CN114109944A - Hydraulic system of deep ploughing crushing scarifier - Google Patents

Hydraulic system of deep ploughing crushing scarifier Download PDF

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Publication number
CN114109944A
CN114109944A CN202111649366.8A CN202111649366A CN114109944A CN 114109944 A CN114109944 A CN 114109944A CN 202111649366 A CN202111649366 A CN 202111649366A CN 114109944 A CN114109944 A CN 114109944A
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CN
China
Prior art keywords
valve
oil
way
control
steering
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Pending
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CN202111649366.8A
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Chinese (zh)
Inventor
向前
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Sichuan Zhongke Gufeng Agricultural Machinery Co ltd
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Sichuan Zhongke Gufeng Agricultural Machinery Co ltd
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Priority to CN202111649366.8A priority Critical patent/CN114109944A/en
Publication of CN114109944A publication Critical patent/CN114109944A/en
Pending legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • 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
    • F15B11/20—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors controlling several interacting or sequentially-operating members
    • A—HUMAN NECESSITIES
    • A01—AGRICULTURE; FORESTRY; ANIMAL HUSBANDRY; HUNTING; TRAPPING; FISHING
    • A01B—SOIL WORKING IN AGRICULTURE OR FORESTRY; PARTS, DETAILS, OR ACCESSORIES OF AGRICULTURAL MACHINES OR IMPLEMENTS, IN GENERAL
    • A01B71/00—Construction or arrangement of setting or adjusting mechanisms, of implement or tool drive or of power take-off; Means for protecting parts against dust, or the like; Adapting machine elements to or for agricultural purposes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/04—Special measures taken in connection with the properties of the fluid
    • F15B21/041—Removal or measurement of solid or liquid contamination, e.g. filtering
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/04—Special measures taken in connection with the properties of the fluid
    • F15B21/042—Controlling the temperature of the fluid
    • F15B21/0423—Cooling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity

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

Abstract

The invention provides a hydraulic system of a deep ploughing crushing scarifier, which comprises a driving module and an execution module, wherein the driving module comprises more than one execution driving module, the execution driving module is connected with an oil tank, the execution module comprises a crushing and scarifying execution module and a movable execution module, the crushing and scarifying execution module comprises a crushing and scarifying motor oil circuit, a lifting oil cylinder oil circuit, a corner oil cylinder oil circuit and a steering oil cylinder oil circuit, and the lifting oil cylinder oil circuit, the corner oil cylinder oil circuit and the steering oil cylinder oil circuit are connected with the oil tank through oil cylinder hydraulic pump oil circuits, thereby improving the efficiency of the work.

Description

Hydraulic system of deep ploughing crushing scarifier
Technical Field
The invention relates to the technical field of deep ploughing and soil loosening machine control, in particular to a hydraulic system of a deep ploughing and smashing soil loosening machine.
Background
The cultivated land is a basic resource and a condition for human survival, the population is continuously increased in the 21 st century, the cultivated land is gradually reduced, the living standard of people is continuously improved, the quantity and the quality of the cultivated land are firstly ensured for maintaining agricultural sustainable development, and the cultivated land refers to the land for planting crops, including prepared rehmannia root, newly developed land, reclaimed land, prepared land and leisure land; the method mainly comprises the steps of planting crops, and forming a land with sporadic fruit trees, mulberry trees or other trees; on average, the cultivated beach and the shoal can be harvested in one season per year, and the cultivated land comprises fixed ditches, roads and sills with the width of less than 1.0 m in the south and the width of less than 2.0 m in the north; the two-stage classification is paddy field, water-irrigated land and dry land, wherein deep ploughing is the most basic and most important cultivation measure in soil cultivation, and means that before sowing and transplanting, one field needs to be ploughed, deep soil in the field is turned up, shallow soil is covered, the deep ploughing has the largest influence on soil property in the cultivation measure, the action range is wide, the duration is far longer than other measures, other cultivation measures such as raking land and leveling land are carried out on the basis of the measure, the deep ploughing has the effects of soil turning, soil loosening, soil mixing and soil crushing, the yield can be increased obviously through reasonable deep ploughing, deep scarification is carried out mechanically, the plough layer can be loose and soft, the structure is good, the thickness of live soil is thick, and the soil is fertile and level, the solid phase, liquid phase and gas phase proportions are mutually coordinated, and the requirement of action growth is met. Therefore, when deep ploughing and deep scarification are to be performed by a machine, a hydraulic system for controlling and driving the machine is required.
Disclosure of Invention
The invention aims to provide a hydraulic system of a deep ploughing and smashing scarifier.
In order to achieve the purpose, the hydraulic system of the deep ploughing crushing scarifier comprises a driving module and an execution module, wherein the driving module comprises more than one execution driving module, the execution driving module is connected with an oil tank, the execution module comprises a crushing scarifying execution module and a moving execution module, the crushing scarifying execution module comprises a pulverizing loosening motor oil way, a lifting oil cylinder oil way, a corner oil cylinder oil way and a steering oil cylinder oil way, and the lifting oil cylinder oil way, the corner oil cylinder oil way and the steering oil cylinder oil way are connected with the oil tank through oil cylinder hydraulic pump oil ways.
The execution driving module comprises a variable control oil path, a balance oil path, a control valve oil path and an execution hydraulic pump oil path, the execution hydraulic pump oil path is connected with the oil tank, the execution hydraulic pump oil path is further connected with the balance oil path, the balance oil path is connected with the control valve oil path, the control valve oil path is further connected with the variable control oil path, and the variable control oil path is connected with the Pinus motor oil path.
The hydraulic system comprises an execution hydraulic pump, an execution overflow valve and a filter, wherein one end of the execution hydraulic pump is connected with an oil tank, the other end of the execution hydraulic pump is connected with one end of the filter, the execution overflow valve is arranged between the execution hydraulic pump and the filter, the execution overflow valve is connected with the oil tank, and the other end of the filter is connected with a balance oil way.
The balance oil way comprises a balance first spring type check valve, a balance second spring type check valve, a balance first pilot type overflow valve, a balance second pilot type overflow valve, a balance first overflow valve, a balance second overflow valve, a balance first check valve, a balance second check valve, a first stop valve and a second stop valve, the other end of the filter is connected with one end of the balance first spring type check valve and one end of the balance second spring type check valve, the other end of the balance first spring type check valve is connected with one end of the balance first pilot type overflow valve, the other end of the balance first pilot type overflow valve is connected with one end of the balance first overflow valve, the other end of the balance first overflow valve is connected with one end of the balance first check valve, the first stop valve is connected with the balance first check valve in parallel, the other end of the balanced second spring type check valve is connected with one end of a balanced second pilot type overflow valve, the other end of the balanced second pilot type overflow valve is connected with one end of the balanced second overflow valve, the other end of the balanced second overflow valve is connected with one end of the balanced second check valve, the other end of the balanced second check valve is connected with one end of the balanced second overflow valve, the second stop valve and the balanced second check valve are arranged in parallel, the balanced first pilot type overflow valve and the balanced second pilot type overflow valve are connected with a control valve oil path, and hydraulic oil flowing to the control valve oil path is stable under the action of the balanced oil path.
