CN208348465U - 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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- CN208348465U CN208348465U CN201820996183.0U CN201820996183U CN208348465U CN 208348465 U CN208348465 U CN 208348465U CN 201820996183 U CN201820996183 U CN 201820996183U CN 208348465 U CN208348465 U CN 208348465U
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- 230000001050 lubricating effect Effects 0.000 claims abstract description 48
- 238000001816 cooling Methods 0.000 claims abstract description 44
- 150000001875 compounds Chemical class 0.000 claims abstract description 19
- 239000002828 fuel tank Substances 0.000 claims abstract description 17
- 239000012530 fluid Substances 0.000 claims abstract description 11
- 238000006073 displacement reaction Methods 0.000 claims abstract description 4
- 238000005461 lubrication Methods 0.000 claims description 66
- 239000007921 spray Substances 0.000 claims description 31
- 239000000203 mixture Substances 0.000 claims description 9
- 239000000314 lubricant Substances 0.000 claims description 4
- 238000009825 accumulation Methods 0.000 claims 1
- 238000001914 filtration Methods 0.000 abstract description 6
- 230000000903 blocking effect Effects 0.000 abstract description 2
- 230000015556 catabolic process Effects 0.000 abstract 1
- 230000009885 systemic effect Effects 0.000 abstract 1
- 239000003921 oil Substances 0.000 description 135
- 239000007788 liquid Substances 0.000 description 38
- 230000000694 effects Effects 0.000 description 9
- 238000010586 diagram Methods 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 238000004519 manufacturing process Methods 0.000 description 3
- 238000005336 cracking Methods 0.000 description 2
- 238000005516 engineering process Methods 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
- 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
- 239000003344 environmental pollutant Substances 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 238000002386 leaching Methods 0.000 description 1
- 239000010687 lubricating oil Substances 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
- 238000000926 separation method Methods 0.000 description 1
- 230000009897 systematic effect Effects 0.000 description 1
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Abstract
A kind of full power shift commutation gear box of tractor hydraulic control system category agricultural machinery technological field.The control guide end of hydraulic control by-passing valve is connected in the oil inlet and cooling and lubricating subsystem of cooler in the huge discharge oil discharge outlet and cooling and lubricating subsystem of duplex gear pump in the utility model oil supply subsystem；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 second 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 utility model, 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 utility model, can avoid the problem of leading to systemic breakdown because of cooling and filtering branch blocking generation.
Description
Technical field
The utility model belongs to agricultural machinery technological field, and in particular to a kind of full power shift commutation gear box of tractor
Hydraulic control system.
Background technique
The farm tractor in China generallys use traditional engaging sleeve or synchronizer to shift gears at present, and this tradition
Shift mode have the disadvantages that 1. farm tractors often gear number be more, 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, thus shifting gears
Big energy is lost in journey.
Power shifting technology has compared with traditional shift technology as research and development direction new in field of agricultural machinery
Following advantages: 1. driver's gear shift operations are simple, mitigate the working strength of driver.2. effectively reducing in gearbox between part
Abrasion condition.3. may be implemented uninterruptedly to shift gears and switching operation, caused by reducing in shift process because of 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, becomes more complicated hydraulic system, improves production cost, also results in hydraulic
System loss more energy.
In terms of clutch control circuit, in the hydraulic system of current tractor dynamic power shift gear box, often exist
Due to oil cleanliness it is inadequate caused by shift control valve core core clamping stagnation obstruction the problem of.Additionally, due in clutch
During separation and combination, hydraulic shock and shift shake can be led to the problem of, work has adverse effect on to shifting gears.
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 for lubrication of splashing 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 oil liquid, and can guarantee certain
Lubrication pressure, lubricant effect is preferable.But lubricating loop systematic comparison needed for forced feed lubrication is complicated, can increase design difficulty,
Increase manufacturing cost.
Summary of the invention
The purpose of this utility model is to provide a kind of Hydraulic Elements are few, full power shift commutation tractor simple for structure
Gear box hydraulic control system.
