CN107061671A - A kind of buncher hydraulic system - Google Patents
A kind of buncher hydraulic system Download PDFInfo
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- CN107061671A CN107061671A CN201710197812.3A CN201710197812A CN107061671A CN 107061671 A CN107061671 A CN 107061671A CN 201710197812 A CN201710197812 A CN 201710197812A CN 107061671 A CN107061671 A CN 107061671A
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- belt wheel
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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
- F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
- F16H47/02—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type
Abstract
Buncher hydraulic system provided in an embodiment of the present invention, including：Oil pump electrical machinery, double-acting pump, high-pressure oil passage and low pressure oil way.By the way that hydraulic circuit is divided into high-pressure oil passage and low pressure oil way so that the Hydraulic Elements on Hydraulic Elements and low pressure oil way on high-pressure oil passage are independent, it is to avoid the coupling between high voltage demands Hydraulic Elements and low pressure requirements Hydraulic Elements, simplify hydraulic circuit；Simultaneously because the traffic demand of low pressure requirements Hydraulic Elements needs not move through high-pressure oil passage, the power attenuation of hydraulic system can be reduced.And pressure-control valve is set on high-pressure oil passage and low pressure oil way respectively so that the pressure of low pressure requirements Hydraulic Elements need not be reduced and obtained by high pressure, reduce the energy loss of hydraulic system itself.
Description
Technical field
The present invention relates to automotive transmission technology, more particularly, to a kind of buncher hydraulic system.
Background technology
Buncher (Continuously Variable Transmission, CVT), mainly by clutch 2, metal
Band 3 and active and passive band wheel assembly 4 are constituted, shown in such as Fig. 1 traditional CVT structural representations (containing fluid torque-converter 1).In transmission
During, by movement of the active and passive belt wheel of pitch radius consecutive variations in cone dish axle, make metal tape 3 along active and passive band
The V-groove that wheel is constituted is radially slided, and realizes the consecutive variations of gearratio.Due to its can be automatic continuous change gearratio,
Therefore engine can be made to be run in the case of optimal fuel-economy curve or best power source linearity curve, and in the case of speed change
Power can be continuously provided, the comfortableness that the dynamic property of automobile, the economy of fuel oil and driver take greatly is improved.
Existing traditional buncher hydraulic system mainly includes：Hydraulic pump, hydraulic valve, solenoid valve block, main belt
Wheel, passive belt wheel, clutch and fluid torque-converter etc..Hydraulic transmission principle：Hydraulic pump is inhaled by engine driving from oil sump
Oil, and hydraulic valve is pumped into, driving pulley, quilt are controlled pressure to by solenoid valve block and pressure-control valve inside valve body etc.
The pressure of movable belt pulley, clutch and fluid torque-converter demand.Wherein driving pulley and passive belt wheel demand pressure ratio solenoid valve block,
Clutch and fluid torque-converter pressure are high, and the greatest requirements pressure of driving pulley and passive belt wheel is general in 4-6Mpa, electromagnetism
The pressure of valve group, clutch and fluid torque-converter is less than 1Mpa.Therefore, typically the pressure of driving pulley and passive belt wheel is set
It is higher, then by pressure-reducing valve by elevated pressures reduce to solenoid valve block, clutch and fluid torque-converter demand relatively low pressure
Power.
Because in traditional CVT hydraulic systems, hydraulic pump is by engine driving, and hydraulic pump is pumped into the flow of hydraulic system
Raised with the rise of engine speed, very big spill losses particularly can be caused in cruising condition；Simultaneously as clutch
The pressure demand of device and fluid torque-converter etc. is obtained by reducing the pressure of active and passive belt wheel, in high temperature and fast ratio drastically
In change procedure, the bonding state of clutch and fluid torque-converter can be had a strong impact on, the phenomenon hair of " out of supply " is seriously had
It is raw.And all flows come out from hydraulic pump must first pass through high-pressure oil passage, then be down to demand pressure through different vacuum valve, from
Power is equal to the angle that pressure is multiplied by flow, and power loss is inevitable very serious.Therefore, in CVT power losses so that hydraulic pressure system
The power loss of system accounts for 60%, and the power loss of metal tape frictional drive accounts for 30% or so, so, the work(that hydraulic system is produced
Rate loss is the major obstacle for influenceing CVT to lift vehicle fuel economy.
