CN113431817A - Low-pressure control valve group, electro-hydraulic control system and tractor - Google Patents

Low-pressure control valve group, electro-hydraulic control system and tractor Download PDF

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Publication number
CN113431817A
CN113431817A CN202110843369.9A CN202110843369A CN113431817A CN 113431817 A CN113431817 A CN 113431817A CN 202110843369 A CN202110843369 A CN 202110843369A CN 113431817 A CN113431817 A CN 113431817A
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CN
China
Prior art keywords
solenoid valve
way
oil
oil inlet
proportional solenoid
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CN202110843369.9A
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Chinese (zh)
Inventor
蔡二朋
申屠军阳
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Weichai Lovol Heavy Industry Co Ltd
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Weichai Lovol Heavy Industry Co Ltd
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Priority to CN202110843369.9A priority Critical patent/CN113431817A/en
Publication of CN113431817A publication Critical patent/CN113431817A/en
Pending legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/022—Flow-dividers; Priority valves
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K20/00—Arrangement or mounting of change-speed gearing control devices in vehicles
    • 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
    • F15B1/04—Accumulators
    • 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
    • F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B19/00—Testing; Calibrating; Fault detection or monitoring; Simulation or modelling of fluid-pressure systems or apparatus not otherwise provided for
    • F15B19/005—Fault detection or monitoring
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/62—Hybrid vehicles

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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)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Control Of Transmission Device (AREA)

Abstract

The invention discloses a low-pressure control valve group, an electro-hydraulic control system and a tractor, and relates to the technical field of power gear shifting. The low pressure control valve group includes: the oil return device comprises an oil inlet pipeline, an oil return pipeline, a first electromagnetic valve group, a second electromagnetic valve group, a third electromagnetic valve group, a first electromagnetic valve and a second electromagnetic valve, wherein the first electromagnetic valve group is connected with an AMT (automated mechanical transmission) oil cylinder module, the second electromagnetic valve group is connected with a rear power output shaft, the third electromagnetic valve group is connected with a clutch group used for controlling gears, the first electromagnetic valve is connected with a clutch used for controlling four-wheel drive, and the second electromagnetic valve is connected with a differential mechanism. The low-pressure control valve bank provided by the invention is suitable for function control of an electro-hydraulic control system in a power gear-shifting tractor, high integration of the low-pressure control valve bank is realized, the compact valve body design enables the installation space to be smaller, the pipeline arrangement to be more convenient, and the cost is effectively reduced.

Description

Low-pressure control valve group, electro-hydraulic control system and tractor
Technical Field
The invention relates to the technical field of power gear shifting, in particular to a low-pressure control valve bank, an electro-hydraulic control system and a tractor.
Background
The power shifting tractor as a development trend of the tractor becomes one of core technologies of the development of the tractor, and the power shifting tractor is rapidly developed in China in recent years. The power gear shifting technology is that under the condition of uninterrupted power, the transmission gear shifting is realized through an electro-hydraulic control system, and the electro-hydraulic control system is the key of the power gear shifting technology. The low-pressure control system is a main component of an electro-hydraulic control system in the power gear shifting technology, and the combination and braking of the rear output PTO, the front and rear differentials, the four-wheel drive, the AMT cylinder and the separation and combination control of the wet clutch are realized through the low-pressure control system.
However, the existing low-pressure system control mode is that four independent valve blocks respectively control different functions, the installation space of the four valve blocks is large, the pipe distribution is complex, the arrangement of the valve blocks is inconvenient for a tractor with narrow space, and the cost of the four independent control valve blocks is high.
Disclosure of Invention
The invention aims to solve the technical problem of the prior art and provides a low-pressure control valve group, an electro-hydraulic control system and a tractor.
The technical scheme for solving the technical problems is as follows:
a low pressure control valve block comprising: the oil return device comprises an oil inlet pipeline, an oil return pipeline and a first electromagnetic valve group, a second electromagnetic valve group, a third electromagnetic valve group, a first electromagnetic valve and a second electromagnetic valve which are connected between the oil inlet pipeline and the oil return pipeline, wherein the first electromagnetic valve group is connected with an AMT (automated mechanical transmission) oil cylinder module, the second electromagnetic valve group is connected with a rear power output shaft, the third electromagnetic valve group is connected with a clutch group used for controlling gears, the first electromagnetic valve is connected with a clutch used for controlling four-wheel drive, and the second electromagnetic valve is connected with a differential mechanism.