The utility model is made of cooling and lubricating subsystem I, oil supply subsystem II and clutch control subsystem III, wherein
The oil inlet of cooler 1 in the huge discharge oil discharge outlet i and cooling and lubricating subsystem I of duplex gear pump 9 in oil supply subsystem II
Connection.The huge discharge oil discharge outlet i of duplex gear pump 9 in oil supply subsystem II is also bypassed with hydraulic control in cooling and lubricating subsystem I
The control guide end of valve 7 is connected to.Small displacement oil discharge outlet j and clutch control of duplex gear pump 9 in oil supply subsystem II
The oil inlet connection of pilot operated compound relief valve 14 in system III.The overflow hydraulic fluid port of second level overflow valve 5 in cooling and lubricating subsystem I with
The oil return opening of fuel tank 12 in oil supply subsystem II is connected to.The oil overflow of pilot operated compound relief valve 14 in clutch control subsystem III
Mouth is connected to the branch where the oil inlet of the cooler 1 in cooling and lubricating 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, second 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 second level overflow valve 5 corresponding with the flank of tooth to spray lubrication
Branch connection between mouth and the overflow hydraulic fluid port of level-one overflow valve 6.The oil inlet of hydraulic control by-passing valve 7 and the oil inlet of cooler 1
The connection of place branch, 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 end first quarter discharge orifice is connected to branch where the oil inlet of cooler 1.The oil inlet and filter 8 of level-one overflow valve 6
Oil outlet connection, the oil outlet of level-one overflow valve 6 is connected to the oil inlet of second 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 II group 17 of strainer are made of 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 the oil inlet of conduction overflow valve 14 and I group 15 of 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 composition, the connection relationship of each element are 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 principles of the present invention and the course of work are as follows:
In the utility model enter cooling and lubricating subsystem I oil liquid, first along lubrication main road f enter cooler (1) into
Row cooling, effect are that the oil liquid temperature of control hydraulic system is in normal working range, guarantee that work system is reliable.
During the cooling and lubricating of gearbox, if containing impurity and other pollutants, meeting to the oil liquid that components supply
Working condition and service life to components can all have a great impact, therefore will flow to through cooler oil liquid after cooling
Filter 8 is for re-filtering, which ensure that the cleaning of cooling and lubricating oil liquid is reliable.
In the in parallel by-passing valve 2 in the two 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 filter 8 and the concatenated oil circuit of cooler 1
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, increased by the oil pressure that throttle orifice enters by-passing valve, guide end control valve core is mobile, makes the branch
Road connection, guarantees that gearbox has enough cutting oils.
Oil liquid 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 carry out pressure maintaining for entire cooling and lubricating subsystem.
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 oil liquid that 6 overflow of level-one overflow valve goes out flows to second level overflow valve
5 and spray lubrication oilhole 4, the second level overflow valve 5 is responsible for the oil liquid pressure at control spray lubrication oilhole 4, when second level overflow
When 5 overflow of valve, overflow oil liquid flows into fuel tank again.Since forced feed lubrication is compared with spray lubrication, the oil liquid pressure of the former needs
It is bigger, so the cracking pressure of the level-one overflow valve 6 is greater than the cracking pressure of second level overflow valve 5, to guarantee two kinds of lubrications
The oil pressure of mode is different, and then reaches expected lubricant effect.
Since the gearbox gear number of the utility model is more, according to the design arrangement of mechanical driving part, need to pass through
Clutch control subsystem III controls wet clutch group 18 respectively, to complete gear shift operation.
The oil liquid 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. reveal for control loop compensation and keep constant pressure；2. can
It eliminates pulsation and absorbs hydraulic shock, provide guarantee for the ride comfort of shift process.
Clutch control subsystem III is used as directional control valve using ratio electromagnetic switch valve group 16, and the ratio electromagnetism changes
It is two-position three way to valve, which can control the automatically controlled end of electromagnetic actuation equipped with a spring terminal and one.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 closure, output end with
Oil return line connection, 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 oil liquid 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 is compared with other kinds of reversal valve, the advantage is that: it is defeated to can use proportion electro-magnet
Electromagnetic force out so that oil liquid pressure and flow are 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 in proportion to mechanical quantity output.It therefore can using ratio solenoid directional control valve
To improve the ride comfort of shift and the shift control performance of gearbox.