The content of the invention
The embodiment of the present invention provides a kind of buncher liquid for solving the above problems or partly solving the above problems
Pressure system.
First aspect according to embodiments of the present invention there is provided a kind of buncher hydraulic system, including：Oil pump electrical machinery,
Double-acting pump, high-pressure oil passage and low pressure oil way.The Oil pump electrical machinery is connected with the double-acting pump, for driving the double acting
Pump；The double-acting pump includes two inlet ports and two oil-outs；Described two inlet ports are communicated with oil sump, and first goes out
Hydraulic fluid port is communicated with the high-pressure oil passage, and the second oil-out is communicated with the low pressure oil way；The high-pressure oil passage includes first pressure
Control valve, the first pressure control valve respectively with the driving pulley assembly on second oil-out, the high-pressure oil passage and
Passive belt wheel assembly is connected, the oil pressure for controlling the high-pressure oil passage；The low pressure oil way includes second pressure control valve, institute
State second pressure control valve respectively with the coupled clutch on second oil-out and the low pressure oil way to be connected, for controlling
The oil pressure of the low pressure oil way.
Wherein, the Oil pump electrical machinery is additionally operable to actively adjust turning for Oil pump electrical machinery according to hydraulic system real-time traffic demand
Speed.
Wherein, the low pressure oil way also includes the first pilot solenoid valve being connected with the first pressure control valve, is used for
Control the outlet oil pressure of the first pressure control valve.
Wherein, the high-pressure oil passage also includes driving pulley pressure-control valve and passive belt wheel pressure-control valve；The master
Movable belt pulley pressure-control valve is connected with the main belt wheel cylinder in the driving pulley assembly, the oil for controlling main belt wheel cylinder
Pressure；The passive belt wheel pressure-control valve is connected with the passive belt wheel cylinder in the passive belt wheel assembly, for controlling passive belt
The oil pressure of wheel cylinder.
Wherein, the low pressure oil way also includes the second pilot solenoid valve and the 3rd pilot solenoid valve；Described second is first conductive
Magnet valve is connected with the driving pulley pressure-control valve, the outlet oil pressure for controlling the driving pulley pressure-control valve；Institute
State the 3rd pilot solenoid valve with the passive belt wheel pressure-control valve to be connected, for controlling the passive belt wheel pressure-control valve
Outlet oil pressure.
Wherein, the low pressure oil way also includes the coupled clutch pressure-control valve being connected with the coupled clutch, uses
In the oil pressure for controlling the coupled clutch.
Wherein, the low pressure oil way also includes the 4th first conductive magnetism being connected with the coupled clutch pressure-control valve
Valve, the outlet oil pressure for controlling the coupled clutch pressure-control valve.
Wherein, the low pressure oil way also includes the 3rd pressure-control valve, respectively with first pilot solenoid valve, described the
Two pilot solenoid valves, the 3rd pilot solenoid valve are connected with the 4th pilot solenoid valve, for controlling first guide
Magnetic valve, second pilot solenoid valve, the import oil pressure of the 3rd pilot solenoid valve and the 4th pilot solenoid valve.
Wherein, the coupled clutch is wet clutch, and one end of the wet clutch is connected with engine, another
End is connected with the input shaft of the buncher.
Wherein, the first pressure control valve is pilot operated compound relief valve, and the second pressure control valve is definite value overflow valve,
3rd pressure-control valve is fixed pressure reducing valve.
Buncher hydraulic system provided in an embodiment of the present invention, by the way that hydraulic circuit is divided into high-pressure oil passage and low pressure
Oil circuit so that the Hydraulic Elements on Hydraulic Elements and low pressure oil way on high-pressure oil passage are independent, it is to avoid high voltage demands liquid
The coupling between element and low pressure requirements Hydraulic Elements is pressed, simplifies hydraulic circuit；Simultaneously because low pressure requirements Hydraulic Elements
Traffic demand need not move through high-pressure oil passage, the power attenuation of hydraulic system can be reduced.And respectively in high-pressure oil passage and low
Force feed sets pressure-control valve on road so that the pressure of low pressure requirements Hydraulic Elements need not be reduced and obtained by high pressure, be subtracted
The energy loss of primary hydraulic system itself.