Another technical solution of the present invention for solving the above technical problems is as follows:
an electro-hydraulic control system comprises the low-pressure control valve bank in the technical scheme.
Another technical solution of the present invention for solving the above technical problems is as follows:
a tractor comprises the electro-hydraulic control system according to the technical scheme.
The invention has the beneficial effects that: the low-pressure control valve bank provided by the invention is suitable for function control of an electro-hydraulic control system in a power gear-shifting tractor, and a plurality of electromagnetic valve banks are communicated by loop pipelines and are respectively connected with different functions of the electro-hydraulic control system, so that high integration of the low-pressure control valve bank is realized, the compact valve body design enables the installation space to be smaller, the pipeline arrangement to be more convenient, and the cost is effectively reduced.
Advantages of additional aspects of the invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention.
Drawings
FIG. 1 is a schematic diagram of a structural framework for providing an embodiment of a low pressure control valve assembly of the present invention;
fig. 2 is a schematic structural diagram of a low pressure control valve assembly according to another embodiment of the present invention.
Detailed Description
The principles and features of this invention are described below in conjunction with the following drawings, which are set forth to illustrate, but are not to be construed to limit the scope of the invention.
As shown in fig. 1, a schematic structural framework diagram is provided for an embodiment of a low pressure control valve assembly of the present invention, the low pressure control valve assembly includes: oil inlet pipeline 100, return oil pipeline 200 and connect first solenoid valve group 10, second solenoid valve group 20, third solenoid valve group 30, first solenoid valve 40 and second solenoid valve 50 between oil inlet pipeline 100 and return oil pipeline 200, wherein, first solenoid valve group 10 is connected with AMT cylinder module, second solenoid valve group 20 is connected with back power take off axle, third solenoid valve group 30 is connected with the clutch group that is used for controlling the fender position, first solenoid valve 40 is connected with the clutch that is used for controlling four drives, second solenoid valve 50 is connected with differential mechanism.
It should be noted that each electromagnetic valve group may include at least one electromagnetic valve, the type of the electromagnetic valve may be determined according to the connected function module, for example, the electromagnetic valve group may include a proportional electromagnetic valve and an on-off electromagnetic valve, an oil inlet of each electromagnetic valve is communicated with the oil inlet pipeline 100, an oil outlet is communicated with the oil return pipeline 200, and another oil outlet is communicated with different function modules, so that after the oil enters the low-pressure control valve group through the oil inlet pipeline 100, the working states of different electromagnetic valves may be controlled according to actual requirements, so that the oil flows in different electromagnetic valves through the oil return pipeline 200, and high integration of the low-pressure control valve group is.
For example, taking the first electromagnetic valve 40 as an example, it may be a two-position three-way switch electromagnetic valve, the oil inlet is communicated with the oil inlet pipeline 100, the low-pressure oil enters the two-position three-way switch electromagnetic valve through the oil inlet pipeline 100, when the two-position three-way switch electromagnetic valve is powered on, the control oil enters the clutch for controlling the four-wheel drive of the tractor in the transmission, the clutch is pushed by the piston to be combined, so that the tractor is switched to the four-wheel drive working condition, when the two-position three-way switch electromagnetic valve is powered off, the two-position three-way switch electromagnetic valve is reset, the oil enters the oil return pipeline 200, the oil supply to the clutch for controlling the four-wheel drive of the tractor in the transmission is stopped, and the tractor finishes the four-wheel drive working condition.
The control of the rest functional modules is the same, and the description is omitted, and because different functional modules may need a plurality of electromagnetic valves to control together, for example, different gears, the number of the electromagnetic valves of each electromagnetic valve group can be set according to actual needs.
It should be understood that, for example, the solenoid valves implement the control function, and the oil inlet of each solenoid valve may be configured to communicate with the oil inlet pipeline 100, one of the oil outlets communicates with the oil return pipeline 200, the oil return pipeline 200 only communicates with each solenoid valve, and the other oil outlets may respectively communicate with the oil inlets of the corresponding control modules, thereby implementing the control function. The control end of the electromagnetic valve can be connected with a control system of the vehicle, receives a control signal and conducts power-on and power-off control on each electromagnetic valve according to the control signal.
For example, if the tractor needs to use the differential while working, the electronic control system of the tractor sends a command to the controller to power the second solenoid valve 50, the controller powers the second solenoid valve 50 according to the command, and after the second solenoid valve 50 is powered, the oil is controlled to flow into the differential, so that the differential starts to work.
