CN108571584A - A kind of full power shift commutation gear box of tractor hydraulic control system - Google Patents
A kind of full power shift commutation gear box of tractor hydraulic control system Download PDFInfo
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- CN108571584A CN108571584A CN201810674796.7A CN201810674796A CN108571584A CN 108571584 A CN108571584 A CN 108571584A CN 201810674796 A CN201810674796 A CN 201810674796A CN 108571584 A CN108571584 A CN 108571584A
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- oil inlet
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- 230000001050 lubricating effect Effects 0.000 claims abstract description 47
- 238000001816 cooling Methods 0.000 claims abstract description 43
- 239000012530 fluid Substances 0.000 claims abstract description 38
- 150000001875 compounds Chemical class 0.000 claims abstract description 19
- 239000002828 fuel tank Substances 0.000 claims abstract description 17
- 238000006073 displacement reaction Methods 0.000 claims abstract description 4
- 238000005461 lubrication Methods 0.000 claims description 68
- 239000007921 spray Substances 0.000 claims description 31
- 239000000203 mixture Substances 0.000 claims description 8
- 239000000314 lubricant Substances 0.000 claims description 4
- 238000009825 accumulation Methods 0.000 claims 1
- 238000001914 filtration Methods 0.000 abstract description 6
- 230000015556 catabolic process Effects 0.000 abstract 1
- 230000009885 systemic effect Effects 0.000 abstract 1
- 239000003921 oil Substances 0.000 description 107
- 239000007788 liquid Substances 0.000 description 12
- 230000000694 effects Effects 0.000 description 9
- 238000010586 diagram Methods 0.000 description 4
- 238000005516 engineering process Methods 0.000 description 3
- 238000004519 manufacturing process Methods 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 239000000446 fuel Substances 0.000 description 2
- 239000012535 impurity Substances 0.000 description 2
- 238000012827 research and development Methods 0.000 description 2
- 230000035939 shock Effects 0.000 description 2
- 239000013589 supplement Substances 0.000 description 2
- 238000005299 abrasion Methods 0.000 description 1
- 230000002411 adverse Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 230000000903 blocking effect Effects 0.000 description 1
- 238000004140 cleaning Methods 0.000 description 1
- 230000003749 cleanliness Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 239000010730 cutting oil Substances 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 239000003344 environmental pollutant Substances 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000002386 leaching Methods 0.000 description 1
- 231100000719 pollutant Toxicity 0.000 description 1
- 230000001681 protective effect Effects 0.000 description 1
- 230000010349 pulsation Effects 0.000 description 1
- 238000004064 recycling Methods 0.000 description 1
- 230000009897 systematic effect Effects 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0402—Cleaning of lubricants, e.g. filters or magnets
- F16H57/0404—Lubricant filters
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0412—Cooling or heating; Control of temperature
- F16H57/0413—Controlled cooling or heating of lubricant; Temperature control therefor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0434—Features relating to lubrication or cooling or heating relating to lubrication supply, e.g. pumps ; Pressure control
- F16H57/0435—Pressure control for supplying lubricant; Circuits or valves therefor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/38—Control of exclusively fluid gearing
- F16H61/40—Control of exclusively fluid gearing hydrostatic
Abstract
A kind of full power shift commutation gear box of tractor hydraulic control system category agricultural machinery technological field.The huge discharge oil discharge outlet of duplex gear pump in oil supply subsystem of the present invention and the control guide end of hydraulic control by-passing valve in the oil inlet and cooling and lubricating subsystem of cooler in cooling and lubricating subsystem are connected to；The small displacement oil discharge outlet of duplex gear pump is connected to the oil inlet of pilot operated compound relief valve in clutch control subsystem in oil supply subsystem；The overflow hydraulic fluid port of two level overflow valve in cooling and lubricating subsystem is connected to the oil return opening of the fuel tank in oil supply subsystem；The overflow hydraulic fluid port of pilot operated compound relief valve is connected to the branch where the oil inlet of the cooler in cooling and lubricating subsystem in clutch control subsystem.The present invention, as dynamical element, can save hydraulic system space using duplex gear pump；A hydraulic control by-passing valve is set in the cooling and lubricating subsystem of the present invention, can avoid occurring the problem of leading to systemic breakdown due to cooling and filtering branch blocks.