The control valve oil path comprises a control three-position five-way electromagnetic directional valve, a control three-position four-way electromagnetic directional valve, a control one-way valve and a control throttle valve, a balance second pilot overflow valve is connected with the TP end of the control three-position five-way electromagnetic directional valve, the TA end of the control three-position five-way electromagnetic directional valve is connected with the UP end of the control three-position four-way electromagnetic directional valve, the UA end and the UT end of the control three-position four-way electromagnetic directional valve are connected with one end of a control one-way valve, the other end of the control one-way valve is connected with a balance oil way, the control throttle valve is arranged in parallel with the control one-way valve, the balance first pilot overflow valve is connected with the TB end of the control three-position five-way electromagnetic directional valve, the TT end of the control three-position five-way electromagnetic directional valve is connected with the oil tank, the UB end of the control three-position four-way electromagnetic directional valve is connected with the TT end of the control three-position five-way electromagnetic directional valve, and the control three-position five-way electromagnetic directional valve is further connected with the variable control oil circuit.
The variable control oil circuit comprises a bidirectional variable pump and a variable piston cylinder, the TP end of the control three-position five-way electromagnetic directional valve is connected with one end of the variable piston cylinder, the TB end of the control three-position five-way electromagnetic directional valve is connected with the other end of the variable piston cylinder, the control end of the variable piston cylinder is connected with the control end of a bidirectional variable pump, the bidirectional variable pump is connected with an oil way of the Pinus massa motor, the control end of the three-position five-way electromagnetic directional control valve is also connected with the control end of the variable piston cylinder, therefore, when the bidirectional variable pump needs to be reversed, the TP end and the TT end of the three-position five-way electromagnetic reversing valve are controlled to be communicated, the TA end and the TB end are communicated, therefore, the hydraulic oil flowing to one end of the variable piston cylinder returns to the oil tank by balancing the second pilot overflow valve, and the hydraulic oil flows to the other end of the variable piston cylinder by balancing the first pilot overflow valve, so that the variable piston cylinder is driven to control and reverse the bidirectional variable pump.
According to the hydraulic system, the execution modules are driven through the unified driving module, so that the oil paths of each execution element cannot be influenced mutually, the working efficiency is improved, hydraulic oil circularly flows between the driving module and the execution modules when the hydraulic system works, and when the flow direction of the oil paths needs to be changed, the hydraulic oil flowing through the driving module reversely flows when the bidirectional variable pump is controlled, so that the reversing of the whole oil path can be controlled, and the operation is simple.
Furthermore, the oil path of the oil cylinder hydraulic pump comprises an oil cylinder hydraulic pump, a two-position three-way reversing valve and an oil cylinder hydraulic pump overflow valve, one end of the oil cylinder hydraulic pump is connected with an oil tank, the PF end of the two-position three-way reversing valve is connected with the other end of the oil cylinder hydraulic pump, the CF end of the two-position three-way reversing valve is connected with a lifting oil cylinder oil way and a corner oil cylinder oil way, the EF end of the two-position three-way reversing valve is connected with a steering oil cylinder oil way, the control end of the two-position three-way reversing valve is connected with the oil tank through an overflow valve of the oil cylinder hydraulic pump, therefore, when the lifting oil cylinder and the corner oil cylinder need to be controlled, the two-position three-way reversing valve is controlled to link the CF end and the EF end with the PF end, therefore, hydraulic oil can flow to the lifting oil cylinder, the corner oil cylinder and the steering oil cylinder, and when the hydraulic oil does not flow to the steering oil cylinder, the two-position three-way reversing valve is controlled to communicate the CF end with the PF end.
Furthermore, the lifting oil cylinder oil circuit comprises a lifting three-position five-way electromagnetic valve, a lifting one-way valve, a lifting first hydraulic control one-way valve, a lifting second hydraulic control one-way valve and a lifting oil cylinder, wherein a CF end of the two-position three-way reversing valve is connected with an E1P end of the lifting three-position five-way electromagnetic valve, the lifting one-way valve is arranged between the CF end of the two-position three-way reversing valve and an E1P end of the lifting three-position five-way electromagnetic valve, an E1A end of the lifting three-position five-way electromagnetic valve is connected with one end of the lifting first hydraulic control one-way valve, and the other end of the lifting first hydraulic control one-way valve is connected with one end of the lifting oil cylinder; the end E1B of the lifting three-position five-way electromagnetic valve is connected with one end of a lifting second hydraulic control one-way valve, the other end of the lifting second hydraulic control one-way valve is connected with the other end of a lifting oil cylinder, the end E1T of the lifting three-position five-way electromagnetic valve is connected with an oil tank, when the lifting oil cylinder needs to be driven, the lifting three-position five-way electromagnetic valve is controlled to enable the end E1P to be communicated with the end E1A, and the end E1B of the lifting three-position five-way electromagnetic valve is communicated with the end E1T, so that hydraulic oil can flow to the lifting oil cylinder, and the lifting oil cylinder is driven towards one end; when the lifting oil cylinder needs to be driven to the other end, the lifting three-position five-way electromagnetic valve is controlled to enable the E1P end to be communicated with the E1B end, and the E1A end of the lifting three-position five-way electromagnetic valve is controlled to be communicated with the E1T end, so that the lifting oil cylinder can be driven to the other end.
Furthermore, the oil path of the corner oil cylinder comprises a corner three-position five-way electromagnetic valve, a corner one-way valve, a corner first hydraulic control one-way valve, a corner second hydraulic control one-way valve and a lifting oil cylinder, wherein a CF end of the two-position three-way reversing valve is connected with an E2P end of the corner three-position five-way electromagnetic valve, the lifting one-way valve is arranged between the CF end of the two-position three-way reversing valve and an E2P end of the corner three-position five-way electromagnetic valve, an E2A end of the corner three-position five-way electromagnetic valve is connected with one end of the corner first hydraulic control one-way valve, and the other end of the corner first hydraulic control one-way valve is connected with one end of the corner oil cylinder; the end E2B of the corner three-position five-way electromagnetic valve is connected with one end of a corner second hydraulic one-way valve, the other end of the corner second hydraulic one-way valve is connected with the other end of a corner oil cylinder, the end E1T of the corner three-position five-way electromagnetic valve is connected with an oil tank, when the corner oil cylinder needs to be driven, the corner three-position five-way electromagnetic valve is controlled to enable the end E2P to be communicated with the end E2A, and the end E2B of the corner three-position five-way electromagnetic valve is communicated with the end E2T, so that hydraulic oil can flow to the corner oil cylinder, and the corner oil cylinder is driven to one end; when the corner oil cylinder needs to be driven to the other end, the corner three-position five-way electromagnetic valve is controlled to enable the end E2P to be communicated with the end E2B, and the end E2A of the corner three-position five-way electromagnetic valve is controlled to be communicated with the end E2T, so that the corner oil cylinder can be driven to the other end.