The low-pressure control valve group that this embodiment provided is applicable to power and shifts the function control of electric hydraulic control system in the tractor, through with a plurality of solenoid valve groups with return circuit pipeline intercommunication, the different functions of connection control electric hydraulic control system have respectively realized the high integration of low-pressure control valve group, and compact valve body design makes installation space littleer, and the pipe arrangement is more convenient, the cost is reduced effectively.
Fig. 2 is a schematic structural diagram provided for another embodiment of the low pressure control valve assembly of the present invention, in which P denotes an oil inlet of an oil inlet pipeline, and T denotes an oil return port of the oil inlet pipeline, and some optional embodiments of the present invention are described below with reference to fig. 2.
Optionally, in some possible embodiments, the first solenoid valve group 10 comprises: first two-position three-way switch solenoid valve 11, second two-position three-way switch solenoid valve 12, third two-position three-way switch solenoid valve 13 and fourth two-position three-way switch solenoid valve 14, wherein:
an oil inlet of the first two-position three-way switching solenoid valve 11, an oil inlet of the second two-position three-way switching solenoid valve 12, an oil inlet of the third two-position three-way switching solenoid valve 13 and an oil inlet of the fourth two-position three-way switching solenoid valve 14 are respectively communicated with an oil inlet pipeline 100, and a first oil outlet of the first two-position three-way switching solenoid valve 11, a first oil outlet of the second two-position three-way switching solenoid valve 12, a first oil outlet of the third two-position three-way switching solenoid valve 13 and a first oil outlet of the fourth two-position three-way switching solenoid valve 14 are respectively communicated with an oil return pipeline 200;
the second oil outlet of the first two-position three-way switch electromagnetic valve 11 is connected with the rodless cavity of the first AMT cylinder, the second oil outlet of the second two-position three-way switch electromagnetic valve 12 is connected with the rodless cavity of the second AMT cylinder, the second oil outlet of the third two-position three-way switch electromagnetic valve 13 is connected with the rodless cavity of the third AMT cylinder, and the second oil outlet of the fourth two-position three-way switch electromagnetic valve 14 is connected with the rodless cavity of the fourth AMT cylinder.
It should be noted that, in a conventional tractor, only 1 AMT cylinder is provided, and due to considerations such as cost and circuit layout, the conventional tractor can only provide power output of 1 gear, and therefore, the gear shifting selectivity of the conventional tractor is very low. On the basis of the low-pressure control valve group, the invention realizes that the electromagnetic valve is arranged in a small space to control four different AMT cylinders, thereby realizing the switching of four gears and having the advantage of simple circuit arrangement. In fig. 2, TH, TL, TN, and TM denote pressure measurement ports of the AMT cylinder.
The operation of the first solenoid valve group 10 will be explained below.
The first two-position three-way switch electromagnetic valve 11 is electrified, low-pressure control hydraulic oil enters a rodless cavity of a first AMT oil cylinder, a piston rod extends out to drive a shifting fork to move and is combined with a synchronizer connected with the shifting fork, the tractor is switched to an H gear, and the H gear can be a high gear;
the second two-position three-way switch electromagnetic valve 12 is electrified, low-pressure control hydraulic oil enters a rodless cavity of a second AMT oil cylinder, a piston rod extends out to drive a shifting fork to move and is combined with a synchronizer connected with the shifting fork, the tractor is switched to an L gear, and the L gear can be a medium-low gear;
the third two-position three-way switch electromagnetic valve 13 is electrified, low-pressure control hydraulic oil enters a rodless cavity of a third AMT oil cylinder, a piston rod extends out to drive a shifting fork to move and is combined with a synchronizer connected with the shifting fork, the tractor is switched to an N gear, and the N gear can be a low gear;
the fourth two-position three-way switch electromagnetic valve 14 is electrified, low-pressure control hydraulic oil enters a rod-free cavity of a fourth AMT oil cylinder, a piston rod extends out to drive a shifting fork to move, the shifting fork is combined with a synchronizer connected with the shifting fork, the tractor is switched to an M gear, and the M gear can be a middle gear or a high gear.
It should be understood that different gears are determined by different gear sizes of the synchronizer, and the structure of the synchronizer is common knowledge in the art and is not described in detail herein.
It should be understood that the principle of controlling the AMT cylinder by the solenoid valve is well known in the art and will not be described herein.
