外壳为一体结构的阀体，P口、T口及B口形成在阀体上。
在一实施例中，减压阀的阀芯和顺序阀的阀芯为一体结构的总阀芯，卸荷阻尼形成在总阀芯上，阀体内具有阀体腔，总阀芯滑动设置在阀体腔内，P口、T口及B口穿透阀体的壁并连通阀体腔。
在一实施例中，总阀芯上设置有轴向延伸的中心油道，卸荷阻尼包括穿透总阀芯的壁并贯通中心油道的阻尼孔，总阀芯上还设置有贯通总阀芯的壁并连通中心油道的压力油口：在初始状态，P口通过压力油口及中心油道再通过阻尼孔后同时连通T口和B口。
在一实施例中，总阀芯上形成有贯通总阀芯的壁并连通中心油道的先导油孔，在负载状态，阻尼孔与B口断开，P口和B口连通，其中，从P口输送的压力油经压力油口沿中心油道通往先导油孔形成第一先导油路，在第一先导油路的作用下总阀芯能够移动使得先导油孔与B口连通实现控制单元从初始状态向负载状态切换。
本申请第二方面提供一种液压系统，该液压系统包括上述的控制单元和执行单元，其中，B口通往执行单元。
在一实施例中，执行单元包括马达和制动马达的制动器，B口通往制动器的制动缸，液压系统还包括第一管路和第二管路，马达具有两个油口，其一者通过第一管路连接第一主压力口，其另一者通过第二管路连接第二主压力油口，P口连通第一管路和第二管路中的高压者。
在一实施例中，液压系统还包括平衡阀，平衡阀安装在第一管路和第二管路中其一者上，平衡阀的控制端连接其另一者。
本申请第三方面提供一种作业机械，该作业机械包括上述的液压系统。
 有益效果
通过以上设置，本申请通过在减压阀和顺序阀间设置卸荷阻尼，并设置为在初始状态从P口输送的压力油经卸荷阻尼后分别连通B口和T口，实现减压溢流卸荷，在负载状态B口和P口绕过卸荷阻尼直接连通为执行单元提供需要的压力，本申请还通过第一先导油路控制减压阀实现控制P口的流量，利用第二先导油路控制顺序阀动作实现初始转态和负载状态间切换，可以实现按需开启，先减压溢流，后顺序开启，这样即便控制单元制造精度较低，外壳也可以保证与B口连接的制动器正常工作，从而避免了由于控制单元制造精度的影响造成的制动器在卷扬系统中开启不正常现象的发生，从而彻底解决了卷扬系统在卷扬微动作工况中抖动的问题。
 附图说明
图1为本申请实施例提供的一种控制单元的工作原理示意图；
图2为本申请实施例提供的一种控制单元的结构示意图；
图3为图2中的总阀芯的结构示意图；
图4为本申请实施例提供的一种液压系统示意图。
 本发明的实施方式
下面将结合本申请实施例中的附图，对本申请实施例中的技术方案进行清楚、完整地描述，显然，所描述的实施例仅是本申请一部分实施例，而不是全部的实施例。基于本申请中的实施例，本领域普通技术人员在没有做出创造性劳动前提下所获得的所有其他实施例，都属于本申请保护的范围。
为了更方便的了解本申请，下面根据具体实施例并结合附图描述本申请。
第一方面，参见图1-图3所示，本申请提供一种控制单元，控制单元具有通往压力源的P口、通往油箱的T口及通往执行单元的B口，控制单元包括连接在P口和B口间的减压阀k1和顺序阀k2及卸荷阻尼k3，控制单元设置为：在初始状态，从P口输送的压力油经卸荷阻尼k3同时输向T口和B口，如图1所示的一种实施例中，在初始状态，从P口输送的压力油经卸荷阻尼k3经第二油路L2输向T口，同时经第三油路L3输向B口；在负载状态，从P口输送的压力油能够从卸荷阻尼k3的进口侧输向B口，并且，B口与卸荷阻尼k3断开，从P口输送的压力油沿第一油路L1向B口流动；所述控制单元还包括第一先导油路d1和第二先导油路d2，其中，所述第一先导油路d1控制所述顺序阀k2动作使得所述控制单元在所述初始转态和所述负载状态间切换，所述第二先导油路d2控制所述减压阀k1动作以控制所述P口的输入流量。