CN108561352B - Prefill valve and mining dump truck hydraulic system - Google Patents

Prefill valve and mining dump truck hydraulic system Download PDF

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Publication number
CN108561352B
CN108561352B CN201810311113.1A CN201810311113A CN108561352B CN 108561352 B CN108561352 B CN 108561352B CN 201810311113 A CN201810311113 A CN 201810311113A CN 108561352 B CN108561352 B CN 108561352B
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oil
valve
hydraulic
port
lifting
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CN108561352A (en
Inventor
杨胜清
王素燕
李茜
唐绪文
唐云娟
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Guangxi Liugong Machinery Co Ltd
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Guangxi Liugong Machinery Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/165—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for adjusting the pump output or bypass in response to demand
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/027—Installations or systems with accumulators having accumulator charging devices
    • 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
    • F15B13/027—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
    • F15B2013/002—Modular valves, i.e. consisting of an assembly of interchangeable components
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/86—Control during or prevention of abnormal conditions
    • F15B2211/8606—Control during or prevention of abnormal conditions the abnormal condition being a shock

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

The invention relates to a hydraulic system of a mining dump truck, which aims to solve the problems of large impact and high failure rate of a constant-pressure variable system lifting system on the existing mining dump truck; the hydraulic system of the mining dump truck is provided, and comprises a liquid filling valve, an LS pressure control valve, a second hydraulic control switch valve and an electromagnetic directional valve; the quantitative pump fills liquid into the energy accumulator and supplies oil to the lifting valve through the liquid filling valve, the load sensitive pump supplies oil to the steering system and supplies oil to the lifting valve through the second hydraulic control switch valve during lifting, and the electromagnetic directional valve controls the second hydraulic control switch valve to cut off the oil supply of the load sensitive pump to the lifting valve when the lifting oil cylinder extends to the lifting stroke end position. The hydraulic system has the advantages of simple structure, good controllability of a steering system and effective control of stroke end point impact of the lifting system.

Description

Prefill valve and mining dump truck hydraulic system
Technical Field
The invention relates to a hydraulic technology, in particular to a prefill valve and a hydraulic system of a mining dump truck.
Background
The existing variable hydraulic system of the mining dump truck generally comprises a load sensitive system and a constant pressure variable system, wherein a variable part is generally used for a steering system, and a lifting system is a quantitative system. The lifting hydraulic system is usually composed of elements such as a lifting pump, a lifting valve, a balance valve, a pilot valve (or an electromagnetic handle), a multistage cylinder and the like, and the steering hydraulic system is usually composed of elements such as a steering pump, a steering control unit, an energy accumulator, a steering cylinder and the like. The brake system consists of brake valve, brake clamp, accumulator and other elements. At present, mine cars of most manufacturers adopt a constant-pressure variable system.
The typical constant pressure variable system has some technical defects:
(1) the lifting system is complex to control, the lifting part adopts a mode of combining electro-hydraulic control, the control valve and the main valve are relatively complex, the number of elements is large, and the failure rate is high.
(2) The constant pressure pump supplements oil for the energy accumulator in real time, the swash plate of the pump moves frequently, and the service life of the pump can be influenced to a certain extent.
(3) Because the steering system is supplied with oil by the energy accumulator, and an EF port of the flow amplifying valve is blocked, the steering controllability is poor.
(4) The lifting system has no hydraulic limit and only adopts mechanical limit, and the stroke end point of the oil cylinder has large impact.
(5) Because the lifting pilot system adopts a control mode of an electromagnetic directional valve, the starting impact of the lifting system is large.
Disclosure of Invention
The invention aims to solve the technical problems that a constant-pressure variable system on the existing mining dump truck has large impact and high failure rate, and provides a prefill valve and a mining dump truck hydraulic system.
The technical scheme for realizing the purpose of the invention is as follows: the charging valve is characterized by comprising an XP oil port, a C oil port, a D oil port, an E oil port, an F oil port, an oil return port and an X2 oil port which are used for being connected with an external oil path, and further comprising a first one-way valve, a second one-way valve, a charging switch valve, an unloading valve and a hydraulic control switch valve;
the oil inlet end of the second one-way valve is connected with the oil port D, and the oil outlet end of the first one-way valve is connected with the oil port F; the oil inlet end and the XP oil port of the first one-way valve are both connected with the oil outlet end of the second one-way valve;
the hydraulic control switch valve is connected between the oil port C and the oil outlet end of the second one-way valve, and the hydraulic control end of the hydraulic control switch valve is connected with the oil port X2;
the oil inlet end and the control end of the liquid filling switch valve are both connected with the oil port D, the spring cavity of the liquid filling switch valve is connected with the oil inlet end through a damping hole, and the oil outlet end of the liquid filling switch valve is connected with the oil port E;
the oil inlet end of the unloading valve is connected with the spring cavity of the liquid filling switch valve, the control end of the unloading valve is connected with the oil outlet end of the second one-way valve, and the oil outlet end of the unloading valve is connected with the oil return port.
Furthermore, in the liquid filling valve, an oil drain valve and/or an overflow valve are also arranged between the XP oil port and the oil return port. When the oil drain valve and the overflow valve are arranged, the oil drain valve and the overflow valve are connected between the XP oil port and the oil return port in parallel.