4 two-position three-way switch electromagnetic valves are arranged to respectively control 4 AMT cylinders, and the low-pressure control valve bank provided by the invention is combined, high-level, middle-level and low-level four-level gear shifting of the AMT cylinders can be realized with minimum space occupation, so that multi-level gear shifting can be realized by matching with a clutch, the number of stages of gear shifting of a tractor can be improved, and the low-pressure control valve bank provided by the embodiment is highly integrated, so that the occupied space is smaller, and the implementation in the tractor is easy.
Optionally, in some possible embodiments, the second solenoid valve group 20 comprises: two-position four-way switch solenoid valve 21 and first two-position three-way proportional solenoid valve 22, wherein:
an oil inlet of the first two-position three-way proportional solenoid valve 22 is communicated with an oil inlet pipeline 100, a first oil outlet of the first two-position three-way proportional solenoid valve 22 is communicated with an oil return pipeline 200, and a second oil outlet of the first two-position three-way proportional solenoid valve 22 is communicated with an oil inlet of the two-position four-way switching solenoid valve 21;
the first oil outlet of the two-position four-way switching solenoid valve 21 is communicated with the oil return pipeline 200, and the second oil outlet and the third oil outlet of the two-position four-way switching solenoid valve 21 are connected with the rear power output shaft.
In fig. 2, PTO and PTOB represent two oil inlets of the rear power take-off shaft, and TPTO and TPTOB represent pressure ports of the rear power take-off shaft.
The operation of the second solenoid valve group 20 will be described below.
The two-position four-way switch electromagnetic valve 21 and the first two-position three-way proportional electromagnetic valve 22 jointly control the rear power output shaft, the two-position four-way switch electromagnetic valve 21 is powered off, the first two-position three-way proportional electromagnetic valve 22 is powered on, and the rear power output shaft starts to output power; the two-position four-way switch electromagnetic valve 21 and the first two-position three-way proportional electromagnetic valve 22 are simultaneously de-energized, and the rear power output shaft stops outputting power; the two-position four-way switch electromagnetic valve 21 and the first two-position three-way proportional electromagnetic valve 22 are simultaneously electrified to brake the rear power output shaft.
It should be understood that the principle of the solenoid controlled rear power take off shaft is well known in the art and will not be described in detail herein.
The two-position four-way switching electromagnetic valve 21 and the first two-position three-way proportional electromagnetic valve 22 jointly control the rear power output shaft, power output, stop and braking of the rear power output shaft can be achieved through the minimum number of electromagnetic valves, and space occupation and cost are further reduced.
Optionally, in some possible embodiments, the third electromagnetic valve group 30 comprises: a second two-position three-way proportional solenoid valve 31, a third two-position three-way proportional solenoid valve 32, a fourth two-position three-way proportional solenoid valve 33, a fifth two-position three-way proportional solenoid valve 34, a sixth two-position three-way proportional solenoid valve 35, and a seventh two-position three-way proportional solenoid valve 36, wherein:
an oil inlet of the second two-position three-way proportional solenoid valve 31, an oil inlet of the third two-position three-way proportional solenoid valve 32, an oil inlet of the fourth two-position three-way proportional solenoid valve 33, an oil inlet of the fifth two-position three-way proportional solenoid valve 34, an oil inlet of the sixth two-position three-way proportional solenoid valve 35 and an oil inlet of the seventh two-position three-way proportional solenoid valve 36 are respectively communicated with an oil inlet pipeline 100, and a first oil outlet of the second two-position three-way proportional solenoid valve 31, a first oil outlet of the third two-position three-way proportional solenoid valve 32, a first oil outlet of the fourth two-position three-way proportional solenoid valve 33, a first oil outlet of the fifth two-position three-way proportional solenoid valve 34, a first oil outlet of the sixth two-position three-way proportional solenoid valve 35 and a first oil outlet of the seventh two-position three-way proportional solenoid valve 36 are respectively communicated with an oil return pipeline 200;
the second oil outlet of the second two-position three-way proportional solenoid valve 31 is connected with the first clutch in the clutch set, the second oil outlet of the third two-position three-way proportional solenoid valve 32 is connected with the second clutch in the clutch set, the second oil outlet of the fourth two-position three-way proportional solenoid valve 33 is connected with the third clutch in the clutch set, the second oil outlet of the fifth two-position three-way proportional solenoid valve 34 is connected with the fourth clutch in the clutch set, the second oil outlet of the sixth two-position three-way proportional solenoid valve 35 is connected with the fifth clutch in the clutch set, and the second oil outlet of the seventh two-position three-way proportional solenoid valve 36 is connected with the sixth clutch in the clutch set.