Brief description of the drawings
In order to illustrate more clearly about the embodiment of the present invention or technical scheme of the prior art, below will be to embodiment or existing
There is the accompanying drawing used required in technology description to be briefly described, it should be apparent that, drawings in the following description are this hairs
Some bright embodiments, for those of ordinary skill in the art, on the premise of not paying creative work, can be with root
Other accompanying drawings are obtained according to these accompanying drawings.
Fig. 1 is tradition CVT structural representations (containing fluid torque-converter)；
Fig. 2 is buncher hydraulic system structure schematic diagram provided in an embodiment of the present invention；
The buncher hydraulic system structure schematic diagram that Fig. 3 provides for another embodiment of the present invention；
Wherein, 1 is Oil pump electrical machinery；2 be double-acting pump；2a is the first oil-out；2b is the second oil-out；3 for coupling from
Clutch；4 be second pressure control valve；5 be first pressure control valve；6 be driving pulley assembly；7 be passive belt wheel assembly；8 are
High-pressure oil passage；9 be low pressure oil way；10 be oil sump；11 be the first pilot solenoid valve；12 be driving pulley pressure-control valve；13
For passive belt wheel pressure-control valve；14 be the second pilot solenoid valve；15 be the 3rd pilot solenoid valve；16 be coupled clutch pressure
Control valve；17 be the 4th pilot solenoid valve；18 be the 3rd pressure-control valve.
Embodiment
To make the purpose, technical scheme and advantage of the embodiment of the present invention clearer, below in conjunction with the embodiment of the present invention
In accompanying drawing, the technical scheme in the embodiment of the present invention is explicitly described, it is clear that described embodiment be the present invention
A part of embodiment, rather than whole embodiments.Based on the embodiment in the present invention, those of ordinary skill in the art are not having
The every other embodiment obtained under the premise of creative work is made, the scope of protection of the invention is belonged to.
Fig. 2 is according to buncher hydraulic system structure schematic diagram provided in an embodiment of the present invention, as shown in Fig. 2 should
Hydraulic system includes Oil pump electrical machinery 1, double-acting pump 2, high-pressure oil passage 8 and low pressure oil way 9.
High-pressure oil passage and low pressure oil way in the embodiment of the present invention are a relative concepts, and wherein high-pressure oil passage is responsible for height
Pressure demand Hydraulic Elements provide the pressure and flow needed, and its pressure limit is generally 4-6MPa；Low pressure oil way is responsible for low pressure
Demand Hydraulic Elements provide the pressure and flow needed, and its pressure is less than 1MPa, but protection scope of the present invention is not limited to
This.Wherein, the present embodiment for convenience, only by taking utilization of the buncher hydraulic system in hybrid power CVT as an example,
But protection scope of the present invention is not limited thereto.
Wherein, Oil pump electrical machinery is a kind of particular motor of improved driving oil pump.Oil pump electrical machinery includes motor body, front end
Lid and take-off (propeller) shaft, offer in a stepped bore, output transmission retraction drive end bearing bracket on drive end bearing bracket, are a hollow axle,
Axis hole aperture is engaged with the external diameter of the input shaft of oil pump, has a keyway in the spindle nose of take-off (propeller) shaft.
Wherein, double-acting pump can be double for double-acting type vane pump, double-acting type gear pump or double-acting type plunger pump etc.
One kind in process pump, because effect of these double-acting pumps played in hydraulic system is that fluid is pumped into from oil sump,
So only illustrated in the embodiment of the present invention by taking double-acting type vane pump as an example, but protection scope of the present invention is not limited to
This.
In one embodiment, Oil pump electrical machinery 1 is connected with double-acting type vane pump 2, for example, the output shaft of Oil pump electrical machinery 1
The rotor of double-acting type vane pump 2 is connected to by sprocket wheel chain, receives and responds control unit for automatic shift
The rotating speed request signal that (Transmission Control Unit, TCU) is sent, and it is double according to rotating speed request signal driving
Action type vane pump 2.The rotor each rotation of double-acting type vane pump 2, it completes oil suction twice and oil extraction twice, and it includes
Two inlet ports and two oil-outs, two inlet ports are communicated with oil sump 10, the first oil-out 2a and the phase of high-pressure oil passage 8
Logical, the second oil-out 2b is communicated with low pressure oil way 9.After Oil pump electrical machinery 1 drives double-acting type vane pump 2, two inlet ports
Fluid is pumped into from oil sump 10, fluid is then delivered to by high-pressure oil passage 8, and the second oil-out 2b by the first oil-out 2a
Fluid is delivered to low pressure oil way 9.