Furthermore, in the liquid filling valve, the oil drain valve comprises an electromagnetic switch valve and/or a manual switch valve which are connected between the XP oil port and the oil return port.
The technical scheme for realizing the purpose of the invention is as follows: the hydraulic system of the mining dump truck comprises a hydraulic braking system, a hydraulic steering control mechanism, a steering oil cylinder, a hydraulic lifting control mechanism, a lifting oil cylinder, a load sensitive pump, a constant delivery pump, an energy accumulator and a hydraulic oil tank, wherein the steering oil cylinder and the hydraulic lifting control mechanism are connected with the hydraulic steering control mechanism; the hydraulic steering control mechanism comprises a flow amplification valve connected with the steering oil cylinder and a steering gear connected with the flow amplification valve; the hydraulic lifting control mechanism comprises a lifting valve connected with a lifting oil cylinder and a pilot valve connected with the lifting valve; oil inlets of the fixed displacement pump and the load sensitive pump are connected with a hydraulic oil tank; the hydraulic control system is characterized by also comprising the liquid filling valve, an LS pressure control valve, a second hydraulic control switch valve and an electromagnetic directional valve;
an oil return port of the liquid charging valve is connected with a hydraulic oil tank, an oil port F is connected with an oil inlet end of brake pressure oil of a hydraulic brake system, an oil port XP is connected with an energy accumulator, an oil port E is connected with a pressure oil inlet of the lifting valve, an oil port D is connected with an oil outlet of the fixed displacement pump, and an oil port C and an oil outlet of the load sensitive pump are connected with a pressure oil inlet of the flow amplifying valve;
an oil inlet of the second hydraulic switch valve is connected with an oil outlet of the load sensitive pump, an oil outlet of the second hydraulic switch valve is connected with a pressure oil inlet of the lifting valve, a hydraulic control end oil port of the second hydraulic switch valve, a hydraulic control end of the LS pressure control valve and a lifting pilot control end of the lifting valve are connected with each other and then connected with a lifting pilot output end of the pilot valve through the electromagnetic directional valve, and when the hydraulic control end oil port of the second hydraulic switch valve has a pilot pressure signal, the oil inlet and the oil outlet of the second hydraulic switch valve are communicated;
an oil port a of the LS pressure control valve is simultaneously connected with an X2 oil port of the liquid charging valve and a pump port pressure signal interface of the load sensitive pump, an oil port b of the LS pressure control valve is connected with an oil port LS2 of a steering gear, an oil port c of the LS pressure control valve is connected with an oil port LS1 of the load sensitive pump, an oil port d of the LS pressure control valve is connected with a hydraulic oil tank, when a pilot pressure signal is provided at a hydraulic control end of the LS pressure control valve, the oil port a is communicated with the oil port c, when the pilot pressure signal is not provided at the hydraulic control end of the LS pressure control valve, the oil port b is communicated with the oil port c, and the oil port a is cut off;
when the lifting oil cylinder is close to the lifting stroke end position, the electromagnetic directional valve is at a stop position; and when the pump port pressure signal interface of the load-sensitive pump has pressure output, the hydraulic control switch valve is in a stop position.
Further, in the hydraulic system of the mining dump truck, the second hydraulic switch valve comprises a hydraulic control reversing valve and a cartridge switch valve, a hydraulic control end of the hydraulic control reversing valve is connected with a hydraulic control end oil port, an oil port a of the hydraulic control reversing valve and an oil inlet end of the cartridge switch valve are both connected with an oil inlet, an oil port b of the hydraulic control reversing valve is connected with an oil return port of the hydraulic control switch valve connected with a hydraulic oil tank, an oil port c of the hydraulic control reversing valve is connected with a hydraulic control end of the cartridge switch valve, and an oil outlet end of the cartridge switch valve is connected with an oil outlet; when the pilot pressure signal is not generated in the hydraulic control oil port, the oil port a of the hydraulic control reversing valve is communicated with the oil port c, and the oil port a of the cartridge switch valve is closed.
Further, in the hydraulic system of the mining dump truck, the electromagnetic directional valve is provided with an oil inlet, an oil outlet and an oil return port, the oil inlet is connected with the lifting pilot output end of the pilot valve, the oil outlet is simultaneously connected with a hydraulic control port of the second hydraulic control switch valve, a hydraulic control end of the LS pressure control valve and a lifting pilot control end of the lifting valve, the oil return port is connected with the hydraulic oil tank, and when the electromagnetic directional valve is at a stopping position, the oil outlet is communicated with the oil return port.
Further, the hydraulic system of the mining dump truck further comprises a pilot oil source valve, an oil inlet of the pilot oil source valve is connected with an XP oil port of the liquid filling valve, and an oil outlet of the pilot oil source valve is connected with an oil inlet of the pilot valve.
Further, in the hydraulic system of the mining dump truck, the surplus flow oil outlet of the flow amplifying valve is connected with the oil inlet of the lifting valve.