Description
Technical field
The invention belongs to agricultural machinery technological fields, and in particular to a kind of full power shift commutation gear box of tractor hydraulic pressure
Control system.
Background technology
The farm tractor in China is generally shifted gears using traditional engaging sleeve or synchronizer at present, and this tradition
Shift mode have the disadvantages that：1. often gear number is more for farm tractor, driver is cumbersome in shift, causes
Driving difficulty increases, and accelerates driver fatigue.2. attrition is very big between each part in gearbox, lead in case high temperature simultaneously
Shorten the service life of part.3. in shift process, the phenomenon that inevitably will appear power interruption, to shift gears
Big energy is lost in journey.
Power shifting technology has as research and development direction new in field of agricultural machinery compared with traditional shift technology
Following advantages：1. driver's gear shift operation is simple, mitigate the working strength of driver.2. effectively reducing in gearbox between part
Abrasion condition.3. uninterruptedly shift and switch operation may be implemented, reduce in shift process caused by power interruption
Energy loss situation.
In the research and development of tractor dynamic power shift gear box, including cooling and lubricating subsystem and clutch control subsystem
The relevant design of hydraulic system including system and oil supply subsystem is a particularly important ring.
In the design of Hydraulic System of existing dynamic power shift gear box, using two hydraulic pumps come respectively cooling and lubricating system
It is energized with clutch control, while entire design of Hydraulic System being worked at two independent systems.This design
Mode not only increases Hydraulic Elements quantity, and hydraulic system is made to become more complicated, and improves production cost, also results in hydraulic pressure
System loss more energy.
In terms of clutch control circuit, in the hydraulic system of current tractor dynamic power shift gear box, often exist
The problem of the shift control valve core core clamping stagnation obstruction caused by oil cleanliness is inadequate.Additionally, due in clutch
During detaching with combination, it will produce hydraulic shock and the problem of shaking of shifting gears, shift work had adverse effect on.
In terms of the lubricating system of dynamic power shift gear box, the lubricating system designed at present is usually splash lubrication or pressure profit
It is sliding.The advantages of lubrication of splashing, is to enormously simplify the design of lubricating system, but due to the lubrication feature of splashing lubrication itself, becomes
The space layout of related components can be very limited in fast case, in addition for lubricant effect, splash lubrication and other lubrication sides
Formula is compared to often poor.The advantages of forced feed lubrication, is accurately control the lubricating place of fluid, and can ensure certain
Lubrication pressure, lubricant effect is preferable.But the lubricating loop systematic comparison needed for forced feed lubrication is complicated, can increase design difficulty,
Increase manufacturing cost.
Invention content
The purpose of the present invention is to provide a kind of Hydraulic Elements are few, full power simple for structure shift commutation tractor speed change
Case hydraulic control system.
The present invention is made of cooling and lubricating subsystem I, oil supply subsystem II and clutch control subsystem III, wherein fuel feeding
The huge discharge oil discharge outlet i of duplex gear pump 9 in subsystem II is connected to the oil inlet of cooler 1 in cooling and lubricating subsystem I.
The huge discharge oil discharge outlet i of duplex gear pump 9 in oil supply subsystem II also with hydraulic control by-passing valve 7 in cooling and lubricating subsystem I
Control the connection of guide end.The small displacement oil discharge outlet j of duplex gear pump 9 in oil supply subsystem II and clutch control subsystem III
The oil inlet of middle pilot operated compound relief valve 14 is connected to.The overflow hydraulic fluid port of two level overflow valve 5 in cooling and lubricating subsystem I with for foxy old hand
The oil return opening of fuel tank 12 in system II is connected to.In clutch control subsystem III the overflow hydraulic fluid port of pilot operated compound relief valve 14 with it is cold
But the branch connection where the oil inlet of the cooler 1 in lubrication subsystem I.
The cooling and lubricating subsystem I is by cooler 1, by-passing valve I 2, forced feed lubrication oilhole group 3, spray lubrication oilhole
Group 4, two level overflow valve 5, level-one overflow valve 6, hydraulic control by-passing valve 7 and filter 8 form, and wherein forced feed lubrication oilhole group 3 is by 22
A forced feed lubrication oilhole composition；Spray lubrication oilhole group 4 is made of 5 spray lubrication oilholes.The oil inlet and mistake of by-passing valve I 2
Branch connection where the oil inlet of filter 8, the oil outlet of by-passing valve I 2 are connected to the branch where the oil outlet of filter 8.