通过这样设置，本申请可以实现按需开启，先减压溢流，后顺序开启，这样即便减压阀k1和顺序阀k2制造精度较低，减压阀k1的阀芯和减压阀k1的外壳之间、顺序阀k2的阀芯和顺序阀k2的外壳之间存在较大的间隙，也可以保证与B口连接的制动器6正常工作，从而彻底解决溢流卸荷带来抖动的影响，在卷扬系统中可以有效防止在卷扬微动工况下卷扬抖动。在本申请中，由于在初始状态，卸荷阻尼k3的出口处同时连通B口和T口，使得此时B口和T口也连通，当P口压力逐渐减小，顺序阀k2在从负载状态向初始状态复位时，B口连通T口，可实现控制口快速泄压，避免动作延迟。
在图1所示的一种实施例中，顺序阀k2具有两个工位，顺序阀k2的第一工位k21接入时，B口从卸荷阻尼k3的进口侧连通减压阀k1的出口，在顺序阀k2的第二工位k22接入时，从P口输送的压力油经卸荷阻尼k3同时输向T口和B口。
又一实施例中，第一先导油路d1的两端分别连接顺序阀k2的控制端和卸荷阻尼k3的进口，顺序阀k2根据卸荷阻尼k3的进口侧压力驱动顺序阀k2的阀芯移动实现从初始状态和负载状态间的切换，其中，卸荷阻尼k3和进口处的压力和减压阀k1的出口处的压力一致。
又一实施例中，第二先导油路d2的两端分别连接减压阀k1的控制端和卸荷阻尼k3的进口，由于卸荷阻尼k3的进口压力和减压阀k1的出口压力一致，也就是说本申请第二先导油路d2可根据减压阀k1的出口压力调整P口的进口流量，从而B口需要多少压力，P口可以提供多大压力。
其中，减压阀k1和/或顺序阀k2上设置有泄油孔，泄油孔连通T口。如图1所示，减压阀k1的泄油孔直接通过第四油路L4连通T口回到油箱。顺序阀k2的泄油孔通过第五油路L5直接连通T口回到油箱。
在本申请中，减压阀k1和顺序阀k2及卸荷阻尼k3可以设置为多个独立的阀，然后通过外接管道连接，也可以设置为至少其中的两个共用一个外壳组成阀组。
比如减压阀k1的外壳和顺序阀k2的外壳为一体结构的阀体1，P口、T口及B口形成在阀体1上。当然，阀体1也可以三者共用的外壳。
参考图2所示的一种实施例中，减压阀k1和顺序阀k2及卸荷阻尼k3共用一个同一个阀体1作为外壳，减压阀k1的阀芯和顺序阀k2的阀芯为一体结构的总阀芯2，卸荷阻尼k3形成在总阀芯2上，阀体1内具有阀体腔10，总阀芯2滑动设置在阀体腔10内，P口、T口及B口穿透阀体1的壁并连通阀体腔10。
其中，总阀芯2上设置有轴向延伸的中心油道2a，卸荷阻尼k3包括穿透总阀芯2的壁并贯通中心油道2a的阻尼孔2b，总阀芯2上还设置有贯通总阀芯2的壁并连通中心油道2a的压力油口2c：在初始状态，P口通过压力油口2c及中心油道2a再通过阻尼孔2b后同时连通T口和B口。其中，为了使得总阀芯2在P口的压力变小后自动复位，总阀芯2的一端设置有压力弹簧3。通过这样设置，初始状态，P口通过阻尼孔2b与B、T口连接，先减压溢流，当作用在总阀芯2的轴向的压力大于压力弹簧3的开启力之后，总阀芯2逐渐向压力弹簧3移动，直至阻尼孔2b和B口断开，B口和P口直接连通，实现顺序开启，其中，从P口提供的压力与总阀芯2开启需求的压力相适应。当总阀芯2运行至极限位置不能进一步向压力弹簧3的方向运行后，P口和压力油口2c可以断开。