The technical scheme for realizing the purpose of the invention is as follows: a hydraulic system of a mining dump truck comprises a hydraulic braking system, a hydraulic steering control mechanism, a steering oil cylinder connected with the hydraulic steering control mechanism, a hydraulic lifting control mechanism, a lifting oil cylinder connected with the hydraulic lifting control mechanism, a load sensitive pump, a constant delivery pump, an energy accumulator and a hydraulic oil tank; the hydraulic steering control mechanism comprises a flow amplification valve connected with the steering oil cylinder and a steering gear connected with the flow amplification valve; the hydraulic lifting control mechanism comprises a lifting valve connected with a lifting oil cylinder and a pilot valve connected with the lifting valve; oil inlets of the fixed displacement pump and the load sensitive pump are connected with a hydraulic oil tank; the hydraulic control system is characterized by also comprising the liquid filling valve, an LS pressure control valve and an electromagnetic reversing valve; an oil return port of the liquid charging valve is connected with a hydraulic oil tank, an oil port F is connected with an oil inlet end of brake pressure oil of a hydraulic brake system, an oil port XP is connected with an energy accumulator, an oil port E is connected with a pressure oil inlet of the lifting valve, an oil port D is connected with an oil outlet of the fixed displacement pump, and an oil port C and an oil outlet of the load sensitive pump are connected with a pressure oil inlet P3 port of the flow amplifying valve; the hydraulic control end of the LS pressure control valve and the lifting pilot control end of the lifting valve are connected with each other and then connected with the lifting pilot output end of the pilot valve through the electromagnetic directional valve; an oil port a of the LS pressure control valve is connected with an oil port X2 of the liquid charging valve and a pump port pressure signal interface X12 of the load sensitive pump at the same time, an oil port b of the LS pressure control valve is connected with an oil port LS2 of a steering gear, an oil port c of the LS pressure control valve is connected with an oil port LS1 of the load sensitive pump, an oil port d of the LS pressure control valve is connected with a hydraulic oil tank, when a pilot pressure signal is provided at a pilot control end of the LS pressure control valve, the oil port a is communicated with the oil port c, and when the pilot pressure signal is not provided at the pilot control end of the LS pressure control valve, the oil port b is communicated with the oil port c, and the oil port a is cut off; when the lifting oil cylinder is close to the lifting stroke end position, the electromagnetic directional valve is at a stop position; when a pump port pressure signal interface of the load-sensitive pump has pressure output, the hydraulic control switch valve is at a stop position; and a surplus flow oil outlet of the flow amplifying valve is connected with an oil inlet of the lifting valve. The electromagnetic reversing valve is provided with an oil inlet, an oil outlet and an oil return port, the oil inlet is connected with the lifting pilot output end of the pilot valve, the oil outlet is simultaneously connected with the hydraulic control end of the LS pressure control valve and the lifting pilot control end of the lifting valve, the oil return port is connected with the hydraulic oil tank, and when the electromagnetic reversing valve is at a stopping position, the oil outlet is communicated with the oil return port. The oil inlet of the pilot oil source valve is connected with the XP oil port of the liquid filling valve, and the oil outlet of the pilot oil source valve is connected with the oil inlet of the pilot valve.
Compared with the prior art, the invention has the following advantages:
(1) the liquid charging valve is an integrated valve group and controls the liquid charging state of the steering accumulator, when the pressure of the accumulator is lower than a set lower limit value, the quantitative pump automatically charges the accumulator, and when the pressure of the accumulator reaches the set upper limit value, the liquid charging of the accumulator is automatically cut off.
(2) The steering system is a load sensitive system, the energy accumulator has the functions of supplying oil to the braking system on one hand and supplying oil to the steering system as an emergency oil source on the other hand, and if the load sensitive pump fails to supply oil to the steering system, oil of the energy accumulator is automatically supplied to the steering system. The energy accumulator supplies oil to the brake system at the same time, so that the brake energy accumulator can be omitted, the cost is reduced, and the complexity of the system is reduced.
(3) The flow of the steering pump is matched with the requirement of a steering system under the driving working condition of the load sensitive pump; during a lift condition, the load sensitive pump supplies the lift system at maximum displacement.
(4) The method is characterized in that the impact of the stroke end point of the lifting oil cylinder is reduced by adopting an electro-hydraulic combination mode, when the lifting oil cylinder reaches a specified stroke, the load sensitive pump immediately cuts off oil supplied to a lifting system, then the lifting valve rod returns to the middle position, finally the oil supplied to the lifting oil cylinder is stopped by the oil of the lifting pump, and the impact is reduced by buffering time at the end point of the lifting oil cylinder.
Drawings
FIG. 1 is a schematic diagram of a hydraulic system of a mining dump truck.
FIG. 2 is a schematic diagram of a prefill valve.
Fig. 3 is a schematic diagram of a second hydraulic switching valve.
Part names and serial numbers in the figure:
the hydraulic control system comprises a fixed displacement pump 1, a load sensitive pump 2, a second hydraulic control switch valve 3, an LS pressure control valve 4, a liquid charging valve 5, a hydraulic oil tank 6, an energy accumulator 7, a steering gear 8, a flow amplifying valve 9, a steering oil cylinder 10, a pilot oil source valve 11, an electromagnetic directional valve 12, a pilot valve 13, a lifting oil cylinder 14, a balance valve 15, a lifting valve 16 and a braking system 17.
A liquid charging switch valve 51, an unloading valve 52, a manual switch valve 53, an overflow valve 54, an electromagnetic switch valve 55, a first check valve 56, a hydraulic control switch valve 57 and a second check valve 58.