22 forced feed lubrication oilholes of forced feed lubrication oilhole group 3 are located in full power shift commutation gear box of tractor on each axis,
And it is corresponding with bearing to be lubricated on axis, clutch, the oil outlet and level-one overflow valve 6 of forced feed lubrication oil circuit and filter 8
Branch connection between oil inlet.5 spray lubrication oilholes of spray lubrication oilhole group 4 are located at full power shift commutation tractor
On the spray tube of upper part of gear box, and, the oil inlet of spray lubrication oil circuit and two level overflow valve 5 corresponding with the flank of tooth of spray lubrication is waited for
Branch connection between mouth and the overflow hydraulic fluid port of level-one overflow valve 6.The oil inlet of the oil inlet and cooler 1 of hydraulic control by-passing valve 7
Place branch connection, the oil outlet of hydraulic control by-passing valve 7 are connected to branch where the oil outlet of filter 8, the liquid of hydraulic control by-passing valve 7
Control guide's end first quarter discharge orifice is connected to branch where the oil inlet of cooler 1.The oil inlet of level-one overflow valve 6 and filter 8
Oil outlet connection, the oil outlet of level-one overflow valve 6 is connected to the oil inlet of two level overflow valve 5.
The oil supply subsystem II is by duplex gear pump 9, by-passing valve II 10, coarse filter 11, fuel tank 12 and fine filter 13
Composition, wherein the oil inlet of by-passing valve II 10 is connected to the oil outlet of coarse filter 11, the oil outlet and fine filter of by-passing valve II 10
13 oil outlet connection；The oil inlet of coarse filter 11 is connected to the oil inlet of fine filter 13.The oil discharge outlet of 12 bottom of fuel tank is through essence
Filter 13 is connected to the inlet port of duplex gear pump 9.
The clutch control subsystem III is by pilot operated compound relief valve 14, I group 15 of strainer, ratio electromagnetic switch valve group
16, II group 17 of strainer, wet clutch group 18, pressure sensor group 19 and accumulator 20 form, wherein ratio solenoid directional control valve
Group 16 is made of 10 ratio solenoid directional control valves, and I group 15 of strainer and strainer are made of for II group 17 10 strainers, wet clutch
Group 18 is made of 10 wet clutches, and pressure sensor group 19 is made of 10 pressure sensors.Accumulator 20 is installed on elder generation
Branch road between I group 15 of the oil inlet of conduction overflow valve 14 and strainer.For simultaneously between the control loop of 10 wet clutches
Connection connection, the control loop of each wet clutch is by a ratio solenoid directional control valve, a strainer II, one of strainer I, one
Pressure sensor forms, and the connection relation of each element is as follows：The input terminal of ratio solenoid directional control valve overflows through strainer I and pilot-operated type
Branch connection where flowing the oil inlet of valve 14.Pressure oil of the output end of ratio solenoid directional control valve through strainer II Yu wet clutch
Branch connection where hole.Pressure sensor is installed on the road of the branch between strainer II and the pressure oilhole of wet clutch.
The principle of the present invention and the course of work are as follows：
Enter the fluid of cooling and lubricating subsystem I in the present invention, it is cold to enter cooler (1) progress along lubrication main road f first
But, effect is that the oil liquid temperature of control hydraulic system is in normal working range, ensures that work system is reliable.
During the cooling and lubricating of gearbox, if the fluid supplied to parts contains impurity and other pollutants, meeting
Working condition and service life to parts can all have a great impact, therefore to that will be flowed to through cooler fluid after cooling
Filter 8 is for re-filtering, which ensure that the cleaning of cooling and lubricating fluid is reliable.
In the in parallel by-passing valve 2 in the both sides of filter 8, its object is to：If filter 8 blocks, by-passing valve 2 is beaten
It opens, ensure that the lubrication profit of subsystem.Meanwhile the hydraulic control bypass in parallel on 1 concatenated oil circuit of filter 8 and cooler
Valve 7；The by-passing valve is equipped with a guide end, and guide end is connected to by throttle orifice with lubrication main road f.When filter 8 and cooler 1 are gone here and there
When the oil circuit of connection blocks, the oil pressure that by-passing valve is entered by throttle orifice increases, and guide end controls spool movement, makes the branch
Road is connected to, and ensures that gearbox has enough cutting oils.