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 II group 17 of strainer.The purpose of design that I group 15 of strainer is to carry out the oil liquid that will enter ratio electromagnetic switch valve group 16 one
Secondary filtering avoids the situation of its spool jams from occurring；The effect that design installs II group 17 of strainer is: when wet clutch separates
When, when oil liquid oil return inside plunger shaft, can enter back into ratio electromagnetic switch valve group 16 through II group 17 of filter screen, ensure that
Reversal valve clamping stagnation situation will not occur due to oil liquid takes back the impurity in wet clutch during oil return.
Pressure sensor group 19 is installed on I group 15 of the strainer oil circuit between wet clutch group 18, 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 guarantees, while providing related data for the self-learning function of gearbox and supporting, can also be with
Making the control of entire clutch control subsystem III becomes more accurate.
In order to guarantee 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 oil liquid enters overflow valve and acts directly on main valve
On, when the oil liquid pressure in d branch is higher than the pressure value that guide's valve spring is set up, the spool in pilot valve is opened, wherein
Oil liquid 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 oil liquid 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, to need the biggish cooling and lubricating subsystem of flow to make flow supplement.
The flow required for cooling and lubricating subsystem I and clutch control subsystem III work normally and pressure are 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 as dynamical element.Oil liquid respectively enters branch after the discharge of two oil discharge outlets of the duplex gear pump 9
Oil liquid in b and branch c, branch b flows to cooling and lubricating subsystem I；Oil liquid 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, oil liquid 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 oil liquid.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 oil liquid that can not circulate, by-passing valve 10 is opened, and oil liquid can enter system after the filtering of coarse filter 11, is avoided
The failure conditions of filter.
The lubrication and control fuel tank of gearbox, the fuel tank in the oil supply subsystem II is not separately provided in the utility model
12 be full power shift commutation gear box of tractor cabinet.
The utility model has the beneficial effects that:
The utility model uses dynamical element of the duplex gear pump as two hydraulic circuits, and portion will be lubricated by avoiding
It is divided to and control section is designed to that hydraulic system complexity caused by two autonomous systems, the excessive problem of amount of parts occur.
And each section circuit is compact to design, the Hydraulic Elements division of labor is distinct, saves certain space while simplifying system.
The utility model combines in terms of the lubrication of dynamic power shift gear box using by forced feed lubrication and spray lubrication
Lubricating system, can be needed according to the lubrication of different components using suitable lubricating system, and avoid to a certain extent
Using system complex caused by the single lubricating system of tradition, it is ineffective the problems such as.
A hydraulic control by-passing valve is equipped in the cooling and lubricating subsystem of the utility model, the effect of the hydraulic control by-passing valve is:
When cooler and filter device branch block, branch oil liquid pressure increases, while controlling hydraulic control bypass valve core shifting
It moves that the oil liquid in cooling and lubricating subsystem is made to continue to circulate, plays the protective effect to the subsystem.
Because cooling and lubricating subsystem is compared with clutch control subsystem, flow required for the former is bigger, so at this
A pilot operated compound relief valve is equipped in the clutch control subsystem of utility model, which not only can control this
The oil pressure pressure of subsystem, while oil overflow liquid stream can be made into flow supplement into cooling and lubricating subsystem in overflow.
In the clutch control subsystem of the utility model, traditional hydraulically-controlled type proportional reversing valve is not used, but
Clutch is controlled using ratio solenoid directional control valve.Simplify hydraulic system arrangement while decrease the manufacturing at
This.