Then first pressure control valve 5 be set on high-pressure oil passage 8, first pressure control valve 5 respectively with the first oil-out
Driving pulley assembly 6 and passive belt wheel assembly 7 on 2a, high-pressure oil passage 8 are connected, by the oil pressure cntrol on high-pressure oil passage 8 the
One preset pressure, and first preset pressure disclosure satisfy that the pressure demand on high-pressure oil passage 8 needed for Hydraulic Elements, for example, the
One preset pressure is 6MPa.Second pressure control valve 4 is set on low pressure oil way 9, and second pressure control valve 4 goes out with second respectively
Coupled clutch 3 on hydraulic fluid port 2b and low pressure oil way 9 is connected, by the oil pressure cntrol on low pressure oil way 9 in the second preset pressure, and
Second preset pressure disclosure satisfy that the pressure demand on low pressure oil way 9 needed for Hydraulic Elements, for example, the second preset pressure is
0.9MPa。
The embodiment of the present invention compared with prior art, by the way that hydraulic circuit is divided into high-pressure oil passage and low pressure oil way so that
The Hydraulic Elements on Hydraulic Elements and low pressure oil way on high-pressure oil passage are independent, it is to avoid high voltage demands Hydraulic Elements with it is low
Coupling between pressure demand Hydraulic Elements, simplifies hydraulic circuit；Simultaneously because the traffic demand of low pressure requirements Hydraulic Elements
High-pressure oil passage is needed not move through, the power attenuation of hydraulic system can be reduced.And set respectively on high-pressure oil passage and low pressure oil way
Put pressure-control valve so that the pressure of low pressure requirements Hydraulic Elements need not be reduced and obtained by high pressure, reduce hydraulic system
The energy loss of itself.
On the basis of above-described embodiment, the Oil pump electrical machinery is additionally operable to actively be controlled according to hydraulic system real-time traffic demand
The rotating speed of liquefaction pump motor.
Specifically, buncher is during actual operation, under different driving cycles, and the traffic demand of Hydraulic Elements is not
Together, the rotating speed of Oil pump electrical machinery need to only meet the higher value of high and low pressure oil circuit traffic demand.For example, being become in CVT by large speed ratio
Change to it is small speed than when, speed changingratio is very big, and driving pulley is quickly oil-filled, high-pressure oil passage traffic demand be more than low pressure oil way flow
Demand, now the rotating speed of Oil pump electrical machinery need to only meet the traffic demand of high-pressure oil passage；When cruise mode is travelled, main, quilt
Seldom, coupled clutch is combined to be needed to consume larger flow movable belt pulley consumed flow, and low pressure oil way traffic demand is more than hydraulic oil
Road traffic demand, now the rotating speed of Oil pump electrical machinery need to only meet the traffic demand of low pressure oil way.
In the present embodiment, by Oil pump electrical machinery according to hydraulic system real-time traffic demand active control turn of its own
Speed, the flow for enabling double-acting pump to be pumped into meets the demand of hydraulic system in real time, reduces the fluid circulation for being pumped into hydraulic circuit
Amount, reduction hydraulic system input power loss, reaches the purpose for reducing hydraulic system energy loss.
On the basis of above-described embodiment, as shown in figure 3, the low pressure oil way 9 also includes controlling with the first pressure
The first connected pilot solenoid valve 11 of valve 5, the outlet oil pressure for controlling the first pressure control valve 5.