Fluid is divided into two-way after the filtering of filter 8, is all the way forced feed lubrication branch g, and another way is spray lubrication branch
h.Every branch road is respectively equipped with throttle orifice, and the effect of throttle orifice is：Can be that entire cooling and lubricating subsystem carries out pressurize.
One level-one overflow valve 6 is installed, which is responsible between the forced feed lubrication branch g and spray lubrication branch h
Control enters the oil liquid pressure at forced feed lubrication oilhole 3, while the fluid that 6 overflow of level-one overflow valve goes out flows to two level overflow valve
5 and spray lubrication oilhole 4, the two level overflow valve 5 is responsible for the oil liquid pressure at control spray lubrication oilhole 4, when two level overflow
When 5 overflow of valve, overflow fluid flows into fuel tank again.Since forced feed lubrication is compared with spray lubrication, the oil liquid pressure of the former needs
Bigger, so the Opening pressure of the level-one overflow valve 6 is greater than the Opening pressure of two level overflow valve 5, to ensure two kinds of lubrications
The oil pressure of mode is different, and then reaches expected lubricant effect.
Since the gearbox gear number of the present invention is more, according to the design arrangement of mechanical driving part, need to pass through clutch
Device control subsystem III controls wet clutch group 18 respectively, to complete gear shift operation.
The fluid controlled for wet clutch group 18 enters clutch control subsystem III from branch c.In control main road e
On, it is connected with an accumulator 20；The effect of the accumulator 20 is：1. loop compensation is revealed and keeps constant pressure in order to control；2. can
It eliminates pulsation and absorbs hydraulic shock, guarantee is provided for the ride comfort of shift process.
Clutch control subsystem III is used as directional control valve, the ratio electromagnetism to change using ratio electromagnetic switch valve group 16
It is two-position three way to valve, which sets there are one spring terminal and an automatically controlled end that can control electromagnetic actuation.Work as electromagnetism
When not having electric current in valve, which is in the normal state position, i.e. normally off；The normality position input terminal port be closed, output end with
Oil return line is connected to, and wet clutch group 18 is in discrete state at this time.When passing through electric current in solenoid valve, the input of the reversal valve
End is connected to output end, and control fluid can respectively enter wet clutch group 18 along oil circuit, at this time at wet clutch group 18
In bonding state.
Ratio solenoid directional control valve the advantage is that compared with other kinds of reversal valve：It can be defeated with proportion of utilization electromagnet
The electromagnetic force gone out so that oil liquid pressure and flow continuously, model- following control signal in proportion and change, its control performance is excellent
In bang-bang control, the electric signal of input can be converted to mechanical quantity output in proportion.It therefore can using ratio solenoid directional control valve
To improve the shift control performance of the ride comfort and gearbox of shift.
The input terminal of the ratio electromagnetic switch valve group 16 is equipped with I group 15 of strainer strainer, while its output end is installed
There is strainer II group 17.The purpose of design that I group 15 of strainer is carried out one to that will enter the fluid of ratio electromagnetic switch valve group 16
Secondary filtering avoids the situation of its spool jams from occurring；The effect of design II group 17 of strainer of installation is：When wet clutch detaches
When, when fluid oil return inside plunger shaft, can enter back into ratio electromagnetic switch valve group 16 for II group 17 through filter screen, ensure that
Reversal valve clamping stagnation situation will not occur due to fluid takes back the impurity in wet clutch during oil return.
Pressure sensor group 19 is installed on the oil circuit between wet clutch group 18 in I group 15 of the strainer, is made
With being：The oil liquid pressure signal real-time delivery of wet clutch can be given to power train control system TCU, be power shifting speed change
The closed-loop control of case shift provides guarantee, while providing related data bearing for the self-learning function of gearbox, can also
The control of entire clutch control subsystem III is set to become more precisely.
In order to ensure that the oil liquid pressure of clutch control subsystem III is stablized, a pilot operated compound relief valve is equipped on branch d
14.The pilot operated compound relief valve 14 is made of main valve and pilot valve two parts, and wherein fluid enters overflow valve and acts directly on main valve
On, when the oil liquid pressure in d branches is higher than the pressure value that guide's valve spring is set up, the spool in pilot valve is opened, wherein
Fluid flow back to fuel tank, while causing main valve plug pressure at two ends uneven, when this pressure difference is more than the active force of main spool spring,
Main valve overflow.The fluid that the 14 main valve overflow of pilot operated compound relief valve goes out enters cooling and lubricating subsystem, and the purpose designed in this way exists
In：It can be on the basis of realizing overflow valve function, the cooling and lubricating subsystem to need flow larger makees flow supplement.