A pilot operated directional control valve 31 and a cartridge switching valve 32.
Detailed Description
The following description of the embodiments refers to the accompanying drawings.
The schematic diagram of the hydraulic system of the mining dump truck in this embodiment is shown in fig. 1, and includes a hydraulic braking system 17, a hydraulic steering control mechanism and a steering cylinder 10 connected thereto, a hydraulic lifting control mechanism and a lifting cylinder 14 connected thereto, a load-sensitive pump 2, a fixed displacement pump 1, an energy accumulator 7, a hydraulic oil tank 6, a charging valve 5, an LS pressure control valve 4, a second hydraulic switch valve 3, an electromagnetic directional valve 12, and a pilot oil source valve 11. The constant delivery pump 1 is a gear pump. An oil inlet S2 of the fixed displacement pump 1 and an oil inlet S1 of the load sensitive pump 2 are both connected with a hydraulic oil tank.
The hydraulic steering control mechanism includes a flow amplification valve 9 connected to a steering cylinder 10 and a steering gear 8 connected to the flow amplification valve 9.
The hydraulic lift control mechanism includes a lift valve 16 connected to a lift cylinder 14 and a pilot valve 13 connected to the lift valve 16, and a balance valve 15 is provided between the lift valve 16 and the lift cylinder 14.
The charging valve 5 is an integrated valve, and has the principle as shown in fig. 2, and includes an XP port, a C port, a D port, an E port, an F port, an oil return port T1, and an X2 port for connecting with an external oil passage, and includes a first check valve 56, a second check valve 58, a charging switch valve 51, an unloading valve 52, an overflow valve 54, a pilot-controlled switch valve 57, an electromagnetic switch valve 55, and a manual switch valve 53.
The oil inlet end of the second check valve 58 is connected with the oil port D, and the oil outlet end of the first check valve 56 is connected with the oil port F; the oil inlet and the XP port of the first check valve 56 are both connected to the oil outlet of the second check valve 58.
The pilot-controlled switch valve 57 is connected between the port C and the outlet end of the second check valve 58, and the pilot-controlled end of the pilot-controlled switch valve 57 is connected with the port X2. When the pressure of the X2 oil port is greater than the pressure of the spring cavity of the pilot-operated switching valve 57, the pilot-operated switching valve 57 is in a cut-off state, and when the pressure of the X2 oil port is less than the pressure of the spring cavity of the pilot-operated switching valve, the pilot-operated switching valve 57 is in a turned-on state.
The oil inlet end and the control end of the liquid filling switch valve 51 are both connected with the D oil port, the spring cavity of the liquid filling switch valve 51 is connected with the oil inlet end of the liquid filling switch valve 51 through a damping hole, and the oil outlet end of the liquid filling switch valve 51 is connected with the E oil port.
The oil inlet end of the unloading valve 52 is connected with the spring cavity of the liquid charging switch valve 51, the control end of the unloading valve 52 is connected with the oil outlet end of the second one-way valve 58, and the oil outlet end of the unloading valve 52 is connected with the oil return port T1.
The overflow valve 54, the electromagnetic switch valve 55 and the manual switch valve 53 are connected in parallel and are connected between the XP oil port and the oil return port T1. The electromagnetic switch valve 55 and the manual switch valve 53 are used for discharging oil and releasing pressure to the energy accumulator 7 when necessary, one or both of the electromagnetic switch valve 55 and the manual switch valve 53 can be set, and electric control oil discharge or manual oil discharge is correspondingly realized. The relief valve 54 functions as a relief valve to prevent the pressure in the accumulator 7 from exceeding a set value.
The second hydraulic switching valve 3 is also an integrated valve, and as shown in fig. 3, has a hydraulic port X5 for connection with an external oil passage, an oil inlet P8, an oil outlet P9, and an oil return port T5. The second hydraulic control switch valve 3 comprises a hydraulic control reversing valve 31 and an insert switch valve 32, a hydraulic control end of the hydraulic control reversing valve 31 is connected with a hydraulic control end oil port X5, an oil port a of the hydraulic control reversing valve and an oil inlet end a of the insert switch valve 32 are both connected with an oil inlet P8, an oil port b of the hydraulic control reversing valve is connected with an oil return port T5, an oil port c of the hydraulic control reversing valve is connected with a hydraulic control end c of the insert switch valve 32, and an oil outlet end b of the insert switch valve 32 is connected with an oil outlet P9; when the pilot pressure signal is provided to the pilot oil port X5, the pilot-operated directional control valve is in the left position, the oil port b of the pilot-operated directional control valve is connected to the oil port c of the pilot-operated directional control valve, the oil port a of the pilot-operated directional control valve is cut off, and the oil inlet end a of the cartridge switch valve 32 is connected to the oil outlet end b, so that the connection between the oil inlet P8 and the oil outlet P9 of the second pilot-operated switch valve 3 is realized. When the pilot pressure signal does not exist in the pilot oil port X5, the pilot reversing valve is in the right position, the oil port a and the oil port c are connected, the oil inlet end a and the oil outlet end b of the cartridge switch valve 32 are cut off, that is, the space between the oil inlet P8 and the oil outlet P9 of the second pilot switch valve 3 is cut off.