Wherein, pilot solenoid valve is made up of pilot valve with main valve, and both have passage to be connected.When electromagnetic valve coil is powered,
Dynamic iron core opens pilot valve hole with static iron core adhesive, and the pressure of valve element back of the body chamber is flowed to by pilot valve hole to be exported, now valve element back of the body chamber
Pressure be less than inlet pressure, using pressure difference make valve element depart from primary valve, medium from import flow to export.When electromagnetic valve coil is disconnected
When electric, dynamic iron core departs from static iron core, closes pilot valve hole, and valve element back of the body cavity pressure is gradually tended to and entered by the supplement of inlet pressure
Mouth pressure balance, valve element is tight shut-off valve because of spring-force driven dual.
Specifically, when first pressure control valve 5 by the oil pressure cntrol on high-pressure oil passage 8 on it disclosure satisfy that high-pressure oil passage 8
During the pressure demand of Hydraulic Elements, first be connected with first pressure control valve 5 first conduction can also be set on low pressure oil way 9
Magnet valve 11, because the pressure itself demand of pilot solenoid valve is 0.6MPa, therefore is disposed on low pressure oil way 9.According to hydraulic pressure
The demand of system adjusts the input current of the first pilot solenoid valve 11, so as to control the pilot pressure of first pressure control valve 5, so
Afterwards by the balanced action of the pilot force of the valve element itself of first pressure control valve 5, feedback force and spring force, by high-pressure oil passage 8
Oil pressure is adjusted to requirements, and requirements are for needed for the main belt wheel cylinder when changing gear ratio or transmission moment of torsion and passive belt wheel cylinder
Larger oil pressure, for example, required larger oil pressure is 6MPa.
In embodiments of the present invention, by setting the first pilot solenoid valve, control first pressure control on low pressure oil way
The outlet oil pressure of valve, so that high-pressure oil passage oil pressure is adjusted, the pressure demand for alloing it to meet CVT in real time, while meeting main, quilt
The demand and supply of movable belt pulley, reduces the pressure of high-pressure oil passage, reduces CVT power losses.
On the basis of above-described embodiment, as shown in figure 3, the high-pressure oil passage 8 also includes driving pulley pressure-control valve
12 and passive belt wheel pressure-control valve 13.Driving pulley pressure-control valve 12 and the main belt wheel cylinder phase in driving pulley assembly 6
Even, the oil pressure for controlling main belt wheel cylinder；Passive belt wheel pressure-control valve 13 and the passive belt wheel cylinder in passive belt wheel assembly 7
It is connected, the oil pressure for controlling passive belt wheel cylinder.
Wherein, driving pulley assembly includes main belt wheel cylinder, driving pulley piston and driving belt pulley shaft.By adjusting master
Movable belt pulley cylinder oil pressure, promotes driving pulley piston to be moved axially inside main belt wheel cylinder along driving belt pulley shaft, so as to change CVT
Transmission speed ratio and the enough clamping force demands of offer driving pulley.Passive belt wheel assembly includes passive belt wheel cylinder, passive belt wheel
Piston, passive belt shaft and passive belt wheel spring.Passive belt shaft is fixed, and by adjusting passive belt wheel cylinder oil pressure, promotes quilt
Movable belt pulley piston is moved inside passive belt wheel cylinder along passive belt axle axial, so as to change CVT transmission speed ratios and provide quilt
The enough clamping force demands of movable belt pulley.
Specifically, driving pulley pressure-control valve 12 and passive belt wheel pressure-control valve 13 are set on high-pressure oil passage 8, should
Driving pulley pressure-control valve 12 is connected with the main belt wheel cylinder in driving pulley assembly 6, the passive belt wheel pressure-control valve 13
It is connected with the passive belt wheel cylinder in passive belt wheel assembly 7.By driving pulley pressure-control valve 12 by the oil pressure of main belt wheel cylinder
The oil pressure required when transmitting moment of torsion or CVT changes transmission speed ratio is controlled, driving pulley piston is then promoted in main belt wheel cylinder
The inside is moved axially along driving belt pulley shaft, is reached transmission moment of torsion or is changed the purpose of CVT transmission speed ratios.Pass through passive belt wheel pressure
Then control valve 13 pushes away the oil pressure cntrol of the passive belt wheel cylinder oil pressure required when transmitting moment of torsion or CVT changes transmission speed ratio
Move passive belt wheel piston to move along passive belt axle axial inside passive belt wheel cylinder, reach transmission moment of torsion or change CVT transmissions
The purpose of fast ratio.