Since cooling and lubricating subsystem I and clutch control subsystem III work normally required flow and pressure not
It is identical, thus for the ease of being respectively controlled to two systems, and simplifying integrated hydraulic system construction, oil supply subsystem II is set
There is a duplex gear pump 9 to be used as dynamical element.Fluid respectively enters branch after the discharge of two oil discharge outlets of the duplex gear pump 9
Fluid in b and branch c, branch b flows to cooling and lubricating subsystem I；Fluid in branch c flows to clutch control subsystem
Ⅲ。
A filter is separately equipped on the main road a of oil supply subsystem II, the filter is by coarse filter 11, fine filter 13
It is formed with by-passing valve 10, the coarse filter 11 is installed in series with by-passing valve 10, and the two is whole in parallel with fine filter 13.Work as duplex-gear
When wheel pump 9 is started to work, fluid enters hydraulic system from fuel tank 12, duplex gear pump 9 is sucked after being filtered by fine filter 13, with complete
At the filtration of fluid.The purpose that the series arm of the coarse filter 11 and by-passing valve 10 designs is：When fine filter 13 is sent out
When raw blocking causes fluid that can not circulate, by-passing valve 10 is opened, and fluid can enter system after the filtering of coarse filter 11, avoid
The failure conditions of filter.
The lubrication and control fuel tank of gearbox is not separately provided in the present invention, the fuel tank 12 in the oil supply subsystem II is
Full power shift commutation gear box of tractor babinet.
The beneficial effects of the present invention are：
The present invention uses dynamical element of the duplex gear pump as two hydraulic circuits, avoid lubrication portion and
Hydraulic system is complicated caused by control section is designed to two autonomous systems, and the excessive problem of amount of parts occurs.And it is each
Partial circuit is compact to design, and the Hydraulic Elements division of labor is distinct, and certain space is saved while simplifying system.
The present invention uses the profit for being combined forced feed lubrication and spray lubrication in terms of the lubrication of dynamic power shift gear box
Sliding mode can need to use suitable lubricating system according to the lubrication of different parts, and avoid adopt to a certain extent
With the system complex caused by the single lubricating system of tradition, it is ineffective the problems such as.
It is set in the cooling and lubricating subsystem of the present invention there are one hydraulic control by-passing valve, the effect of the hydraulic control by-passing valve is：When cold
But when device and filter device branch block, branch oil liquid pressure increases, at the same control the hydraulic control bypass valve core move from
And the fluid in cooling and lubricating subsystem is made to continue to circulate, play the protective effect to the subsystem.
Because cooling and lubricating subsystem is compared with clutch control subsystem, the former required flow bigger, so at this
It is set in the clutch control subsystem of invention there are one pilot operated compound relief valve, which can not only control the subsystem
The oil pressure pressure of system, while oil overflow liquid stream can be made flow supplement into cooling and lubricating subsystem in overflow.
In the clutch control subsystem of the present invention, traditional hydraulically-controlled type proportional reversing valve is not used, but is used
Ratio solenoid directional control valve controls clutch.Manufacturing cost is decreased while simplifying hydraulic system arrangement.
Description of the drawings
Fig. 1 is the principle schematic of full power shift commutation gear box of tractor hydraulic control system
Fig. 2 is the structural schematic diagram of full power shift commutation gear box of tractor hydraulic control system
Fig. 3 is the structural schematic diagram of cooling and lubricating subsystem I
Fig. 4 is the structural schematic diagram of oil supply subsystem II
Fig. 5 is the structural schematic diagram of clutch control subsystem III
Wherein：By I III, clutch control subsystems of cooling and lubricatings II, oil supply subsystems of subsystem, 1. cooler 2.