As shown in fig. 1, the electromagnetic directional valve 12 has an oil inlet P15, an oil outlet P14, and an oil return port T11, the oil inlet P15 is connected to the lifting pilot output end X6 of the pilot valve 13, the oil outlet P14 is simultaneously connected to the hydraulic control port X5 of the second hydraulic switch valve 3, the hydraulic control port X3 of the LS pressure control valve 4, and the lifting pilot control port Xa1 of the lifting valve 16, the oil return port T11 is connected to the hydraulic oil tank 6, and when the electromagnetic directional valve 12 is at the stop position, the oil outlet P14 is connected to the oil return port T11. The on and off of the electromagnetic directional valve 12 are related to the stroke of the lifting oil cylinder 14, when the lifting oil cylinder 14 extends to the end position of the lifting stroke, a control system of the mining dump truck detects the signal and then enables the electromagnetic directional valve 12 to be in the off position, otherwise, the electromagnetic directional valve is in the on position.
The LS pressure control valve 4 is a two-position four-way valve, and four oil ports of the LS pressure control valve are respectively an oil port a, an oil port b, an oil port c and an oil port d. The oil port a of the LS pressure control valve 4 is connected with the oil port X2 of the liquid charging valve 5 and the pump port pressure signal interface X12 of the load sensitive pump 2, the oil port b of the LS pressure control valve 4 is connected with the oil port LS2 of the steering gear 8, the oil port c of the LS pressure control valve 4 is connected with the oil port LS1 of the load sensitive pump 2, the oil port d of the LS pressure control valve 4 is connected with the hydraulic oil tank 6, when the hydraulic control end X3 of the LS pressure control valve 4 has a pilot pressure signal, the oil port a and the oil port c of the LS pressure control valve 4 are communicated, the oil port b and the oil port d are communicated, the pump port pressure signal interface X12 of the load sensitive pump 2 transmits the pump port pressure signal of the load sensitive pump 2 to the oil port LS1 of the load sensitive pump 2, so that the load sensitive pump becomes a fixed displacement pump which supplies oil outwards (supplies oil to the hydraulic lifting system). When the pilot pressure signal does not exist at the pilot control end X3 of the LS pressure control valve 4, the oil port b and the oil port c are communicated, the oil port a is closed, the load pressure signal of the LS2 oil port of the steering gear 8 is transmitted to the LS1 oil port of the load sensitive pump 2 through the LS pressure control valve 4, and the load sensitive pump 2 outputs corresponding flow according to the load pressure to supply oil to the hydraulic steering system.
As shown in fig. 1, an oil return port T1 of the prefill valve 5 is connected to the hydraulic oil tank 6, an oil port F is connected to an oil inlet end of brake pressure oil of the hydraulic brake system 17 to supply oil to the brake system 17, an oil port E is connected to a pressure oil inlet P4 of the lift valve 16, an oil port D is connected to an oil outlet P2 of the fixed displacement pump 1, and both the oil port C and an oil outlet P1 of the load sensing pump 2 are connected to a pressure oil inlet P3 of the flow amplifying valve 9. The XP oil port is led out of the XP1 oil port, the XP2 oil port, the XP3 oil port, the XP4 oil port, the X1 oil port and the like, wherein the XP1 oil port and the XP2 oil port are correspondingly connected with the two accumulators 7, the XP3 oil port is connected with the pressure switch, and the XP4 oil port is connected with the pressure gauge.
The surplus flow outlet P13 of the flow amplifying valve 9 is connected with the inlet P4 of the lifting valve 16. An oil inlet P5 of the pilot oil source valve 11 is connected with a branch interface X1 oil port of an XP oil port of the liquid charging valve 5, an oil outlet P6 of the pilot oil source valve 11 is connected with an oil inlet P7 of the pilot valve 13, and the pilot valve 13 is provided with a pressure oil source through the energy accumulator 7 and the fixed displacement pump.
An oil inlet P8 of the second hydraulic switch valve 3 is connected with an oil outlet P1 of the load sensitive pump 2, an oil outlet P9 of the second hydraulic switch valve 3 is connected with a pressure oil inlet P4 of the lifting valve 16, a hydraulic control port X5 of the second hydraulic switch valve 3 is connected with an oil outlet P14 of the electromagnetic directional valve 12, and an oil return port T5 is connected with the hydraulic oil tank 6.
In this embodiment, when each component normally works, the oil outlet P2 of the fixed displacement pump supplies oil to the oil port D of the oil filling valve 5, and the hydraulic control switch valve 57 is at the cut-off position by the pressure signal output by the pump port pressure signal interface X12 of the load sensitive pump 2. If the pressure in the accumulator 7 is lower than the predetermined value (lower than the opening pressure of the unloading valve 52), the pressure of the spring cavity of the charging switch valve 51 is equal to that of the control end, the charging switch valve 51 is in a closed state, and the high-pressure oil output by the fixed displacement pump 1 is charged into the accumulator 7 through the second check valve 58, the XP1 oil port and the XP2 oil port, so that energy is stored, and oil supply to a brake system and a pilot valve and oil supply to a hydraulic steering system during emergency steering are realized. When the pressure of the accumulator 7 is higher than a predetermined value (higher than the opening pressure of the unloading valve 52), the unloading valve 52 is opened, the hydraulic oil in the spring cavity of the liquid charging switch valve 51 flows to the hydraulic oil tank 6 through the unloading valve 52, so that the pressure in the spring cavity of the liquid charging switch valve 51 is smaller than the pressure at the control end, the liquid charging switch valve 51 is opened, the hydraulic oil output by the fixed displacement pump 1 flows to the lifting valve 16 through the port D of the liquid charging valve 5, the liquid charging switch valve 51 and the port E, and is unloaded through the middle position of the lifting valve 16 or used for the lifting action of the lifting cylinder 14.