压力弹簧3的设置如图2所示，阀体腔10中设置有阀座5，阀体腔10中还安装有上述压力弹簧3，压力弹簧3的一端安装在阀座5上，另一端抵接总阀芯2，参考图3所示，总阀芯2上具有安装杆26，安装杆26的外径小于压力弹簧3的内径，安装杆26穿设在压力弹簧3的中心孔中。
在本申请中，总阀芯2为柱状，在总阀芯2的外周设置有多个环形槽和位于两个相邻环形槽间的台肩。利用环形槽使得油液可以在总阀芯2的圆周360°分布，因而可以使得在控制各油路时仅需控制总阀芯2在阀体腔10内轴向移动即可。
如图2和图3所示的一种实施例中，中心油道2a为盲孔，中心油道2a的开口位于总阀芯2的远离压力弹簧3的一端端面。
又一实施例中，在初始状态，总阀芯2远离压力弹簧3的一端端面和阀体1之间具有间隙以使得总阀芯2和阀体1间泄露的压力油从中心油道2a的开口处流到中心油道2a中，进而能够回到油箱中。
又一实施例中，阀套11上具有开口在阀套11的内表面的第一环形槽c1，参考图2所示，B口的内端开口于第一环形槽c1的底壁上，参考图2和图3所示，总阀芯2上形成有开口于总阀芯2的外表面的第二环形槽c2和第三环形槽c3，第二环形槽c2和第三环形槽c3之间形成第一台肩21，其中，第二环形槽c2位于第一台肩21的靠近压力弹簧3的一侧，阻尼孔2b的外端开口于第二环形槽c2的底壁上，总阀芯2上还设置有开口于总阀芯2的外表面的第四环形槽c4，第四环形槽c4和第二环形槽c2间的第四台肩24上设置有轴向延伸的凹槽通道24a，阻尼孔2b通过凹槽通道24a路连通T口。通过设置凹槽通道24a，可以在向T口回油时提供一定的背压。
图2所示的一种实施例中，在任何状态下阻尼孔2b均能够通过凹槽通道24a连通第四环形槽c4进而连通T口。
在图2所示的一种实施例中，在初始状态，第二环形槽c2和第一环形槽c1连通，阻尼孔2b通过第二环形槽c2和第一环形槽c1连通B口和中心油道2a，因而可通过压力油口2c连通P口。也就是说，此时，P口通过压力油口2c连通中心油道2a，然后通过阻尼孔2b同时连通B口和T口，从而实现了本申请的减压溢流功能。
又一实施例中，总阀芯2上形成有贯通总阀芯2的壁并连通中心油道2a的先导油孔2d，在负载状态，阻尼孔2b与B口断开，P口和B口连通，其中，从P口输送的压力油经压力油口2c沿中心油道2a通往先导油孔2d形成如图1中所示的第一先导油路d1，在第一先导油路d1的作用下总阀芯2能够移动使得先导油孔2d与B口连通，实现控制单元从初始状态向负载状态切换。参考图2所示，第一环形槽c1的靠近压力弹簧3的一侧形成第一内台肩11b，在初始状态，第一内台肩11b在轴向位于第二环形槽c2中间，从而使得阻尼孔2b可以通过第二环形槽c2及第一环形槽c1连通B口，同时阻尼孔2b通过凹槽通道24a再通过第四环形槽c4连通T口，实现减压溢流。当从初始状态向负载状态切换时，随着P口压力增大，中心油道2a中的压力也逐渐增大，在轴向力的作用下推动总阀芯2向压力弹簧3的方向移动，第三台肩23逐渐向第一内台肩11b靠近直至与第一内台肩11b抵接，使得阻尼孔2b和第一环形槽c1断开，此时先导油孔2d通过第五环形槽c5与第三环形槽c3连通。其中，第五环形槽c5开口于总阀芯2的外表面，先导油孔2d的外端开口于第五环形槽c5的底壁上。第一环形槽c1靠近压力油口2c的一侧形成第二内台肩1ld，在初始状态，第二内台肩1ld与第一台肩21贴合，B口无法通过第五环形槽c5和先导油孔2d及中心油道2a与P口连通。