Furthermore, a lifting corner control oil path is also arranged between the oil cylinder hydraulic pump oil path and the corner oil cylinder oil path and the lifting oil cylinder oil path, the lifting corner control oil path comprises a lifting corner control first overflow valve, a lifting corner filter, a lifting corner second overflow valve, a lifting corner third overflow valve and a lifting corner fourth overflow valve, a CF end of the two-position three-way reversing valve is connected with one end of the lifting corner filter, the other end of the lifting corner filter is connected with one end of the lifting corner first overflow valve, the other end of the lifting corner first overflow valve is connected with the oil tank, a CF end of the two-position three-way reversing valve is also connected with one end of the lifting corner second overflow valve, the other end of the lifting corner second overflow valve is connected with a control end of the lifting three-position five-way electromagnetic valve and a control end of the corner three-position five-way electromagnetic valve, and one end of the lifting corner third overflow valve is arranged between the CF end of the two-position three-way reversing valve and one end of the lifting corner second overflow valve, the other end of the lifting corner third overflow valve is connected with an oil tank; and one end of a lifting corner fourth overflow valve is connected between the lifting corner second overflow valve and the control end of the lifting three-position five-way electromagnetic valve and the control end of the corner three-position five-way electromagnetic valve, and the other end of the lifting corner fourth overflow valve is connected with the oil tank, so that the lifting three-position five-way electromagnetic valve and the corner three-position five-way electromagnetic valve are controlled through a lifting corner control oil way.
Furthermore, the steering oil cylinder oil path comprises a circulating oil path, a steering oil cylinder, a steering oil drainage overflow valve and a steering oil inlet one-way valve, the EF end of the two-position three-way reversing valve is connected with one end of the steering oil inlet one-way valve, the other end of the steering oil inlet one-way valve is connected with the circulating oil path, one end of the steering oil inlet one-way valve is also connected with one end of the steering oil drainage overflow valve, the other end of the steering oil drainage overflow valve is connected with the circulating oil path, and the circulating oil path is connected with the steering oil cylinder; the steering oil cylinder is provided with a first steering oil cylinder and a second steering oil cylinder, the circulating oil path comprises a steering adjusting valve and a steady flow oil path, the OP end of the steering adjusting valve is connected with the other end of the steering oil inlet one-way valve, the OT end of the steering adjusting valve is connected with the other end of the steering oil drainage overflow valve and is connected with the oil tank, the OR end of the steering adjusting valve is connected with one end of the first steering oil cylinder and the other end of the second steering oil cylinder, and the OL end of the steering adjusting valve is connected with one end of the second steering oil cylinder and the other end of the first steering oil cylinder; a steady flow oil way is arranged between the OR end and the OL end of the steering regulating valve, so that when the steering oil cylinder needs to be driven to steer to the left, the steering regulating valve is controlled to communicate the OP end with the OL end, and at the moment, hydraulic oil flows to one end of the second steering oil cylinder and the other end of the first steering oil cylinder from the OL end of the steering regulating valve, so that steering to the left is realized; when the steering oil cylinder needs to be driven to steer to a side, the steering adjusting valve is controlled to enable the OP end of the steering adjusting valve to be communicated with the OR end, at the moment, hydraulic oil flows to one end of the first steering oil cylinder and the other end of the second steering oil cylinder from the OR end of the steering adjusting valve, and therefore steering to the right is achieved.
Furthermore, the steady flow oil path comprises a steering first overflow valve, a steering second overflow valve, a steering first check valve and a steering second check valve, one end of the steering first overflow valve is connected with the OR end of the steering regulating valve, the other end of the steering first overflow valve is connected with one end of the steering second overflow valve, the other end of the steering second overflow valve is connected with the OL end of the steering regulating valve, the other end of the steering first overflow valve and one end of the steering second overflow valve are also connected with the oil tank, one end of the steering first check valve is connected with the OR end of the steering regulating valve, the other end of the steering first check valve is connected with one end of the steering second check valve, the other end of the steering second check valve is connected with the OL end of the steering regulating valve, and the oil tank is connected between the steering first check valve and the steering second check valve, so that the steady flow oil path can prevent the steering oil cylinder from generating large fluctuation, so that the oil passage is stable.
Furthermore, the powder loosening motor oil path comprises a powder loosening motor and a motor oil drainage oil path, one end of the bidirectional variable pump is connected with one end of the powder loosening motor, the other end of the Pinus motor is connected with the other end of the bidirectional variable pump, a motor oil drainage oil path is arranged between the Pinus motor and the bidirectional variable pump, the motor oil drainage oil path comprises a motor oil drainage three-position two-way reversing valve and a motor oil drainage overflow valve, the MA end of the motor oil drainage three-position two-way reversing valve is connected with one end of the Pink motor, the MB end of the motor oil drainage three-position two-way reversing valve is connected with the other end of the Pink motor, the MT end of the motor oil drainage three-position two-way reversing valve is connected with one end of a motor oil drainage overflow valve, the other end of the motor oil drainage overflow valve is connected with an oil tank, therefore, when the Pink motor stops working, the hydraulic oil remained on the Pink motor flows back to the oil tank through the motor oil drainage oil way.
Furthermore, the execution driving module is also connected with the mobile execution module, the mobile execution module comprises a brake motor, a brake control valve and a brake two-position two-way reversing valve, one end of the bidirectional variable pump is connected with one end of the brake motor, the other end of the brake motor is connected with the other end of the bidirectional variable pump, the brake motor is also provided with a brake control valve which is connected with an SA end of the brake two-position two-way reversing valve, the SP end of the braking two-position two-way reversing valve is connected with the execution driving module, the ST end of the braking two-position two-way reversing valve is connected with the oil tank, therefore, when the brake is needed, the SP end of the two-position two-way reversing valve for controlling the brake is communicated with the SA end, so that the hydraulic oil can flow to the brake control valve, therefore, braking is realized, and when the braking is stopped, the SA end of the braking two-position two-way reversing valve is controlled to be communicated with the ST end, so that hydraulic oil can flow back to the oil tank.