When the mining dump truck performs steering action, at the moment, the hydraulic lifting system does not work, no pilot pressure is output from a lifting pilot output end X6 of the pilot valve 13, the LS pressure control valve 4 is in the left position, an oil port b of the LS pressure control valve is communicated with an oil port c of the LS pressure control valve, a load pressure signal of an oil port LS2 of the steering gear 8 is transmitted to an oil port LS1 of the load sensitive pump 2 through the LS pressure control valve 4, the load sensitive pump 2 outputs corresponding flow according to the load pressure signal of the steering gear 8, oil is supplied to the hydraulic steering system from a pressure oil inlet P3 of the flow amplifying valve 9, steering surplus flow flows to the lifting valve 16 from a surplus flow oil outlet P13 of the flow amplifying valve 9, and flows to the hydraulic oil tank 6 from the middle position of.
When the mining dump truck performs lifting action, no steering action is performed at the moment, and the lifting pilot output end X6 of the pilot valve 13 outputs pilot pressure. The pilot pressure output by the lifting pilot output end X6 of the pilot valve acts on a pilot control oil port X5 of the second hydraulic control switch valve 3 to enable an oil inlet P8 and an oil outlet P9 of the second hydraulic control switch valve 3 to be communicated; the pilot pressure output by the lifting pilot output end X6 of the pilot valve 13 acts on the control end of the LS pressure control valve 4 to enable the LS pressure control valve 4 to be in the right position, the oil port a of the LS pressure control valve is communicated with the oil port c, and the pressure output by the pump port pressure signal interface X12 of the load sensitive pump 2 is transmitted to the LS1 oil port of the load sensitive pump 2 through the LS pressure control valve 4, so that the load sensitive pump 2 works in a fixed displacement pump and outputs hydraulic oil according to the maximum displacement value of the load sensitive pump; the pilot pressure output from the lift pilot output terminal X6 of the pilot valve 13 acts on the lift pilot control terminal Xa1 of the lift valve 16 to lift the lift cylinder 14. Most of the hydraulic oil output by the load sensitive pump 2 at the maximum displacement passes through the second hydraulic switch valve 3, and a small part of the hydraulic oil passes through the priority valve and the surplus flow oil outlet P13 in the flow amplifying valve 9, the two oil paths flow to the lifting valve 16 after being converged, and the hydraulic oil output by the fixed displacement pump 1 also supplies oil to the lifting valve 16 after being converged by the hydraulic oil port D and the hydraulic oil output by the load sensitive pump 2 through the oil port E of the liquid filling valve 5, so that the lifting oil cylinder 14 is quickly lifted. When the lifting oil cylinder 14 extends to the end position of the lifting stroke, an electromagnet of the electromagnetic directional valve 12 receives a set displacement signal of the lifting oil cylinder 14 to be electrified, the electromagnetic directional valve 12 is switched to the right position, an oil outlet P14 of the electromagnetic directional valve is communicated with an oil return port T11 and is connected with the hydraulic oil tank 6, the second hydraulic switch valve 3 cuts off oil supplied to the lifting valve 16 by the load-sensitive pump 2, then a valve rod of the lifting valve 16 returns to the middle position, finally the oil of the constant delivery pump 1 is stopped to be supplied to the lifting oil cylinder 14, and a buffer time is reserved at the end point of the lifting oil cylinder 14 to reduce impact.
When the mining dump truck has a power failure, for example, an engine is stopped due to a failure, the fixed displacement pump 1 and the load sensitive pump 2 cannot output hydraulic oil at the moment, the pressure of a pump port pressure signal interface X12 of the load sensitive pump 2 is zero, the hydraulic control switch valve 57 is in the left position, the hydraulic oil in the energy accumulator 7 is supplied to the hydraulic steering system through the hydraulic control switch valve 57 and the C oil port, and is supplied to the braking system 17 through the first check valve 56 and the F oil port, so that the hydraulic steering and braking system is supplied with oil in an emergency.
In the above embodiment, during the lifting operation, the hydraulic oil output by the load-sensitive pump 2 is supplied to the lifting valve 16 through the second pilot-controlled switch valve 3 and the surplus flow outlet P13 of the flow amplifying valve 9. During specific implementation, according to design requirements in a hydraulic system of the mining dump truck, only one path of oil way can be designed, namely the second hydraulic switch valve 3 is omitted, and hydraulic oil output by the load sensitive pump 2 flows to the lifting valve through the surplus flow outlet P13 of the flow amplifying valve 9 during lifting. The design of an oil path from the surplus flow outlet P13 of the flow amplifying valve to the lifting valve 16 can be omitted, and the hydraulic oil output by the load sensitive pump 2 only flows to the lifting valve 16 through the second hydraulic switch valve 3 during lifting.