当从初始状态向负载状态切换时，第一台肩21相对第二内台肩1ld向压力弹簧3移动，第二内台肩1ld和第一台肩21逐渐脱离接触，使得第五环形槽c5和第一环形槽c1连通，从而使得P口能够通过压力油口2c及中心油道2a从先导油孔2d经第五环形槽c5再经第一环形槽c1连通B口形成如图1和图4中的第一油路L1，同时第三台肩23和第一内台肩11b贴合，隔断阻尼孔2b和B口。实现P口和B口从阻尼孔2b的进口侧直接连通。阻尼孔2h此时仅和T口连接，这样可避免压力油一方面从B口靠近压力弹簧3的一侧向B口汇聚，另一方面从远离压力弹簧4的一侧向B口汇聚而引起的压力冲击而相互干扰。
在本申请中，当总阀芯2在负载状态，P口和B口通过先导油孔2d直接连通后，如果油压继续升高，在中心油道2a中的压力油的作用下即第二先导油路d2的作用下，第五环形槽c5的控制边LX与P口的口边LT相对运动，形成节流孔，可以调节P口的流量，从而实现B口需要多少压力，系统提供多少压力。
当P口的压力逐渐变小时，在压力弹簧3的复位力作用下，总阀芯2向着压力油口2c移动，第一内台肩11b和第三台肩23从贴合逐渐脱离接触使得B口和T口连通，可实现中心油道2a中快速泄压，避免动作延迟。
又一种实施例中，第四环形槽c4和安装杆26之间形成第五台肩25，第五台肩25的外壁与阀体腔10的内壁贴合。第五台肩25上设置轴向贯穿第五台肩25的泄油孔25a，泄油孔25a通过第四环形槽c4连接T口实现泄油。
又一种实施例中，阀体1包括阀套11和阀座12，阀套11和阀座12其一者具有内螺纹，其另一者具有外螺纹，二者螺纹连接在一起。
进一步的，阀套11和阀座12二者中位于外部的一者还设置有外螺纹以将本申请的控制单元安装在使用该控制单元的机构上。如图2所示的一种实施例中，阀套11具有外螺纹，阀座12具有与阀套11的外螺纹配合的内螺纹。同时阀座12还具有外螺纹以将控制单元固定在其他机构上。
进一步的，控制单元包括套在本申的控制单元外部的密封圈4以保证控制单元和上述机构之间的密封。在图2所示的实施例中，密封圈4套在阀座12的外周。
第二方面，本申请提供一种液压系统，该液压系统包括上述控制单元和执行单元，其中，B口通往执行单元。所述液压系统具有上述控制单元所具有的技术优势，在此不再赘述。
又一实施例中，执行单元包括马达7和制动马达7的制动器6，B口通往制动器6的制动缸，液压系统还包括第一管路g1和第二管路g2，马达7具有两个油口，其一者通过第一管路g1连接第二主压力油口B’，其另一者通过第二管路g2连接第一主压力口A’，P口连通第一管路g1和第二管路g2中的高压者。在初始状态，本液压系统通过B口实现向制动器6预充部分压力油。
进一步的，P口通过梭阀连通第一主压力口A’和第二主压力油口B’中的高压者。
又一实施例中，液压系统还包括平衡阀k5，平衡阀k5安装在第一管路g1和第二管路g2中其一者上，平衡阀k5的控制端连接其另一者。
参考图4所示的一实施例中，压力油从第二主压力油口B’沿第一管路g1进入马达7，一部分压力油克服平衡阀k5的弹簧压力，顶开平衡阀k5的阀杆开启平衡阀k5，使得平衡阀k5的第二工作位k52接入，使得第二管路g2与马达7和第一主压力口A’接通。其中，平衡阀k5的第二工作位k52中设置有节流阀以为马达7提供背压。
当压力油从第一主压力油口A’沿第二管路g2进入马达7，其中，第一工作位k51中设置有单项阀；在单项阀的的作用下，平衡阀k5的第一工作位k51接入，使得马达7与第二主压力口A’接通。