Furthermore, one end of the oil cylinder hydraulic pump, which is connected with the oil tank, is connected with a fan motor oil way, the fan motor oil way comprises a fan motor hydraulic pump, a fan motor and a fan motor overflow valve, one end of the fan motor hydraulic pump is connected with the oil tank, the other end of the fan motor hydraulic pump is connected with one end of the fan motor, the other end of the fan motor is connected with the oil tank, the fan motor overflow valve is arranged between the two ends of the fan motor, one end of the fan motor overflow valve is connected with one end of the fan motor, which is connected with the fan motor hydraulic pump, and the other end of the fan motor overflow valve is connected with one end of the fan motor, which is connected with the oil tank, so that the heat dissipation is realized through the action of the fan motor oil way.
Drawings
Fig. 1 is a schematic view of a hydraulic system of the deep ploughing and crushing ripper of the present invention.
Fig. 2 is a schematic diagram of an execution driving module according to the present invention.
Fig. 3 is an enlarged view of a portion a in fig. 2.
Fig. 4 is an enlarged view at B in fig. 2.
Fig. 5 is an enlarged view at C in fig. 2.
Fig. 6 is a schematic diagram of an oil path of a hydraulic pump of the oil cylinder.
Fig. 7 is a schematic diagram of the lift cylinder oil path and the corner cylinder oil path of the present invention.
Fig. 8 is an enlarged view at D in fig. 7.
Fig. 9 is an enlarged view at E in fig. 6.
Fig. 10 is a schematic view of an oil path of the Pinus motor of the present invention.
FIG. 11 is a diagram of a mobile execution module according to the present invention.
Fig. 12 is an enlarged view at F in fig. 11.
Fig. 13 is an enlarged view at G in fig. 6.
Detailed Description
The present invention will be described in further detail with reference to the accompanying drawings and specific embodiments.
As shown in fig. 1 to 13, a hydraulic system of a deep ploughing and smashing ripper comprises a driving module 1y and an executing module 2y, wherein the driving module 1y comprises more than one executing driving module 10y, the executing driving module 10y is connected with an oil tank 0y, the executing module 2y comprises a smashing and loosening executing module 4y and a moving executing module 22y, the smashing and loosening executing module 4y comprises a smashing and loosening motor oil way 41y, a lifting oil cylinder oil way 42y, a corner oil cylinder oil way 43y and a steering oil cylinder oil way 44y, and the lifting oil cylinder oil way 42y, the corner oil cylinder oil way 43y and the steering oil cylinder oil way 44y are connected with the oil tank 0y through an oil cylinder hydraulic pump oil way 45 y.
As shown in fig. 2, the execution driving module 10y includes a variable control oil path 101y, a balance oil path 102y, a control valve oil path 103y and an execution hydraulic pump oil path 104y, the execution hydraulic pump oil path 104y is connected to the oil tank 0y, the execution hydraulic pump oil path 104y is further connected to the balance oil path 102y, the balance oil path 102y is connected to the control valve oil path 103y, the control valve oil path 103y is further connected to the variable control oil path 101y, and the variable control oil path 101y is connected to the pulverizing loosening motor oil path 41 y.
As shown in fig. 2 and 5, the performing hydraulic pump line 104y includes a performing hydraulic pump 1041y, a performing overflow valve 1042y, and a filter 1043y, one end of the performing hydraulic pump 1041y is connected to the oil tank 0y, the other end of the performing hydraulic pump 1041y is connected to one end of the filter 1043y, the performing overflow valve 1042y is disposed between the performing hydraulic pump 1041y and the filter 1043y, the performing overflow valve 1042y is connected to the oil tank 0y, and the other end of the filter 1043y is connected to the balance line 102y, so that the hydraulic oil pumped by the performing hydraulic pump to flow to other lines is filtered by the filter to filter impurities in the hydraulic oil.
As shown in fig. 3, the balanced oil path 102y includes a balanced first spring type check valve 1021y, a balanced second spring type check valve 1022y, a balanced first pilot type overflow valve 1023y, a balanced second pilot type overflow valve 1024y, a balanced first overflow valve 1025y, a balanced second overflow valve 1026y, a balanced first check valve 1027y, a balanced second check valve 1028y, a first stop valve 1029y and a second stop valve 1020y, the other end of the filter 1043y is connected to one end of the balanced first spring type check valve 1021y and one end of the balanced second spring type check valve 1022y, the other end of the balanced first spring type check valve 1021y is connected to one end of the balanced first pilot type overflow valve 1023y, the other end of the balanced first pilot type overflow valve 1023y is connected to one end of the balanced first overflow valve 1025y, the other end of the balanced first overflow valve 1025y is connected to one end of the balanced first check valve 1027y, the other end of the balance first check valve 1027y is connected with one end of a balance first overflow valve 1025y, a first cut-off valve 1029y is connected with the balance first check valve 1027y in parallel, the other end of the balanced second spring type check valve 1022y is connected with one end of a balanced second pilot operated overflow valve 1024y, the other end of the balanced second pilot operated relief valve 1024y is connected to one end of a balanced second relief valve 1026y, the other end of the balanced second overflow valve 1026y is connected with one end of a balanced second check valve 1028y, the other end of the balanced second check valve 1028y is connected with one end of a balanced second overflow valve 1026y, the second stop valve 1020y is arranged in parallel with the balanced second check valve 1028y, the balanced first pilot overflow valve 1023y and the balanced second pilot overflow valve 1024y are connected with the control valve oil path 103y, and the hydraulic oil pressure flowing to the control valve oil path is stable under the action of the balanced oil path.
As shown in fig. 4, the control valve oil path 103y includes a control three-position five-way electromagnetic directional valve 1031y, a control three-position four-way electromagnetic directional valve 1032y, a control check valve 1033y and a control throttle valve 1034y, the balance second pilot overflow valve 1024y is connected to the TP end of the control three-position five-way electromagnetic directional valve 1031y, the TA end of the control three-position five-way electromagnetic directional valve 1031y is connected to the UP end of the control three-position four-way electromagnetic directional valve 1032y, the UA end and the UT end of the control three-position four-way electromagnetic directional valve 1032y are connected to one end of the control check valve 1033y, the other end of the control check valve 1033y is connected to the balance oil path 102y, the control throttle valve 1034y is connected to the control check valve 1033y in parallel, the balance first pilot overflow valve y is connected to the TB end of the control three-position five-way electromagnetic directional valve 1031y, the TT end of the control three-position five-way electromagnetic directional valve 1031y is connected to the oil tank 0y, the UB end of the control three-position four-way electromagnetic reversing valve 1032y is connected with the TT end of the control three-position five-way electromagnetic reversing valve 1031y, and the control three-position five-way electromagnetic reversing valve 1031y is further connected with the variable control oil path 101 y.