For example, when needing transmission engine, motor or engine and motor to input the moment of torsion come, passing through main belt
The oil pressure and passive belt wheel pressure-control valve 13 for taking turns the regulation main belt wheel cylinder of pressure-control valve 12 adjust the oil of passive belt wheel cylinder
Pressure, makes the clamping force between metal tape and active and passive belt wheel transmit the requirement of moment of torsion needed for meeting, so as to reach transmission moment of torsion
Purpose.
In embodiments of the present invention, by setting driving pulley pressure-control valve and passive belt wheel pressure on high-pressure oil passage
Control valve, on the basis of first pressure control valve control high-pressure oil passage oil pressure, then will be main by driving pulley pressure-control valve
The oil pressure cntrol of movable belt pulley cylinder is in required pressure value, and passive belt wheel pressure-control valve is by the oil pressure cntrol of passive belt wheel cylinder
In required pressure value, the pressure of high-pressure oil passage is reduced, so as to reduce the power attenuation of hydraulic system.
On the basis of above-described embodiment, as shown in figure 3, the low pressure oil way 9 also includes the He of the second pilot solenoid valve 14
3rd pilot solenoid valve 15.Second pilot solenoid valve 14 is connected with the driving pulley pressure-control valve 12, for controlling
The outlet oil pressure of the driving pulley pressure-control valve 12；3rd pilot solenoid valve 15 and the passive belt wheel Stress control
Valve 13 is connected, the outlet oil pressure for controlling the passive belt wheel pressure-control valve 13.
Specifically, main belt wheel cylinder oil pressure and passive belt wheel pressure-control valve 13 are controlled in driving pulley pressure-control valve 12
Control on the basis of passive belt wheel cylinder oil pressure, the second pilot solenoid valve 14 and the 3rd guide can also be set on low pressure oil way 9
Magnetic valve 15, second pilot solenoid valve 14 is connected with driving pulley pressure-control valve 12, the 3rd pilot solenoid valve 15 and quilt
Movable belt pulley pressure-control valve 13 is connected.
Then the input current of the second pilot solenoid valve 14 is adjusted according to the demand of hydraulic system, so as to control driving pulley
The pilot pressure of pressure-control valve 12, passes through the pilot force of the valve element itself of driving pulley pressure-control valve 12, feedback force and spring
The balanced action of power, by the oil pressure cntrol of main belt wheel cylinder in requirements, when meeting transmission moment of torsion or CVT change transmission speed ratios
Pressure demand.The input current of the 3rd pilot solenoid valve 15 is adjusted according to the demand of hydraulic system, so as to control passive belt wheel
The pilot pressure of pressure-control valve 13, passes through pilot force, feedback force and the spring of the valve element itself of passive belt wheel pressure-control valve 13
The balanced action of power, by the oil pressure cntrol of passive belt wheel cylinder in requirements, when meeting transmission moment of torsion or CVT change transmission speed ratios
Pressure demand.
For example, when needing to change CVT transmission speed ratios, by adjusting the second pilot solenoid valve 14 and the 3rd pilot solenoid valve
15 input current, so as to control the outlet oil pressure of driving pulley pressure-control valve 12 and passive belt wheel Stress control 13, makes master
The oil pressure of movable belt pulley cylinder and passive belt wheel cylinder changes, so as to promote piston to be moved axially along belt shaft, change main belt wheel cylinder and
The radius of clean-up of passive belt wheel cylinder so that the radius of clean-up of metal tape and driving pulley and passive belt wheel changes, and reaches and changes
The purpose of gear ratio.
In embodiments of the present invention, by setting the second pilot solenoid valve and the 3rd pilot solenoid valve on low pressure oil way,
The oil pressure of main belt wheel cylinder and passive belt wheel cylinder is adjusted according to the demand of hydraulic system to requirements so that transmission moment of torsion or
When CVT changes transmission speed ratio, the oil pressure of main belt wheel cylinder and passive belt wheel cylinder can be met, and reduce the pressure of high-pressure oil passage
Power, so as to reduce CVT power losses, and can meet CVT pressure demand in real time.
On the basis of above-described embodiment, as shown in figure 3, the low pressure oil way 9 also includes and the phase of coupled clutch 3
Coupled clutch pressure-control valve 16 even, the oil pressure for controlling the coupled clutch 3.