I 3. forced feed lubrication oilhole group of port valve, 4. 6. level-one overflow valve of spray lubrication oilhole 5. two level overflow valve of group, 7. hydraulic control bypasses
13. fine filter of valve 8. filter, 9. duplex gear pump, 10. by-passing valve, II 11. coarse filter, 12. fuel tank, 14. pilot-operated type overflows
Flow 15. strainer of valve, I group of 16. 17. strainer of ratio electromagnetic switch valve group, II group of 18. 19. pressure sensor of wet clutch group
20. accumulators of group
Specific implementation mode
As depicted in figs. 1 and 2, the present invention is by cooling and lubricating subsystem I, oil supply subsystem II and clutch control subsystem
III composition, it is cooling wherein in the huge discharge oil discharge outlet i Yu cooling and lubricating subsystem I of the duplex gear pump 9 in oil supply subsystem II
The oil inlet of device 1 is connected to；The huge discharge oil discharge outlet i of duplex gear pump 9 in oil supply subsystem II also with cooling and lubricating subsystem I
The control guide end of middle hydraulic control by-passing valve 7 is connected to.The small displacement oil discharge outlet j of duplex gear pump 9 in oil supply subsystem II with from
The oil inlet connection of pilot operated compound relief valve 14 in clutch control subsystem III.Two level overflow valve 5 in cooling and lubricating subsystem I
Overflow hydraulic fluid port is connected to the oil return opening of the fuel tank 12 in oil supply subsystem II.Pilot operated compound relief valve in clutch control subsystem III
14 overflow hydraulic fluid port is connected to the branch where the oil inlet of the cooler 1 in cooling and lubricating subsystem I.
As shown in figure 3, the cooling and lubricating subsystem I is by cooler 1, by-passing valve I 2, forced feed lubrication oilhole group 3, spray
It drenches oilhole group 4, two level overflow valve 5, level-one overflow valve 6, hydraulic control by-passing valve 7 and filter 8 to form, cooling and lubricating subsystem
I can realize each transmission parts sufficient lubrication in dynamic power shift gear box, and keep the parts in gearbox rational at one
Work in temperature range.Wherein forced feed lubrication oilhole group 3 is made of 22 forced feed lubrication oilholes；Spray lubrication oilhole group 4 is by 5
Spray lubrication oilhole forms.The oil inlet of by-passing valve I 2 is connected to the branch where the oil inlet of filter 8, and by-passing valve I 2 goes out
Hydraulic fluid port is connected to the branch where the oil outlet of filter 8.22 forced feed lubrication oilholes of forced feed lubrication oilhole group 3 are located at
In full power shift commutation gear box of tractor on each axis, and, forced feed lubrication oil corresponding with bearing to be lubricated on axis, clutch
Branch between road and the oil outlet of filter 8 and the oil inlet of level-one overflow valve 6 is connected to.5 sprays of spray lubrication oilhole group 4
Leaching oilhole be located at full power shift commutate gear box of tractor top spray tube on, and with the flank of tooth pair that waits for spray lubrication
It answers, the branch between spray lubrication oil circuit and the oil inlet of two level overflow valve 5 and the overflow hydraulic fluid port of level-one overflow valve 6 is connected to.Liquid
Branch where controlling the oil inlet of by-passing valve 7 and the oil inlet of cooler 1 is connected to, oil outlet and the filter 8 of hydraulic control by-passing valve 7
Branch connection where oil outlet, the hydraulic control guide end first quarter discharge orifice of hydraulic control by-passing valve 7 and branch where the oil inlet of cooler 1
Connection.The oil inlet of level-one overflow valve 6 is connected to the oil outlet of filter 8, oil outlet and the two level overflow valve of level-one overflow valve 6
5 oil inlet connection.
As shown in figure 4, the oil supply subsystem II is by duplex gear pump 9, by-passing valve II 10, coarse filter 11, fuel tank 12
It is formed with fine filter 13, oil supply subsystem II provides power for entire gear box hydraulic system, and fluid is through cooling and lubricating
After system I and clutch control subsystem III work, fuel tank is back flowed back into, recycling for fluid is completed.Fuel feeding subsystem
The oil inlet of by-passing valve II 10 is connected to the oil outlet of coarse filter 11 in system II, oil outlet and the fine filter 13 of by-passing valve II 10
Oil outlet is connected to；The oil inlet of coarse filter 11 is connected to the oil inlet of fine filter 13.The oil discharge outlet of 12 bottom of fuel tank is through fine filter
13 are connected to the inlet port of duplex gear pump 9.