In fig. 2, A, B, C, D, E and F respectively indicate oil inlets of each clutch, and TA, TB, TC, TD, TE and TF respectively indicate pressure measurement ports of each clutch.
The operation of the third solenoid valve group 30 will be described below.
It should be noted that the clutch group is arranged in the transmission, wherein 3 clutches can be arranged on one transmission shaft of the transmission, the other 3 clutches can be arranged on the other transmission shaft of the transmission, wherein 1 clutch can control the reverse of the vehicle, the other 5 clutches can control the forward of the vehicle, and every two electromagnetic valves can be mutually matched to combine the clutches on the two transmission shafts, thereby realizing different gear control.
For convenience of explanation, the control of the different gears will be described below without considering reverse gear and only forward gear, except that the clutch controlling reverse gear, 2 clutches on one transmission shaft are combined with 3 clutches on the other transmission shaft to realize 6 gears in total, which will be described in detail below.
Assuming that the first clutch, the second clutch and the third clutch are located on the first transmission shaft, the fourth clutch, the fifth clutch and the sixth clutch are located on the second transmission shaft, and the first clutch is in reverse gear:
the third two-position three-way proportional solenoid valve 32 and the fifth two-position three-way proportional solenoid valve 34 are powered on simultaneously, low-pressure control hydraulic oil enters a second clutch piston on the first transmission shaft and a fourth clutch piston on the second transmission shaft respectively, the two clutches are combined respectively under the pushing of the pistons, and the tractor runs in a forward 1 gear;
the third two-position three-way proportional solenoid valve 32 and the sixth two-position three-way proportional solenoid valve 35 are powered on simultaneously, low-pressure control hydraulic oil enters a second clutch piston on the first transmission shaft and a fifth clutch piston on the second transmission shaft respectively, the two clutches are combined respectively under the pushing of the pistons, and the tractor runs in a forward 2-gear;
the third two-position three-way proportional solenoid valve 32 and the seventh two-position three-way proportional solenoid valve 36 are powered on simultaneously, low-pressure control hydraulic oil enters a second clutch piston on the first transmission shaft and a sixth clutch piston on the second transmission shaft respectively, the two clutches are combined respectively under the pushing of the pistons, and the tractor runs in a forward 3-gear;
the fourth two-position three-way proportional solenoid valve 33 and the fifth two-position three-way proportional solenoid valve 34 are simultaneously electrified, low-pressure control hydraulic oil respectively enters a third clutch piston on the first transmission shaft and a fourth clutch piston on the second transmission shaft, the two clutches are respectively combined under the pushing of the pistons, and the tractor runs in a forward 4-gear mode;
the fourth two-position three-way proportional solenoid valve 33 and the sixth two-position three-way proportional solenoid valve 35 are powered on simultaneously, low-pressure control hydraulic oil enters a third clutch piston on the first transmission shaft and a fifth clutch piston on the second transmission shaft respectively, the two clutches are combined respectively under the pushing of the pistons, and the tractor runs in a forward 5-gear mode;
the fourth two-position three-way proportional solenoid valve 33 and the seventh two-position three-way proportional solenoid valve 36 are energized simultaneously, the low-pressure control hydraulic oil enters the third clutch piston on the first transmission shaft and the sixth clutch piston on the second transmission shaft respectively, the two clutches are combined respectively under the pushing of the pistons, and the tractor runs in a forward 6-gear mode.
It will be appreciated that the principles of solenoid controlled clutches are well known in the art and will not be described in detail herein.
Through different clutches of a plurality of solenoid valve control, can realize the multistage of tractor and shift, furthermore, AMT cylinder control synchronizer can also provide 4 fender position, it keeps off to be high fender H respectively, well high fender M keeps off, well low fender L keeps off and low fender N keeps off, the gearshift of reunion clutch pack, can realize shifting of super multistage number, can realize 4X 6 for 24 fender positions, thereby the mode that this embodiment provided can use the minimum space to select for the tractor provides more fender positions, the tractor that agrees with the space very much less uses, not only can reduce the space occupation of electric hydraulic control system, can also reduce the pipe arrangement, reduce electric hydraulic control system's complexity, and reduce the cost, the problem that the tractor keeps off the position few, and can not increase the volume of tractor.