Specifically, when the oil pressure cntrol on low pressure oil way 9 is being met hydraulic pressure on low pressure oil way 9 by second pressure control valve 4
After the oil pressure demand of element, by setting the coupled clutch pressure-control valve being connected with coupled clutch 3 on low pressure oil way 9
16, by the oil pressure cntrol of coupled clutch 3 pressure value required when changing drive pattern.
On the basis of above-described embodiment, as shown in figure 3, the low pressure oil way 9 also includes and the coupled clutch pressure
The 4th connected pilot solenoid valve 17 of force control valve 16, the outlet oil for controlling the coupled clutch pressure-control valve 16
Pressure.
Specifically, on the basis of the control oil pressure of coupled clutch 3 of coupled clutch pressure-control valve 16, by low pressure
The 4th pilot solenoid valve 17 being connected with coupled clutch pressure-control valve 16 is set on oil circuit 9.According to the demand of hydraulic system
The input current of the 4th pilot solenoid valve 17 is adjusted, so as to control the pilot pressure of coupled clutch pressure-control valve 16, then
By the balanced action of the pilot force of the valve element itself of coupled clutch pressure-control valve 16, feedback force and spring force, will couple from
The oil pressure cntrol of clutch 3 is in requirements, so as to control the state of coupled clutch.
For example, when needing to change power drive mode, for motive and motor serial mixed power, according to hydraulic pressure
The demand of system adjusts the electric current of the 4th pilot solenoid valve 17, so as to adjust the outlet oil of coupled clutch pressure-control valve 16
Pressure, controls the disengaging of coupled clutch 3, cunning to rub or bonding state.When coupled clutch 3 is combined, engine can be selected
With the power drive mode of motor or engine；When coupled clutch 3 is disengaged, motor can only be selected as power drive mould
Formula.
In embodiments of the present invention, by setting the 4th pilot solenoid valve on low pressure oil way, coupled clutch pressure is controlled
The outlet oil pressure of force control valve, reaches the purpose of control coupled clutch state, and the oil pressure cntrol and main belt wheel cylinder and by
The oil pressure cntrol of movable belt pulley cylinder is independent of each other.Simultaneously as the Hydraulic Elements such as coupled clutch and pilot solenoid valve be arranged on it is low
Press oil on road, the Hydraulic Elements such as active and passive band wheel assembly are arranged on high-pressure oil passage, this causes coupled clutch and first conductive magnetism
Substantially without coupling between the Hydraulic Elements such as valve and active and passive belt wheel oil cylinder.
On the basis of above-described embodiment, as shown in figure 3, the low pressure oil way 9 also includes the 3rd pressure-control valve 18, point
Not with first pilot solenoid valve 11, second pilot solenoid valve 14, the 3rd pilot solenoid valve 15 and the described 4th
Pilot solenoid valve connected 17, for controlling first pilot solenoid valve 11, second pilot solenoid valve 14, the described 3rd first
The import oil pressure of conductive magnet valve 15 and the 4th pilot solenoid valve 17.
Specifically, when second pressure control valve 4 by the Stress control on low pressure oil way 9 on it disclosure satisfy that low pressure oil way
After the demand of Hydraulic Elements, on low pressure oil way 9 set the 3rd pressure-control valve 18, its respectively with the first pilot solenoid valve 11,
Second pilot solenoid valve 14, the 3rd pilot solenoid valve 15 are connected with the 4th pilot solenoid valve 17.Pass through electromagnetic fuel supply pressure and bullet
The equilibrium relation of spring force, by electromagnetic fuel supply Stress control in a definite value, meets the pressure demand of pilot solenoid valve fuel feed pump, makes
Pilot solenoid valve works under relatively stable pressure environment, improves the pressure stability of hydraulic system itself.
On the basis of above-described embodiment, the coupled clutch 3 is wet clutch, one end of the wet clutch
It is connected with engine, the other end is connected with the input shaft of the buncher.