As shown in fig. 5, the variable control oil path 101y includes a two-way variable pump 1011y and a variable piston cylinder 1012y, a TP end of the control three-position five-way electromagnetic directional valve 1031y is connected to one end of the variable piston cylinder 1012y, a TB end of the control three-position five-way electromagnetic directional valve 1031y is connected to the other end of the variable piston cylinder 1012y, a control end 10121y of the variable piston cylinder 1012y is connected to a control end 10111y of the two-way variable pump 1011y, the two-way variable pump 1011y is connected to the pinking motor oil path 41y, a control end 10311y of the control three-position five-way electromagnetic directional valve 1031y is also connected to a control end 10121y of the variable piston cylinder 1012y, and thus when the two-way variable pump needs to be commutated, the TP end of the control three-position five-way electromagnetic directional valve is communicated with the TT end, and the TA end is communicated with the TB end, so that hydraulic oil flowing to one end of the variable piston cylinder through the balanced second pilot operated spill valve flows back to the oil tank, and hydraulic oil flows to the other end of the variable piston cylinder through the balance first pilot type overflow valve, so that the variable piston cylinder is driven to control and commutate the bidirectional variable pump.
As shown in fig. 6, the cylinder hydraulic pump oil path 45y includes a cylinder hydraulic pump 451y, a two-position three-way directional valve 452y and a cylinder hydraulic pump overflow valve 453y, one end of the cylinder hydraulic pump 451y is connected to the oil tank 0y, a PF end of the two-position three-way directional valve 452y is connected to the other end of the cylinder hydraulic pump 451y, a CF end of the two-position three-way directional valve 452y is connected to the lift cylinder oil path 42y and the corner cylinder oil path 43y, an EF end of the two-position three-way directional valve 452y is connected to the steering cylinder oil path 44y, and a control end 4521y of the two-position three-way directional valve 452y is connected to the oil tank 0y through the cylinder hydraulic pump overflow valve 453y, so that, when the lift cylinder and the corner cylinder need to be controlled, the two-position three-way directional valve is controlled to link the CF end and the EF end thereof with the PF end, thereby allowing hydraulic oil to flow to the lift cylinder, the corner cylinder and the steering cylinder, when hydraulic oil does not need to flow to the steering cylinder, and controlling the two-position three-way reversing valve to communicate the CF end with the PF end.
As shown in fig. 7 and 8, the lift cylinder oil path 42y includes a lift three-position five-way solenoid valve 421y, a lift check valve 422y, a lift first hydraulic control check valve 423y, a lift second hydraulic control check valve 424y and a lift cylinder 425y, a CF end of the two-position three-way directional valve 452y is connected to an E1P end of the lift three-position five-way solenoid valve 421y, the lift check valve 422y is disposed between the CF end of the two-position three-way directional valve 452y and an E1P end of the lift three-position five-way solenoid valve 421y, an E1A end of the lift three-position five-way solenoid valve 421y is connected to one end of the lift first hydraulic control check valve 423y, and the other end of the lift first hydraulic control check valve 423y is connected to one end of the lift cylinder 425 y; the end E1B of the lifting three-position five-way electromagnetic valve 421y is connected with one end of a lifting second hydraulic control one-way valve 424y, the other end of the lifting second hydraulic control one-way valve 424y is connected with the other end of a lifting oil cylinder 425y, the end E1T of the lifting three-position five-way electromagnetic valve 421y is connected with an oil tank 0y, when the lifting oil cylinder needs to be driven, the lifting three-position five-way electromagnetic valve is controlled to enable the end E1P to be communicated with the end E1A, and the end E1B of the lifting three-position five-way electromagnetic valve is communicated with the end E1T, so that hydraulic oil can flow to the lifting oil cylinder, and the lifting oil cylinder is driven towards one end; when the lifting oil cylinder needs to be driven to the other end, the lifting three-position five-way electromagnetic valve is controlled to enable the E1P end to be communicated with the E1B end, and the E1A end of the lifting three-position five-way electromagnetic valve is controlled to be communicated with the E1T end, so that the lifting oil cylinder can be driven to the other end.
As shown in fig. 7 and 8, the corner cylinder oil path 43y includes a corner three-position five-way solenoid valve 431y, a corner check valve 432y, a corner first hydraulic control check valve 433y, a corner second hydraulic control check valve 434y and a lift cylinder 435y, a CF end of the two-position three-way selector valve 452y is connected to an E2P end of the corner three-position five-way solenoid valve 431y, the lift check valve 432y is arranged between the CF end of the two-position three-way selector valve 452y and an E2P end of the corner three-position five-way solenoid valve 431y, an E2A end of the corner three-position five-way solenoid valve 431y is connected to one end of the corner first hydraulic control check valve 433y, and the other end of the corner first hydraulic control check valve 433y is connected to one end of the corner cylinder 435 y; the end E2B of the corner three-position five-way electromagnetic valve 431y is connected with one end of a corner second hydraulic one-way valve 434y, the other end of the corner second hydraulic one-way valve 434y is connected with the other end of a corner oil cylinder 435y, the end E1T of the corner three-position five-way electromagnetic valve 431y is connected with an oil tank 0y, when the corner oil cylinder needs to be driven, the corner three-position five-way electromagnetic valve is controlled to enable the end E2P to be communicated with the end E2A, and the end E2B of the corner three-position five-way electromagnetic valve is communicated with the end E2T, so that hydraulic oil can flow to the corner oil cylinder, and the corner oil cylinder is driven towards one end; when the corner oil cylinder needs to be driven to the other end, the corner three-position five-way electromagnetic valve is controlled to enable the end E2P to be communicated with the end E2B, and the end E2A of the corner three-position five-way electromagnetic valve is controlled to be communicated with the end E2T, so that the corner oil cylinder can be driven to the other end.
As shown in fig. 8, a lifting corner control oil path 46y is further provided between the oil cylinder hydraulic pump oil path 45y and the corner oil cylinder oil path 43y and the lifting oil cylinder oil path 42y, the lifting corner control oil path 46y includes a first lifting corner control overflow valve 461y, a lifting corner filter 462y, a second lifting corner overflow valve 463y, a third lifting corner overflow valve 464y and a fourth lifting corner overflow valve 465y, a CF end of the two-position three-way reversing valve 452y is connected to one end of the lifting corner filter 462y, the other end of the lifting corner filter 462y is connected to one end of the first lifting corner overflow valve 461y, the other end of the first lifting corner overflow valve 461y is connected to the oil tank 0y, a CF end of the two-position three-way reversing valve 452y is further connected to one end of the second lifting corner overflow valve 463y, and the other end of the second lifting corner overflow valve 463y is connected to a control end 4211y of the lifting three-position five-way electromagnetic valve 421y and a control end 4311y of the corner five-position electromagnetic valve 431y y, one end of a lifting corner third overflow valve 464y is connected between the CF end of the two-position three-way reversing valve 452y and one end of the lifting corner second overflow valve 463y, and the other end of the lifting corner third overflow valve 464y is connected with the oil tank 0 y; one end of a lifting corner fourth overflow valve 465y is connected between the lifting corner second overflow valve 463y and the control end 4211y of the lifting three-position five-way electromagnetic valve 421y and the control end 4311y of the corner three-position five-way electromagnetic valve 431y, and the other end of the lifting corner fourth overflow valve 465y is connected with the oil tank 0y, so that the lifting three-position five-way electromagnetic valve and the corner three-position five-way electromagnetic valve are controlled through a lifting corner control oil path.