As shown in figure 5, the clutch control subsystem III is by pilot operated compound relief valve 14, I group 15 of strainer, ratio electromagnetism
Commutate valve group 16, II group 17 of strainer, wet clutch group 18, pressure sensor group 19 and the composition of accumulator 20, passes through electric ratio
The control of example reversal valve, can complete the gear shift operation of driver's instruction.Wherein ratio electromagnetic switch valve group 16 is by 10 ratios
Solenoid directional control valve forms, and I group 15 of strainer and strainer are made of for II group 17 10 strainers, and wet clutch group 18 is by 10 wet types
Clutch forms, and pressure sensor group 19 is made of 10 pressure sensors.Accumulator 20 is installed on pilot operated compound relief valve 14
Branch road between I group 15 of oil inlet and strainer.To be connected in parallel between the control loop of 10 wet clutches, each wet type
The control loop of clutch is made of a ratio solenoid directional control valve, a pressure sensor of strainer II, one of strainer I, one,
The connection relation of its each element is as follows：Oil inlet of the input terminal of ratio solenoid directional control valve through strainer I Yu pilot operated compound relief valve 14
Place branch connection.Branch where pressure oilhole of the output end of ratio solenoid directional control valve through strainer II and wet clutch connects
It is logical.Pressure sensor is installed on the road of the branch between strainer II and the pressure oilhole of wet clutch.
Claims (4)
1. a kind of full power shift commutation gear box of tractor hydraulic control system, it is characterised in that：By cooling and lubricating subsystem
(I), oil supply subsystem (II) and clutch control subsystem (III) composition, the wherein duplex gear pump in oil supply subsystem (II)
(9) huge discharge oil discharge outlet (i) is connected to the oil inlet of cooler (1) in cooling and lubricating subsystem (I)；Oil supply subsystem (II)
In duplex gear pump (9) control of the huge discharge oil discharge outlet (i) also with hydraulic control by-passing valve (7) in cooling and lubricating subsystem (I)
Guide end is connected to；The small displacement oil discharge outlet (j) and clutch control subsystem of duplex gear pump (9) in oil supply subsystem (II)
(III) the oil inlet connection of pilot operated compound relief valve (14) in；The oil overflow of two level overflow valve (5) in cooling and lubricating subsystem (I)
Mouth is connected to the oil return opening of the fuel tank (12) in oil supply subsystem (II)；Pilot operated compound relief valve in clutch control subsystem (III)
(14) overflow hydraulic fluid port is connected to the branch where the oil inlet of the cooler (1) in cooling and lubricating subsystem (I).
2. full power shift commutation gear box of tractor hydraulic control system as described in claim 1, it is characterised in that：It is described
Cooling and lubricating subsystem (I) by cooler (1), by-passing valve I (2), forced feed lubrication oilhole group (3), spray lubrication oilhole group
(4), two level overflow valve (5), level-one overflow valve (6), hydraulic control by-passing valve (7) and filter (8) composition, wherein forced feed lubrication oilhole
Group (3) is made of 22 forced feed lubrication oilholes；Spray lubrication oilhole group (4) is made of 5 spray lubrication oilholes；By-passing valve I (2)
Oil inlet be connected to the branch where the oil inlet of filter (8), the oil outlet of by-passing valve I (2) is fuel-displaced with filter (8)
Branch connection where mouthful；22 forced feed lubrication oilholes of forced feed lubrication oilhole group (3) are located at full power shift commutation and drag
In machine drawing gearbox on each axis, and, forced feed lubrication oil circuit and filter (8) corresponding with bearing to be lubricated on axis, clutch
Branch connection between oil outlet and the oil inlet of level-one overflow valve (6)；5 spray lubrication oil of spray lubrication oilhole group (4)
Hole is located on the spray tube on full power shift commutation gear box of tractor top, and, spray corresponding with the flank of tooth of spray lubrication is waited for
Branch between lubricant passage way and the oil inlet of two level overflow valve (5) and the overflow hydraulic fluid port of level-one overflow valve (6) is connected to；By hydraulic control
The oil inlet of port valve (7) is connected to branch where the oil inlet of cooler (1), the oil outlet and filter of hydraulic control by-passing valve (7)
(8) branch connection, the oil inlet of the hydraulic control guide end first quarter discharge orifice and cooler (1) of hydraulic control by-passing valve (7) where oil outlet
Branch connection where mouthful；The oil inlet of level-one overflow valve (6) is connected to the oil outlet of filter (8), and level-one overflow valve (6) go out
Hydraulic fluid port is connected to the oil inlet of two level overflow valve (5).