Optionally, in some possible embodiments, the oil inlet of the first two-position three-way proportional solenoid valve 22, the oil inlet of the second two-position three-way proportional solenoid valve 31, the oil inlet of the third two-position three-way proportional solenoid valve 32, the oil inlet of the fourth two-position three-way proportional solenoid valve 33, the oil inlet of the fifth two-position three-way proportional solenoid valve 34, the oil inlet of the sixth two-position three-way proportional solenoid valve 35, and the oil inlet of the seventh two-position three-way proportional solenoid valve 36 are respectively provided with a filter screen 60.
It should be noted that, the filter screen 60 can be fixed in the oil path, and can filter the impurity in the hydraulic oil, guarantee the cleanliness of the hydraulic oil entering the proportional solenoid valve, prevent the proportional solenoid valve core from being stuck, thereby improve the service life of the valve core.
Optionally, in some possible embodiments, the first solenoid valve 40 comprises: an oil inlet of the fifth two-position three-way switching solenoid valve 41 is communicated with the oil inlet pipeline 100, a first oil outlet of the fifth two-position three-way switching solenoid valve 41 is communicated with the oil return pipeline 200, and a second oil outlet of the fifth two-position three-way switching solenoid valve 41 is connected with a clutch for controlling four-wheel drive.
A clutch for controlling the four-wheel drive is also provided in the transmission, and oil can push the clutch to be combined through a clutch piston.
In fig. 2, 4WD denotes an oil inlet port for controlling the four-wheel drive clutch, and T4WD denotes a pressure measuring port for controlling the four-wheel drive clutch.
The operation of the first solenoid valve 40 will be explained below.
The fifth two-position three-way switch electromagnetic valve 41 is electrified, low-pressure control hydraulic oil enters a clutch piston, the clutch is combined under the pushing of the piston, and the tractor is switched to a four-wheel drive working condition; and the fifth two-position three-way switch electromagnetic valve 41 is powered off, the low-pressure control hydraulic oil stops entering the clutch piston, the piston is reset, the clutch is separated, and the tractor finishes the four-wheel drive working condition.
It will be appreciated that the principles of solenoid controlled clutches, and the principles of clutches controlling four-wheel drive of a vehicle, are well known in the art and will not be described in detail herein.
Optionally, in some possible embodiments, the second solenoid valve 50 comprises: an oil inlet of the sixth two-position three-way switching solenoid valve 51 is communicated with the oil inlet pipeline 100, a first oil outlet of the sixth two-position three-way switching solenoid valve 51 is communicated with the oil return pipeline 200, and a second oil outlet of the fifth two-position three-way switching solenoid valve 41 is connected with the differential.
In fig. 2, DL denotes an oil inlet of the differential, and TDL denotes a pressure measuring port of the differential.
The operation of the second solenoid valve 50 will be described below.
The sixth two-position three-way switch electromagnetic valve 51 is electrified, low-pressure control hydraulic oil enters the differential mechanism, and the tractor differential mechanism starts to work; the sixth two-position three-way switch electromagnetic valve 51 is de-energized, and the tractor differential stops working.
It will be appreciated that the principles of solenoid valve controlled differentials are well known in the art and will not be described in detail herein.
Optionally, in some possible embodiments, the method further includes: the pressure sensor 70 and the accumulator 80, and the pressure sensor 70 and the accumulator 80 are communicated with the oil inlet pipeline 100.
It should be understood that the pressure sensor 70 is provided with a detection end, which can be directly inserted into the oil inlet pipe to detect the pressure of the oil in the oil inlet pipe 100, and the accumulator 80 has a function of absorbing the pressure fluctuation, so as to eliminate the pressure fluctuation of the hydraulic oil entering the low-pressure control valve set, ensure the stability of the control pressure, and further improve the gear shifting control performance.
Alternatively, the pressure sensor 70 and the accumulator 80 may be provided at the inlet of the low pressure control valve block in the oil feed line 100, thereby more accurately monitoring and controlling the oil pressure in the oil feed line 100.
It should be understood that the principles of operation of the pressure sensor 70 and the accumulator 80 are well known in the art and will not be described in detail herein.
It is to be understood that some or all of the various embodiments described above may be included in some embodiments.
The invention further provides an electro-hydraulic control system which comprises the low-pressure control valve bank disclosed in any of the above embodiments.