Claims (10)

1. A liquid charging valve is characterized by comprising an XP oil port, a C oil port, a D oil port, an E oil port, an F oil port, an oil return port T1 and an X2 oil port which are used for being connected with an external oil path, and the liquid charging valve comprises a first one-way valve (56), a second one-way valve (58), a liquid charging switch valve (51), an unloading valve (52) and a hydraulic control switch valve (57);
the oil inlet end of the second check valve (58) is connected with the oil port D, and the oil outlet end of the first check valve is connected with the oil port F; the oil inlet end and the XP oil port of the first one-way valve are both connected with the oil outlet end of the second one-way valve;
the hydraulic control switch valve (57) is connected between the oil outlet end of the second check valve and the oil outlet end of the C oil port, and the hydraulic control end of the hydraulic control switch valve is connected with the oil port X2;
the oil inlet end and the control end of the liquid filling switch valve (51) are both connected with the oil port D, the spring cavity of the liquid filling switch valve is connected with the oil inlet end of the liquid filling switch valve through a damping hole, and the oil outlet end of the liquid filling switch valve is connected with the oil port E;
the oil inlet end of the unloading valve (52) is connected with the spring cavity of the liquid charging switch valve, the control end of the unloading valve is connected with the oil outlet end of the second one-way valve, and the oil outlet end of the unloading valve is connected with the oil return port T1.
2. The charging valve according to claim 1, characterized in that an oil drain valve and/or an overflow valve are/is further arranged between the XP oil port and the oil return port T1.
3. The charging valve according to claim 2, characterized in that the oil drain valve comprises an electromagnetic switch valve and/or a manual switch valve connected between a XP oil port and an oil return port T1.
4. A hydraulic system of a mining dump truck comprises a hydraulic braking system, a hydraulic steering control mechanism, a steering oil cylinder connected with the hydraulic steering control mechanism, a hydraulic lifting control mechanism, a lifting oil cylinder connected with the hydraulic lifting control mechanism, a load sensitive pump, a constant delivery pump, an energy accumulator and a hydraulic oil tank; the hydraulic steering control mechanism comprises a flow amplification valve connected with the steering oil cylinder and a steering gear connected with the flow amplification valve; the hydraulic lifting control mechanism comprises a lifting valve connected with a lifting oil cylinder and a pilot valve connected with the lifting valve; oil inlets of the fixed displacement pump and the load sensitive pump are connected with a hydraulic oil tank; characterized by further comprising the liquid charging valve as claimed in any one of claims 1 to 3, and an LS pressure control valve (4), a second hydraulic switch valve (3) and a solenoid directional valve (12);
an oil return port T1 of the liquid charging valve is connected with a hydraulic oil tank, an oil port F is connected with the oil inlet end of brake pressure oil of a hydraulic brake system, an oil port XP is connected with an energy accumulator, an oil port E is connected with a pressure oil inlet P4 of the lifting valve, an oil port D is connected with the oil outlet of the fixed displacement pump, and an oil port C and the oil outlet of the load sensitive pump are both connected with a pressure oil inlet P3 of the flow amplifying valve;
an oil inlet P8 of the second hydraulic switch valve (3) is connected with an oil outlet P1 of the load-sensitive pump, an oil outlet P9 of the second hydraulic switch valve (3) is connected with a pressure oil inlet P4 of the lifting valve, a hydraulic control oil port X5 of the second hydraulic switch valve (3), a hydraulic control end X3 of the LS pressure control valve and a lifting pilot control end Xa1 of the lifting valve are connected with a lifting pilot output end X6 of the pilot valve through the electromagnetic directional valve (12) after being connected with each other, and when the hydraulic control oil port X5 of the second hydraulic switch valve (3) has a pilot pressure signal, an oil inlet P8 of the second hydraulic switch valve (3) is communicated with the oil outlet P9;
an oil port a of the LS pressure control valve is connected with an oil port X2 of the liquid charging valve and a pump port pressure signal interface X12 of the load sensitive pump at the same time, an oil port b of the LS pressure control valve is connected with an oil port LS2 of a steering gear, an oil port c of the LS pressure control valve is connected with an oil port LS1 of the load sensitive pump, an oil port d of the LS pressure control valve is connected with a hydraulic oil tank, when a pilot pressure signal is provided at a pilot control end X3 of the LS pressure control valve, the oil port a is communicated with the oil port c, and when the pilot pressure signal is not provided at the pilot control end of the LS pressure control valve, the oil port b is communicated with the oil port c, and the oil port a is blocked;
when the lifting oil cylinder is close to the lifting stroke end position, the electromagnetic directional valve (12) is in a stop position; the pilot-controlled switch valve (57) is in a cut-off position when the pump port pressure signal interface X12 of the load-sensitive pump has pressure output.