As shown in fig. 6, 7 and 9, the steering cylinder oil path 44y includes a circulation oil path 441y, a steering cylinder 442y, a steering oil-draining overflow valve 443y and a steering oil-inlet check valve 444y, an EF end of the two-position three-way reversing valve 452y is connected to one end of the steering oil-inlet check valve 444y, the other end of the steering oil-inlet check valve 444y is connected to the circulation oil path 441y, one end of the steering oil-inlet check valve 444y is further connected to one end of the steering oil-draining overflow valve 443y, the other end of the steering oil-draining overflow valve 443y is connected to the circulation oil path 441y, and the circulation oil path 441y is connected to the steering cylinder 442 y; the steering oil cylinder 442y is provided with a first steering oil cylinder 4421y and a second steering oil cylinder 4422y, the circulating oil circuit 441y comprises a steering adjusting valve 445y and a steady flow oil circuit 446y, the OP end of the steering adjusting valve 445y is connected with the other end of the steering oil inlet one-way valve 444y, the OT end of the steering adjusting valve 445y is connected with the other end of the steering oil drain overflow valve 443y and is connected with the oil tank 0y, the OR end of the steering adjusting valve 445y is connected with one end of the first steering oil cylinder 4421y and the other end of the second steering oil cylinder 4422y, and the OL end of the steering adjusting valve 445y is connected with one end of the second steering oil cylinder 4422y and the other end of the first steering oil cylinder 4421y (shown in FIG. 7); a steady flow oil path 446y is arranged between the OR end and the OL end of the steering regulating valve 445y, so that when the steering oil cylinder needs to be driven to steer to the left, the steering regulating valve is controlled to communicate the OP end with the OL end, and at the moment, hydraulic oil flows to one end of the second steering oil cylinder and the other end of the first steering oil cylinder from the OL end of the steering regulating valve, so that steering to the left is realized; when the steering oil cylinder needs to be driven to steer to a side, the steering adjusting valve is controlled to enable the OP end of the steering adjusting valve to be communicated with the OR end, at the moment, hydraulic oil flows to one end of the first steering oil cylinder and the other end of the second steering oil cylinder from the OR end of the steering adjusting valve, and therefore steering to the right is achieved.
As shown in fig. 9, the steady flow oil path 441y includes a first diverting overflow valve 4411y, a second diverting overflow valve 4412y, a first diverting check valve 4413y and a second diverting check valve 4414y, one end of the first diverting overflow valve 4411y is connected to an OR end of the diverting regulating valve 445y, the other end of the first diverting overflow valve 4411y is connected to one end of the second diverting overflow valve 4412y, the other end of the second diverting overflow valve 4412y is connected to an OL end of the diverting regulating valve 445y, the other end of the first diverting overflow valve 4411y and one end of the second diverting overflow valve 4412y are further connected to the oil tank 0y, one end of the first diverting check valve 4413y is connected to the OR end of the diverting regulating valve 445y, the other end of the first diverting check valve 4413y is connected to one end of the second diverting check valve 4414y, the other end of the diverting second diverting check valve 4414y is connected to the OL end of the diverting regulating valve 445y, the steering first one-way valve 4413y and the steering second one-way valve 4414y are connected with the oil tank 0y, so that the hydraulic oil communicated with the steering oil cylinder cannot fluctuate greatly through the steady flow oil path, and the oil path is stable.
As shown in fig. 10, the pulverizing loosening motor oil path 41y includes a pulverizing loosening motor 411y and a motor oil drainage path 412y, one end of the bidirectional variable pump 101y is connected with one end of the pulverizing loosening motor 411y, the other end of the pulverizing loosening motor 411y is connected with the other end of the bidirectional variable pump 101y, a motor oil drainage path 412y is arranged between the pulverizing loosening motor 411y and the bidirectional variable pump 101y, the motor oil drainage path 412y includes a motor oil drainage three-position two-way reversing valve 413y and a motor oil drainage overflow valve 414y, an MA end of the motor oil drainage three-position two-way reversing valve 413y is connected with one end of the pulverizing loosening motor 411y, an MB end of the motor oil drainage three-position two-way reversing valve 413y is connected with the other end of the pulverizing loosening motor 411y, an MT end of the motor oil drainage three-position two-way reversing valve 413y is connected with one end of the motor oil drainage overflow valve 414y, and the other end of the motor oil drainage overflow valve 414y is connected with the oil tank 0y, therefore, when the Pink motor stops working, the hydraulic oil remained on the Pink motor flows back to the oil tank through the motor oil drainage oil way.
As shown in fig. 11 and 12, the execution driving module 10y is further connected to the movement execution module 22y, the movement execution module 22y includes a brake motor 221y, a brake control valve 222y and a brake two-position two-way reversing valve 223y, one end of the two-way variable pump 101y is connected to one end of the brake motor 221y, the other end of the brake motor 221y is connected to the other end of the two-way variable pump 101y, the brake motor 221y is further provided with a brake control valve 222y, the brake control valve 222y is connected to an SA end of the brake two-position two-way reversing valve 223y, an SP end of the brake two-position two-way reversing valve 223y is connected to the execution driving module 10y, and an ST end of the brake two-position two-way reversing valve 223y is connected to the oil tank 0y, so that when braking is required, the SP end of the brake two-position two-way reversing valve is controlled to communicate with the SA end, so that hydraulic oil can flow to the brake control valve, therefore, braking is realized, and when the braking is stopped, the SA end of the braking two-position two-way reversing valve is controlled to be communicated with the ST end, so that hydraulic oil can flow back to the oil tank.
As shown in fig. 6 and 13, one end of the cylinder hydraulic pump 451y connected to the oil tank 0y is connected to a fan motor oil path 47y, the fan motor oil passage 47y includes a fan motor hydraulic pump 471y, a fan motor 472y and a fan motor spill valve 473y, one end of the fan motor hydraulic pump 471y is connected to the oil tank 0y, the other end of the fan motor hydraulic pump 471y is connected to one end of the fan motor 472y, the other end of the fan motor 472y is connected to the oil tank 0y, a fan motor overflow valve 473y is arranged between the two ends of the fan motor 472y, one end of the fan motor overflow valve 473y is connected with the end of the fan motor 472y connected with the fan motor hydraulic pump 471y, and the other end of the fan motor overflow valve 473y is connected with the end of the fan motor 472y connected with the oil tank 0y, so that heat dissipation is realized through the action of the fan motor oil path.