3. full power shift commutation gear box of tractor hydraulic control system as described in claim 1, it is characterised in that：It is described
Oil supply subsystem (II) by duplex gear pump (9), by-passing valve II (10), coarse filter (11), fuel tank (12) and fine filter (13)
Composition, wherein the oil inlet of by-passing valve II (10) is connected to the oil outlet of coarse filter (11), the oil outlet of by-passing valve II (10) and
The oil outlet of fine filter (13) is connected to；The oil inlet of coarse filter (11) is connected to the oil inlet of fine filter (13)；Fuel tank (12) bottom
The oil discharge outlet in portion is connected to through fine filter (13) with the inlet port of duplex gear pump (9).
4. full power shift commutation gear box of tractor hydraulic control system as described in claim 1, it is characterised in that：It is described
Clutch control subsystem (III) by pilot operated compound relief valve (14), strainer I group (15), ratio electromagnetic switch valve group (16), filter
Net II group (17), wet clutch group (18), pressure sensor group (19) and accumulator (20) composition, wherein ratio electromagnetic switch
Valve group (16) is made of 10 ratio solenoid directional control valves, and strainer I group (15) and II group of strainer (17) are made of 10 strainers, wet
Formula clutch group (18) is made of 10 wet clutches, and pressure sensor group (19) is made of 10 pressure sensors；Accumulation of energy
Device (20) is installed on the road of the branch between the oil inlet of pilot operated compound relief valve (14) and I group of strainer (15)；10 wet clutches
Control loop between to be connected in parallel, the control loop of each wet clutch is by a ratio solenoid directional control valve, a filter
I, one, the net pressure sensor of strainer II, one forms, and the connection relation of each element is as follows：The input of ratio solenoid directional control valve
End is connected to through strainer I with branch where the oil inlet of pilot operated compound relief valve (14)；The output end of ratio solenoid directional control valve is through strainer
II is connected to branch where the pressure oilhole of wet clutch；Pressure sensor is installed on the pressure of strainer II and wet clutch
Branch road between oilhole.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810674796.7A CN108571584B (en) | 2018-06-27 | 2018-06-27 | Hydraulic control system for gearbox of full-power gear shifting reversing tractor |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810674796.7A CN108571584B (en) | 2018-06-27 | 2018-06-27 | Hydraulic control system for gearbox of full-power gear shifting reversing tractor |
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| CN108571584A true CN108571584A (en) | 2018-09-25 |
| CN108571584B CN108571584B (en) | 2024-01-23 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201810674796.7A Active CN108571584B (en) | 2018-06-27 | 2018-06-27 | Hydraulic control system for gearbox of full-power gear shifting reversing tractor |
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| CN110319181A (en) * | 2019-06-20 | 2019-10-11 | 无锡明恒混合动力技术有限公司 | A kind of hydraulic gear-shifting and cooling and lubricating system for hybrid power gearbox |
| CN111075919A (en) * | 2019-09-12 | 2020-04-28 | 肇庆宏旺金属实业有限公司 | A lubricated spraying system for decoiler |
| 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 |
| CN114658843A (en) * | 2022-03-16 | 2022-06-24 | 陕西法士特齿轮有限责任公司 | Hydraulic control system of hybrid automatic transmission |
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| CN110319181A (en) * | 2019-06-20 | 2019-10-11 | 无锡明恒混合动力技术有限公司 | A kind of hydraulic gear-shifting and cooling and lubricating system for hybrid power gearbox |
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| CN111075919A (en) * | 2019-09-12 | 2020-04-28 | 肇庆宏旺金属实业有限公司 | A lubricated spraying system for decoiler |
| 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 |
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| CN114658843A (en) * | 2022-03-16 | 2022-06-24 | 陕西法士特齿轮有限责任公司 | Hydraulic control system of hybrid automatic transmission |
| CN114658843B (en) * | 2022-03-16 | 2023-11-07 | 陕西法士特齿轮有限责任公司 | Hydraulic control system of hybrid automatic transmission |
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| CN108571584B (en) | 2024-01-23 |
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