不管压力油从第一主压力油口A’还是从第二主压力油口B’输入马达7，本申请控制单元的P口总是和第一主压力油口A’和第二主压力油口B’中的高压者连通，B口和制动器6连通。实现先溢流减压再顺序开启顺序阀k2对制动器6加压。保证了制动器6正常工作。
其中，当马达7用于驱动卷扬机构时。此时本申请的液压系统可以有效解决微动作中卷扬抖动的问题。
为了更进一步的说明本申请，下面就卷扬的起落进行描述。
卷扬起升时，主压力油由第一主压力油口A’经第二管路g2进马达7，马达7正转，从第一主压力油口A’输送的压力油一部分经过梭阀k4进入经P口进入本申请的控制单元，顺序阀k2的第一工位k21接入,通过B口向制动器6输送压力油，制动器6打开，马达7正转，卷扬起升。
卷扬降落时，主压力油由第二主压力油口B’经第一管路g1进马达7，一部分压力油克服平衡阀k5的弹簧压力，顶开平衡阀k5的阀杆开启平衡阀k5，使得马达7的出口经第二管路g2与第一主压力油口A’接通。
另一部分压力油经梭阀k4进入本申请的控制单元，通过减压阀k1减压，减压后的压力油一部分经卸荷阻尼k3溢流，溢流的压力油一部分回油箱，另一部分经顺序阀k2连通制动器6，使制动管路中预充一部分压力油。
同时，减压后的另一部分压力油经第一先导油路d1直接作用在顺序阀k2的控制端，参考图1和图4，当压力达到顺序阀k2的开启压力后即实现顺序阀k2开启，顺序阀k2的第一工位k21接入,通过B口向制动器6输送压力油，制动器6打开。
马达7经第二管路g2与第一主压力油口A’回油，马达7反转，实现卷扬降落。
本申请第三方面提供一种作业机械，作业机械包括上述的液压系统。作业机械具有液压系统所具有的技术优势，在此不再赘述。
作业机械还包括泵，泵具有两个尤其，其中之一为进口，另一未出口，泵的进口和出口分别通过第一主压力口A’和第二主压力油口B’连接马达7的两个油口。
应理解，本文中术语“和/或”，仅仅是一种描述关联对象的关联关系，表示可以存在三种关系，例如，A和/或B，可以表示：单独存在A，同时存在A和B，单独存在B这三种情况，其中A，B可以是单数或者复数。另外，本文中字符“/”，一般表示前后关联对象是一种“或”的关系，但也可能表示的是一种“和/或”的关系，具体可参考前后文进行理解。
本申请中，“多个”是指两个或两个以上。“以下至少一项个)”或其类似表达，是指的这些项中的任意组合，包括单项（个）或复数项（个）的任意组合。例如，a，b，或c中的至少一项（个），可以表示：a，b，c，a-b，a-c，b-c或a-b-c，其中a，b，c可以是单个，也可以是多个。
应理解，在本申请的各种实施例中，上述各过程的序号的大小并不意味着执行顺序的先后，各过程的执行顺序应以其功能和内在逻辑确定，而不应对本申请实施例的实施过程构成任何限定。
以上所述仅为本申请的较佳实施例而已，并不用以限制本申请，凡在本申请的精神和原则之内，所作的任何修改、等同替换等，均应包含在本申请的保护范围之内。

Claims (10)

  1. 一种控制单元，所述控制单元具有通往压力源的P口、通往油箱的T口及通往执行单元的B口，其中，所述控制单元包括连接在所述P口和所述B口间的减压阀（k1）和顺序阀（k2）及卸荷阻尼（k3），所述控制单元设置为：
    在初始状态，从所述P口输送的压力油经所述卸荷阻尼（k3）同时输向所述T口和所述B口；
    在负载状态，从所述P口输送的压力油能够从所述卸荷阻尼（k3）的进口侧输向所述B口，并且，所述B口与所述卸荷阻尼（k3）断开；