According to the hydraulic system, the execution modules are driven through the unified driving module, so that the oil paths of each execution element cannot be influenced mutually, the working efficiency is improved, hydraulic oil circularly flows between the driving module and the execution modules when the hydraulic system works, and when the flow direction of the oil paths needs to be changed, the hydraulic oil flowing through the driving module reversely flows when the bidirectional variable pump is controlled, so that the reversing of the whole oil path can be controlled, and the operation is simple.

Claims (10)

1. The utility model provides a hydraulic system of scarifier is smashed in deep ploughing, includes drive module and execution module, its characterized in that: the driving module comprises more than one execution driving module, the execution driving module is connected with an oil tank, the execution module comprises a crushing and loosening execution module and a mobile execution module, the crushing and loosening execution module comprises a crushing and loosening motor oil way, a lifting oil cylinder oil way, a corner oil cylinder oil way and a steering oil cylinder oil way, and the lifting oil cylinder oil way, the corner oil cylinder oil way and the steering oil cylinder oil way are connected with the oil tank through oil cylinder hydraulic pump oil ways;
the execution driving module comprises a variable control oil path, a balance oil path, a control valve oil path and an execution hydraulic pump oil path, the execution hydraulic pump oil path is connected with an oil tank, the execution hydraulic pump oil path is also connected with the balance oil path, the balance oil path is connected with the control valve oil path, the control valve oil path is also connected with a variable control oil path, and the variable control oil path is connected with a Pinus motor oil path;
the oil path of the execution hydraulic pump comprises an execution hydraulic pump, an execution overflow valve and a filter, one end of the execution hydraulic pump is connected with the oil tank, the other end of the execution hydraulic pump is connected with one end of the filter, the execution overflow valve is arranged between the execution hydraulic pump and the filter, the execution overflow valve is connected with the oil tank, and the other end of the filter is connected with the balance oil path;
the balance oil way comprises a balance first spring type check valve, a balance second spring type check valve, a balance first pilot type overflow valve, a balance second pilot type overflow valve, a balance first overflow valve, a balance second overflow valve, a balance first check valve, a balance second check valve, a first stop valve and a second stop valve, the other end of the filter is connected with one end of the balance first spring type check valve and one end of the balance second spring type check valve, the other end of the balance first spring type check valve is connected with one end of the balance first pilot type overflow valve, the other end of the balance first pilot type overflow valve is connected with one end of the balance first overflow valve, the other end of the balance first overflow valve is connected with one end of the balance first check valve, the first stop valve is connected with the balance first check valve in parallel, the other end of the balanced second spring type check valve is connected with one end of a balanced second pilot type overflow valve, the other end of the balanced second pilot type overflow valve is connected with one end of the balanced second overflow valve, the other end of the balanced second overflow valve is connected with one end of the balanced second check valve, the other end of the balanced second check valve is connected with one end of the balanced second overflow valve, a second stop valve and the balanced second check valve are arranged in parallel, and the balanced first pilot type overflow valve and the balanced second pilot type overflow valve are connected with a control valve oil circuit;
the control valve oil path comprises a control three-position five-way electromagnetic directional valve, a control three-position four-way electromagnetic directional valve, a control one-way valve and a control throttle valve, a balance second pilot overflow valve is connected with the TP end of the control three-position five-way electromagnetic directional valve, the TA end of the control three-position five-way electromagnetic directional valve is connected with the UP end of the control three-position four-way electromagnetic directional valve, the UA end and the UT end of the control three-position four-way electromagnetic directional valve are connected with one end of a control one-way valve, the other end of the control one-way valve is connected with a balance oil way, the control throttle valve is arranged in parallel with the control one-way valve, the balance first pilot overflow valve is connected with the TB end of the control three-position five-way electromagnetic directional valve, the TT end of the control three-position five-way electromagnetic directional valve is connected with the oil tank, the UB end of the control three-position four-way electromagnetic directional valve is connected with the TT end of the control three-position five-way electromagnetic directional valve, and the control three-position five-way electromagnetic directional valve is also connected with the variable control oil circuit;
the variable control oil circuit comprises a bidirectional variable pump and a variable piston cylinder, the TP end of the control three-position five-way electromagnetic directional valve is connected with one end of the variable piston cylinder, the TB end of the control three-position five-way electromagnetic directional valve is connected with the other end of the variable piston cylinder, the control end of the variable piston cylinder is connected with the control end of the bidirectional variable pump, the bidirectional variable pump is connected with the Pinus massa motor oil circuit, and the control end of the control three-position five-way electromagnetic directional valve is also connected with the control end of the variable piston cylinder.
2. The hydraulic system of a deep ploughing and crushing loosener of claim 1, wherein: the oil cylinder hydraulic pump oil path comprises an oil cylinder hydraulic pump, a two-position three-way reversing valve and an oil cylinder hydraulic pump overflow valve, one end of the oil cylinder hydraulic pump is connected with the oil tank, the PF end of the two-position three-way reversing valve is connected with the other end of the oil cylinder hydraulic pump, the CF end of the two-position three-way reversing valve is connected with the lifting oil cylinder oil path and the corner oil cylinder oil path, the EF end of the two-position three-way reversing valve is connected with the steering oil cylinder oil path, and the control end of the two-position three-way reversing valve is connected with the oil tank through the oil cylinder hydraulic pump overflow valve.
3. The hydraulic system of a deep ploughing and crushing loosener of claim 2, wherein: the lifting oil cylinder oil circuit comprises a lifting three-position five-way electromagnetic valve, a lifting one-way valve, a lifting first hydraulic control one-way valve, a lifting second hydraulic control one-way valve and a lifting oil cylinder, wherein a CF end of the two-position three-way reversing valve is connected with an E1P end of the lifting three-position five-way electromagnetic valve, the lifting one-way valve is arranged between the CF end of the two-position three-way reversing valve and an E1P end of the lifting three-position five-way electromagnetic valve, an E1A end of the lifting three-position five-way electromagnetic valve is connected with one end of the lifting first hydraulic control one-way valve, and the other end of the lifting first hydraulic control one-way valve is connected with one end of the lifting oil cylinder; the E1B end of the lifting three-position five-way electromagnetic valve is connected with one end of a lifting second hydraulic control one-way valve, the other end of the lifting second hydraulic control one-way valve is connected with the other end of the lifting oil cylinder, and the E1T end of the lifting three-position five-way electromagnetic valve is connected with an oil tank.