The system also comprises other devices or modules for realizing electro-hydraulic control, for example, the system also comprises a controller, a gearbox, a rear power output shaft, an AMT (automated mechanical transmission) oil cylinder, a differential and the like, output ports of all electromagnetic valves in the low-pressure control valve group can be respectively connected with the gearbox, the rear power output shaft, the AMT oil cylinder, the differential and the like, and the corresponding electromagnetic valves are opened according to the control of the controller, so that the control of functions such as speed change, gear shifting, differential locking and the like is realized.
The invention also provides a tractor comprising the electro-hydraulic control system disclosed in any of the above embodiments.
Further comprising: the body of the vehicle and other necessary structures such as the engine, tires, axles and gears, etc.
The reader should understand that in the description of this specification, reference to the description of the terms "one embodiment," "some embodiments," "an example," "a specific example," or "some examples," etc., means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above are not necessarily intended to refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Furthermore, various embodiments or examples and features of different embodiments or examples described in this specification can be combined and combined by one skilled in the art without contradiction.
In the several embodiments provided in the present application, it should be understood that the disclosed apparatus and method may be implemented in other ways. For example, the above-described method embodiments are merely illustrative, and for example, the division of steps into only one logical functional division may be implemented in practice in another way, for example, multiple steps may be combined or integrated into another step, or some features may be omitted, or not implemented.
While the invention has been described with reference to specific embodiments, it will be understood by those skilled in the art that various changes in form and details may be made therein without departing from the spirit and scope of the invention as defined by the appended claims. Therefore, the protection scope of the present invention shall be subject to the protection scope of the claims.

Claims (10)

1. A low pressure control valve block, comprising: the oil return device comprises an oil inlet pipeline, an oil return pipeline and a first electromagnetic valve group, a second electromagnetic valve group, a third electromagnetic valve group, a first electromagnetic valve and a second electromagnetic valve which are connected between the oil inlet pipeline and the oil return pipeline, wherein the first electromagnetic valve group is connected with an AMT (automated mechanical transmission) oil cylinder module, the second electromagnetic valve group is connected with a rear power output shaft, the third electromagnetic valve group is connected with a clutch group used for controlling gears, the first electromagnetic valve is connected with a clutch used for controlling four-wheel drive, and the second electromagnetic valve is connected with a differential mechanism.
2. The set of low pressure control valves of claim 1, wherein the first set of solenoid valves comprises: first two three-way switch solenoid valve, second two three-way switch solenoid valve, third two three-way switch solenoid valve and fourth two three-way switch solenoid valve, wherein:
an oil inlet of the first two-position three-way switching solenoid valve, an oil inlet of the second two-position three-way switching solenoid valve, an oil inlet of the third two-position three-way switching solenoid valve and an oil inlet of the fourth two-position three-way switching solenoid valve are respectively communicated with the oil inlet pipeline, and a first oil outlet of the first two-position three-way switching solenoid valve, a first oil outlet of the second two-position three-way switching solenoid valve, a first oil outlet of the third two-position three-way switching solenoid valve and a first oil outlet of the fourth two-position three-way switching solenoid valve are respectively communicated with the oil return pipeline;
the second oil outlet of the first two-position three-way switch solenoid valve is connected with a rodless cavity of the first AMT cylinder, the second oil outlet of the second two-position three-way switch solenoid valve is connected with a rodless cavity of the second AMT cylinder, the second oil outlet of the third two-position three-way switch solenoid valve is connected with a rodless cavity of the third AMT cylinder, and the second oil outlet of the fourth two-position three-way switch solenoid valve is connected with a rodless cavity of the fourth AMT cylinder.
3. The set of low pressure control valves of claim 1, wherein the second set of solenoid valves comprises: two-position four-way switch solenoid valve and first two-position three-way proportional solenoid valve, wherein:
an oil inlet of the first two-position three-way proportional solenoid valve is communicated with the oil inlet pipeline, a first oil outlet of the first two-position three-way proportional solenoid valve is communicated with the oil return pipeline, and a second oil outlet of the first two-position three-way proportional solenoid valve is communicated with an oil inlet of the two-position four-way switching solenoid valve;
and a first oil outlet of the two-position four-way switching solenoid valve is communicated with the oil return pipeline, and a second oil outlet and a third oil outlet of the two-position four-way switching solenoid valve are connected with the rear power output shaft.