5. The mining dump truck hydraulic system according to claim 4, characterized in that the second hydraulic switch valve (3) comprises a hydraulic control directional control valve (31) and a cartridge switch valve (32), a hydraulic control end of the hydraulic control directional control valve (31) is connected with a hydraulic control end oil port X5, an oil port a of the hydraulic control directional control valve and an oil inlet end of the cartridge switch valve (32) are both connected with an oil inlet P8, an oil port b of the hydraulic control directional control valve is connected with an oil return port T5 of the hydraulic control directional control valve connected with a hydraulic oil tank, an oil port c of the hydraulic control directional control valve is connected with the hydraulic control end of the cartridge switch valve, and an oil outlet end of the cartridge switch valve is connected with an oil outlet P9; when the pilot pressure signal is generated at the hydraulic control port X5, the port b and the port c of the hydraulic control reversing valve are communicated, the port a is closed, the oil inlet end and the oil outlet end of the cartridge switch valve are communicated, and when the pilot pressure signal is not generated at the hydraulic control port X5, the port a and the port c of the hydraulic control reversing valve are communicated, and the oil inlet end and the oil outlet end of the cartridge switch valve are closed.
6. The mining dump truck hydraulic system according to claim 4 or 5, characterized in that the electromagnetic directional valve (12) has an oil inlet P15, an oil outlet P14 and an oil return T11, the oil inlet P15 is connected with a lifting pilot output end X6 of a pilot valve, the oil outlet P14 is simultaneously connected with a hydraulic control port X5 of the second hydraulic switch valve (3), a hydraulic control end X3 of the LS pressure control valve and a lifting pilot control end Xa1 of the lifting valve, the oil return T11 is connected with a hydraulic oil tank, and when the electromagnetic directional valve (12) is at the cut-off position, the oil outlet P14 is communicated with the oil return T11.
7. The mining dump truck hydraulic system according to claim 6, characterized in that the mining dump truck hydraulic system further comprises a pilot oil source valve, an oil inlet P5 of the pilot oil source valve is connected with an XP oil port of the liquid charging valve, and an oil outlet P6 of the pilot oil source valve is connected with an oil inlet P7 of the pilot valve.
8. The mining dump truck hydraulic system according to claim 4 or 5, characterized in that the surplus flow oil outlet P13 of the flow amplifying valve is connected with the oil inlet P4 of the lifting valve.
9. A hydraulic system of a mining dump truck comprises a hydraulic braking system, a hydraulic steering control mechanism, a steering oil cylinder connected with the hydraulic steering control mechanism, a hydraulic lifting control mechanism, a lifting oil cylinder connected with the hydraulic lifting control mechanism, a load sensitive pump, a constant delivery pump, an energy accumulator and a hydraulic oil tank; the hydraulic steering control mechanism comprises a flow amplification valve connected with the steering oil cylinder and a steering gear connected with the flow amplification valve; the hydraulic lifting control mechanism comprises a lifting valve connected with a lifting oil cylinder and a pilot valve connected with the lifting valve; oil inlets of the fixed displacement pump and the load sensitive pump are connected with a hydraulic oil tank; characterized by further comprising a charging valve as claimed in any one of claims 1 to 3, and an LS pressure control valve (4) and a solenoid directional valve (12);
an oil return port T1 of the liquid charging valve is connected with a hydraulic oil tank, an oil port F is connected with the oil inlet end of brake pressure oil of a hydraulic brake system, an oil port XP is connected with an energy accumulator, an oil port E is connected with a pressure oil inlet P4 of the lifting valve, an oil port D is connected with the oil outlet of the fixed displacement pump, and an oil port C and the oil outlet of the load sensitive pump are both connected with a pressure oil inlet P3 of the flow amplifying valve;
the hydraulic control end X3 of the LS pressure control valve and the lifting pilot control end Xa1 of the lifting valve are connected with each other and then are connected with the lifting pilot output end X6 of the pilot valve through the electromagnetic directional valve (12);
an oil port a of the LS pressure control valve is connected with an oil port X2 of the liquid charging valve and a pump port pressure signal interface X12 of the load sensitive pump at the same time, an oil port b of the LS pressure control valve is connected with an oil port LS2 of a steering gear, an oil port c of the LS pressure control valve is connected with an oil port LS1 of the load sensitive pump, an oil port d of the LS pressure control valve is connected with a hydraulic oil tank, when a pilot pressure signal is provided at a pilot control end X3 of the LS pressure control valve, the oil port a is communicated with the oil port c, and when the pilot pressure signal is not provided at the pilot control end of the LS pressure control valve, the oil port b is communicated with the oil port c, and the oil port a is blocked;
when the lifting oil cylinder is close to the lifting stroke end position, the electromagnetic directional valve (12) is in a stop position; the hydraulic control switch valve (57) is in a cut-off position when a pump port pressure signal interface X12 of the load-sensitive pump has pressure output; and a surplus flow oil outlet P13 of the flow amplifying valve is connected with an oil inlet P4 of the lifting valve.
10. The mining dump truck hydraulic system according to claim 9, characterized in that the electromagnetic directional valve has an oil inlet P15, an oil outlet P14, and an oil return port T11, the oil inlet P15 is connected with a lifting pilot output end X6 of the pilot valve, the oil outlet P14 is simultaneously connected with a hydraulic control end X3 of the LS pressure control valve and a lifting pilot control end Xa1 of the lifting valve, the oil return port T11 is connected with the hydraulic oil tank, and when the electromagnetic directional valve is at the cut-off position, the oil outlet P14 is communicated with the oil return port T11.
CN201810311113.1A 2018-04-09 2018-04-09 Prefill valve and mining dump truck hydraulic system Active CN108561352B (en)

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