Detailed description of the invention
Fig. 1 is the schematic illustration 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: I 1. cooler of cooling and lubricating subsystem II, oil supply subsystem, III, clutch control subsystem, 2. by-passing valve
I 3. forced feed lubrication oilhole group, 4. 7. hydraulic control by-passing valve of spray lubrication oilhole group 5. second level overflow valve, 6. level-one overflow valve, 8. filter
9. I group 16. of 15. strainer of 12. fuel tank, 13. fine filter, 14. pilot operated compound relief valve of duplex gear pump 10. by-passing valve, II 11. coarse filter
17. strainer of ratio electromagnetic switch valve group, II group of 18. 19. pressure sensor group of wet clutch group, 20. accumulator
Specific embodiment
As depicted in figs. 1 and 2, the utility model is by cooling and lubricating subsystem I, oil supply subsystem II and clutch control
System III forms, 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 cooler 1 is connected to；The huge discharge oil discharge outlet i of duplex gear pump 9 in oil supply subsystem II is also sub with cooling and lubricating
The control guide end connection of hydraulic control by-passing valve 7 in system I.The small displacement oil discharge outlet j of duplex gear pump 9 in oil supply subsystem II
It is connected to the oil inlet of pilot operated compound relief valve 14 in clutch control subsystem III.Second level overflow in cooling and lubricating subsystem I
The overflow hydraulic fluid port of valve 5 is connected to the oil return opening of the fuel tank 12 in oil supply subsystem II.Pilot-operated type in clutch control subsystem III
The overflow hydraulic fluid port of overflow valve 14 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, second 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 is able to achieve each transmission parts sufficient lubrication in dynamic power shift gear box, and keeps the components in gearbox reasonable 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 composition.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 to spray lubrication
It answers, the branch between spray lubrication oil circuit and the oil inlet of second 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 where branch connection where oil outlet, the hydraulic control guide end first quarter discharge orifice of hydraulic control by-passing valve 7 and 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, the oil outlet and second 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 oil liquid is through cooling and lubricating
After system I and clutch control subsystem III work, fuel tank is back flowed back into, recycling for oil liquid 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 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 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 composition, I group 15 of strainer and II group 17 of strainer are made of 10 strainers, and wet clutch group 18 is by 10 wet types
Clutch composition, pressure sensor group 19 are made of 10 pressure sensors.Accumulator 20 is installed on pilot operated compound relief valve 14
Branch road between oil inlet and I group 15 of 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 relationship 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
The connection of place branch.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) form, wherein the 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)
The connection of guide end；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 second 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 according to claim 1, it is characterised in that: 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), second level overflow valve (5), level-one overflow valve (6), hydraulic control by-passing valve (7) and filter (8) form, 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 to spray lubrication
Branch between lubricant passage way and the oil inlet of second 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 where oil outlet, the hydraulic control guide end first quarter discharge orifice of hydraulic control by-passing valve (7) and the oil inlet of cooler (1)
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) goes out
Hydraulic fluid port is connected to the oil inlet of second level overflow valve (5).
3. full power shift commutation gear box of tractor hydraulic control system according to claim 1, it is characterised in that: 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 according to claim 1, it is characterised in that: described
Clutch control subsystem (III) by pilot operated compound relief valve (14), I group of strainer (15), ratio electromagnetic switch valve group (16), filter
II group of net (17), wet clutch group (18), pressure sensor group (19) and accumulator (20) form, wherein ratio electromagnetic switch
Valve group (16) is made of 10 ratio solenoid directional control valves, and I group of strainer (15) and II group of strainer (17) is 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 composition, the connection relationship of each element are 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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| CN201820996183.0U CN208348465U (en) | 2018-06-27 | 2018-06-27 | A kind of full power shift commutation gear box of tractor hydraulic control system |
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| CN201820996183.0U CN208348465U (en) | 2018-06-27 | 2018-06-27 | A kind of full power shift commutation gear box of tractor hydraulic control system |
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| CN208348465U true CN208348465U (en) | 2019-01-08 |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108571584A (en) * | 2018-06-27 | 2018-09-25 | 吉林大学 | A kind of full power shift commutation gear box of tractor hydraulic control system |
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2018
- 2018-06-27 CN CN201820996183.0U patent/CN208348465U/en not_active Withdrawn - After Issue
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108571584A (en) * | 2018-06-27 | 2018-09-25 | 吉林大学 | A kind of full power shift commutation gear box of tractor hydraulic control system |
| CN108571584B (en) * | 2018-06-27 | 2024-01-23 | 吉林大学 | Hydraulic control system for gearbox of full-power gear shifting reversing tractor |
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| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned | ||
| AV01 | Patent right actively abandoned | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20190108 Effective date of abandoning: 20240123 |
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| AV01 | Patent right actively abandoned |
Granted publication date: 20190108 Effective date of abandoning: 20240123 |