4. The set of low pressure control valves of claim 3, wherein the third set of solenoid valves comprises: second two three-position proportional solenoid valve, third two three-position proportional solenoid valve, fourth two three-position proportional solenoid valve, fifth two three-position proportional solenoid valve, sixth two three-position proportional solenoid valve and seventh two three-position proportional solenoid valve, wherein:
an oil inlet of the second two-position three-way proportional solenoid valve, an oil inlet of the third two-position three-way proportional solenoid valve, an oil inlet of the fourth two-position three-way proportional solenoid valve, an oil inlet of the fifth two-position three-way proportional solenoid valve, an oil inlet of the sixth two-position three-way proportional solenoid valve and an oil inlet of the seventh two-position three-way proportional solenoid valve are respectively communicated with the oil inlet pipeline, and a first oil outlet of the second two-position three-way proportional solenoid valve, a first oil outlet of the third two-position three-way proportional solenoid valve, a first oil outlet of the fourth two-position three-way proportional solenoid valve, a first oil outlet of the fifth two-position three-way proportional solenoid valve, a first oil outlet of the sixth two-position three-way proportional solenoid valve and a first oil outlet of;
the second oil outlet of the second two-position three-way proportional solenoid valve is connected with the first clutch in the clutch group, the second oil outlet of the third two-position three-way proportional solenoid valve is connected with the second clutch in the clutch group, the second oil outlet of the fourth two-position three-way proportional solenoid valve is connected with the third clutch in the clutch group, the second oil outlet of the fifth two-position three-way proportional solenoid valve is connected with the fourth clutch in the clutch group, the second oil outlet of the sixth two-position three-way proportional solenoid valve is connected with the fifth clutch in the clutch group, and the second oil outlet of the seventh two-position three-way proportional solenoid valve is connected with the sixth clutch in the clutch group.
5. The low pressure control valve group of claim 4, wherein the oil inlet of the first two-position three-way proportional solenoid valve, the oil inlet of the second two-position three-way proportional solenoid valve, the oil inlet of the third two-position three-way proportional solenoid valve, the oil inlet of the fourth two-position three-way proportional solenoid valve, the oil inlet of the fifth two-position three-way proportional solenoid valve, the oil inlet of the sixth two-position three-way proportional solenoid valve, and the oil inlet of the seventh two-position three-way proportional solenoid valve are respectively provided with a filter screen.
6. The set of low pressure control valves of claim 1, wherein the first solenoid valve comprises: the oil inlet of the fifth two-position three-way switch solenoid valve is communicated with the oil inlet pipeline, the first oil outlet of the fifth two-position three-way switch solenoid valve is communicated with the oil return pipeline, and the second oil outlet of the fifth two-position three-way switch solenoid valve is connected with a clutch used for controlling four-wheel drive.
7. The set of low pressure control valves of claim 1, wherein the second solenoid valve comprises: the oil inlet of the sixth two-position three-way switch solenoid valve is communicated with the oil inlet pipeline, the first oil outlet of the sixth two-position three-way switch solenoid valve is communicated with the oil return pipeline, and the second oil outlet of the fifth two-position three-way switch solenoid valve is connected with the differential mechanism.
8. The set of low pressure control valves of any of claims 1 to 7, further comprising: the pressure sensor and the energy accumulator are communicated with the oil inlet pipeline.
9. Electro-hydraulic control system, characterized in that it comprises a low-pressure control valve group according to any one of claims 1 to 8.
10. A tractor comprising an electro-hydraulic control system according to claim 9.
CN202110843369.9A 2021-07-26 2021-07-26 Low-pressure control valve group, electro-hydraulic control system and tractor Pending CN113431817A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202110843369.9A CN113431817A (en) 2021-07-26 2021-07-26 Low-pressure control valve group, electro-hydraulic control system and tractor

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202110843369.9A CN113431817A (en) 2021-07-26 2021-07-26 Low-pressure control valve group, electro-hydraulic control system and tractor

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CN113431817A true CN113431817A (en) 2021-09-24

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113915325A (en) * 2021-09-28 2022-01-11 常州华创航空科技有限公司 Full-power gear shifting gearbox hydraulic and lubricating system and gearbox

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113915325A (en) * 2021-09-28 2022-01-11 常州华创航空科技有限公司 Full-power gear shifting gearbox hydraulic and lubricating system and gearbox
CN113915325B (en) * 2021-09-28 2023-09-12 江苏常发农业装备股份有限公司 Full power gear shifting gearbox hydraulic pressure and lubrication system and gearbox

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