    所述控制单元还包括第一先导油路（d1）和第二先导油路（d2），其中，所述第一先导油路（d1）控制所述顺序阀（k2）动作使得所述控制单元在所述初始转态和所述负载状态间切换，所述第二先导油路（d2）控制所述减压阀（k1）动作以控制所述P口的输入流量。
  2. 根据权利要求1所述的控制单元，其中，所述第一先导油路（d1）的两端分别连接所述顺序阀（k2）的控制端和所述卸荷阻尼（k3）的进口，
    和/或，所述第二先导油路（d2）的两端分别连接所述减压阀（k1）的控制端和所述卸荷阻尼（k3）的进口。
  3. 根据权利要求1或2所述的控制单元，其中，所述减压阀（k1）的外壳和所述顺序阀（k2）的外壳为一体结构的阀体（1），所述P口、所述T口及所述B口形成在所述阀体（1）上。
  4. 根据权利要求3所述的控制单元，其中，所述减压阀（k1）的阀芯和所述顺序阀（k2）的阀芯为一体结构的总阀芯（2），所述卸荷阻尼（k3）形成在所述总阀芯（2）上，所述阀体（1）内具有阀体腔（10），所述总阀芯（2）滑动设置在所述阀体腔（10）内，所述P口、所述T口及所述B口穿透所述阀体（1）的壁并连通所述阀体腔（10）。
  5. 根据权利要求4所述的控制单元，其中，所述总阀芯（2）上设置有轴向延伸的中心油道（2a），所述卸荷阻尼（k3）包括穿透所述总阀芯（2）的壁并贯通所述中心油道（2a）的阻尼孔（2b），所述总阀芯（2）上还设置有贯通所述总阀芯（2）的壁并连通所述中心油道（2a）的压力油口（2c）：
    在所述初始状态，所述P口通过所述压力油口（2c）及所述中心油道（2a）再通过所述阻尼孔（2b）后同时连通所述T口和所述B口。
  6. 根据权利要求5所述的控制单元，其中，所述总阀芯（2）上形成有贯通所述总阀芯（2）的壁并连通所述中心油道（2a）的先导油孔（2d），
    在所述负载状态，所述阻尼孔（2b）与所述B口断开，所述P口和所述B口连通，其中，从P口输送的压力油经所述压力油口（2c）沿所述中心油道（2a）通往所述先导油孔（2d）形成所述第一先导油路（d1），在所述第一先导油路（d1）的作用下所述总阀芯（2）能够移动使得所述先导油孔（2d）与所述B口连通实现所述控制单元从初始状态向负载状态切换。
  7. 一种液压系统，其中，所述液压系统包括权利要求1-6中任意一项所述控制单元和执行单元，所述B口通往所述执行单元。
  8. 根据权利要求7所述的液压系统，其中，所述执行单元包括马达（7）和制动所述马达（7）的制动器（6），所述B口通往所述制动器（6）的制动缸，所述液压系统还包括第一管路（g1）和第二管路（g2），所述马达（7）具有两个油口，其一者通过所述第一管路（g1）连接第一主压力口（A’），其另一者通过所述第二管路（g2）连接第二主压力油口（B’），所述P口连通所述第一管路（g1）和所述第二管路（g2）中的高压者。
  9. 根据权利要求8所述的液压系统，其中，所述液压系统还包括平衡阀（k5），所述平衡阀（k5）安装在所述第一管路（g1）和所述第二管路（g2）中其一者上，所述平衡阀（k5）的控制端连接其另一者。
  10. 一种作业机械，其中，所述作业机械包括权利要求1-9中任意一项所述的液压系统。
PCT/CN2023/129962 2023-01-31 2023-11-06 控制单元和液压系统及作业机械 Ceased WO2024159846A1 (zh)

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