4. The hydraulic system of a deep ploughing and crushing loosener of claim 2, wherein: the corner oil cylinder oil path comprises a corner three-position five-way electromagnetic valve, a corner check valve, a corner first hydraulic control check valve, a corner second hydraulic control check valve and a lifting oil cylinder, wherein a CF end of the two-position three-way reversing valve is connected with an E2P end of the corner three-position five-way electromagnetic valve, the lifting check valve is arranged between the CF end of the two-position three-way reversing valve and an E2P end of the corner three-position five-way electromagnetic valve, an E2A end of the corner three-position five-way electromagnetic valve is connected with one end of the corner first hydraulic control check valve, and the other end of the corner first hydraulic control check valve is connected with one end of the corner oil cylinder; the end E2B of the corner three-position five-way electromagnetic valve is connected with one end of a corner second hydraulic control one-way valve, the other end of the corner second hydraulic control one-way valve is connected with the other end of the corner oil cylinder, and the end E1T of the corner three-position five-way electromagnetic valve is connected with an oil tank.
5. The hydraulic system of a deep ploughing and crushing loosener as claimed in claim 3 or 4, wherein: a lifting corner control oil path is also arranged between the oil cylinder hydraulic pump oil path and the corner oil cylinder oil path and between the oil cylinder hydraulic pump oil path and the lifting oil cylinder oil path, the lifting corner control oil path comprises a lifting corner control first overflow valve, a lifting corner filter, a lifting corner second overflow valve, a lifting corner third overflow valve and a lifting corner fourth overflow valve, the CF end of the two-position three-way reversing valve is connected with one end of the lifting corner filter, the other end of the lifting corner filter is connected with one end of the lifting corner first overflow valve, the other end of the lifting corner first overflow valve is connected with the oil tank, the CF end of the two-position three-way reversing valve is also connected with one end of the lifting corner second overflow valve, the other end of the lifting corner second overflow valve is connected with the control end of the lifting three-position five-way electromagnetic valve and the control end of the corner three-position five-way electromagnetic valve, and the CF end of the lifting corner second overflow valve is connected with one end of the lifting corner third overflow valve, the other end of the lifting corner third overflow valve is connected with an oil tank; one end of a lifting corner fourth overflow valve is connected between the lifting corner second overflow valve and the control end of the lifting three-position five-way electromagnetic valve and the control end of the corner three-position five-way electromagnetic valve, and the other end of the lifting corner fourth overflow valve is connected with the oil tank.
6. The hydraulic system of a deep ploughing and crushing loosener of claim 2, wherein: the steering oil cylinder oil path comprises a circulating oil path, a steering oil cylinder, a steering oil drainage overflow valve and a steering oil inlet one-way valve, wherein the EF end of the two-position three-way reversing valve is connected with one end of the steering oil inlet one-way valve, the other end of the steering oil inlet one-way valve is connected with the circulating oil path, one end of the steering oil inlet one-way valve is also connected with one end of the steering oil drainage overflow valve, the other end of the steering oil drainage overflow valve is connected with the circulating oil path, and the circulating oil path is connected with the steering oil cylinder; the steering oil cylinder is provided with a first steering oil cylinder and a second steering oil cylinder, the circulating oil path comprises a steering adjusting valve and a steady flow oil path, the OP end of the steering adjusting valve is connected with the other end of the steering oil inlet one-way valve, the OT end of the steering adjusting valve is connected with the other end of the steering oil drainage overflow valve and is connected with the oil tank, the OR end of the steering adjusting valve is connected with one end of the first steering oil cylinder and the other end of the second steering oil cylinder, and the OL end of the steering adjusting valve is connected with one end of the second steering oil cylinder and the other end of the first steering oil cylinder; and a steady flow oil path is arranged between the OR end and the OL end of the steering regulating valve.
7. The hydraulic system of a deep ploughing and crushing loosener of claim 6, wherein: the steady flow oil way comprises a steering first overflow valve, a steering second overflow valve, a steering first check valve and a steering second check valve, one end of the steering first overflow valve is connected with an OR end of the steering adjusting valve, the other end of the steering first overflow valve is connected with one end of the steering second overflow valve, the other end of the steering second overflow valve is connected with an OL end of the steering adjusting valve, the other end of the steering first overflow valve and one end of the steering second overflow valve are further connected with an oil tank, one end of the steering first check valve is connected with the OR end of the steering adjusting valve, the other end of the steering first check valve is connected with one end of the steering second check valve, the other end of the steering second check valve is connected with the OL end of the steering adjusting valve, and the steering first check valve and the steering second check valve are further connected with the oil tank.
8. The hydraulic system of a deep ploughing and crushing loosener of claim 1, wherein: the powder pine motor oil circuit includes powder pine motor and motor draining oil circuit, and the one end of powder pine motor is connected to the one end of two-way variable pump, the other end of powder pine motor is connected with the other end of two-way variable pump, is located and is equipped with motor draining oil circuit between powder pine motor and the two-way variable pump, motor draining oil circuit includes motor draining tribit two-way switching-over valve and motor draining overflow valve, the one end of powder pine motor is connected to the MA end of motor draining tribit two-way switching-over valve, and the other end of powder pine motor is connected to the MB end of motor draining tribit two-way switching-over valve, the one end of motor draining overflow valve is connected to the MT end of motor draining tribit two-way switching-over valve, and the other end of motor draining overflow valve connects the oil tank.
9. The hydraulic system of a deep ploughing and crushing loosener of claim 1, wherein: carry out drive module and still be connected with removal execution module, remove execution module and include brake motor, brake control valve and two-position two-way switching-over valve of brake, the one end of brake motor is connected to the one end of two-way variable pump, the other end of two-way variable pump is connected to the other end of brake motor still be equipped with brake control valve on the brake motor, the SA end of two-position two-way switching-over valve of brake is connected to brake control valve, carry out drive module is connected to the SP end of two-position two-way switching-over valve of brake, and the ST end connection oil tank of two-position two-way switching-over valve of brake.
10. The hydraulic system of a deep ploughing and crushing loosener of claim 2, wherein: the one end that hydro-cylinder hydraulic pump and oil tank are connected is connected with the fan motor oil circuit, the fan motor oil circuit includes fan motor hydraulic pump, fan motor and fan motor overflow valve, the oil tank is connected to the one end of fan motor hydraulic pump, and the one end of fan motor is connected to the other end of fan motor hydraulic pump, the oil tank is connected to the other end of fan motor, is equipped with the fan motor overflow valve between the both ends of fan motor, the one end of fan motor and fan motor hydraulic pump connection is connected to the one end of fan motor overflow valve, and the one end of fan motor and oil tank connection is connected to the other end of fan motor overflow valve.
CN202111649366.8A 2021-12-30 2021-12-30 Hydraulic system of deep ploughing crushing scarifier Pending CN114109944A (en)

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