Wherein, wet clutch is the clutch cooled down with fluid, and its cooling oil does not shield to friction plate, and makes
Power transmission is smooth soft.Its advantage is that service life is long, will not typically be broken down, unless abuse, often makes
Clutch is in half-clutch operation.It is used in automatic transmission, the manual-automatic integrated speed change such as generally used now
Device.Compressing multiple steel discs and friction plate by the effect of hydraulic cylinder combines clutch, after oil return then under spring force
Separate steel disc and friction plate.
Coupled clutch in the embodiment of the present invention selects wet clutch, its one end is connected with engine, the other end with
The input shaft of buncher is connected.Rub and combine by the disengaging of coupled clutch, cunning, select different power drive modes
And the drive pattern transmitted in the moment of torsion of engine input, the hydraulic system includes：Engine driving, motor driving are sent out
Motivation and motor tandem combination drive.Wet clutch causes power smooth soft in transmittance process, to driver and multiplies
Seat personnel bring good comfortableness.
On the basis of above-described embodiment, the first pressure control valve 5 is pilot operated compound relief valve, the second pressure control
Valve 4 processed is definite value overflow valve, and the 3rd pressure-control valve 18 is fixed pressure reducing valve.
Wherein, overflow valve is a kind of hydraulic pressure control valve, plays level pressure overflow and safeguard protection in hydraulic test
Effect.The main spool spring of pilot operated compound relief valve is mainly used in overcoming the frictional force of valve element, and spring rate is small, when spillway discharge change is drawn
When playing the change of main spool spring decrement, spring force change is smaller, therefore the inlet pressure change of pilot operated compound relief valve is also smaller, its
Regulation precision is high, is widely used in high pressure and Mass flow system.Definite value overflow valve refers to that pressure value is adjusted to constant overflow
Valve.
Wherein, pressure-reducing valve is the restricting element that a local resistance can change, i.e., by changing orifice size, make flow velocity
And the kinetic energy of fluid changes, and the different pressure losses is caused, so as to reach the purpose of decompression.
Specifically, first pressure control valve 5 controls the oil pressure of high-pressure oil passage 8, and the oil pressure on high-pressure oil passage 8 is larger, and
The change or transmission moment of torsion of driving pulley assembly 6 and the meeting of passive belt wheel assembly 7 according to the fast ratios of CVT on high-pressure oil passage 8 is not
Together, its oil pressure demand with wheel cylinder can also be changed, therefore first pressure control valve 5 is set as into pilot operated compound relief valve.This
Sample can improve pressure controling precision, make the oil pressure cntrol of high-pressure oil passage 8 in requirements.
Second pressure control valve 4 controls the oil pressure of low pressure oil way 9, because the Hydraulic Elements on low pressure oil way 9 mainly play choosing
The effect of power drive mode is selected, then the oil pressure change on low pressure oil way 9 is little, therefore second pressure control valve 4 is set as
Definite value overflow valve so that the oil pressure of low pressure oil way disclosure satisfy that the pressure of coupled clutch and pilot solenoid valve demand, this
Sample avoids larger flow consumption, saves CVT power consumption penalties.Each elder generation on 3rd pressure-control valve 18 control low pressure oil way 9
The import oil pressure of conductive magnet valve, because the pressure of pilot solenoid valve self-demand is relatively stablized, therefore by the 3rd pressure-control valve
18 are set to fixed pressure reducing valve.
Buncher hydraulic system in above-described embodiment, by the way that hydraulic circuit is divided into high-pressure oil passage and low pressure oil
Road so that when CVT speed is than changing greatly, now the traffic demand needed for active and passive belt wheel is very big, but due to coupled clutch
With active and passive belt wheel not on same hydraulic circuit, therefore, CVT speed is than that in change procedure, can't influence coupled clutch
State.Meanwhile, the traffic demand of high-pressure oil passage and the traffic demand of low pressure oil way, regulation oil can be calculated in real time by TCU
Pump motor rotating speed, meets their higher value, so avoids larger flow consumption, saves CVT power consumption penalties.
After independently being separated due to high-pressure oil passage and low pressure oil way, the leakage rate of hydraulic system is divided by double-acting pump
Dissipate, therefore, the leakage rate of hydraulic system can also reduce.And high voltage demands Hydraulic Elements pass through height with low pressure requirements Hydraulic Elements
Press oil road and low pressure oil way is independent so that the pressure of low pressure requirements Hydraulic Elements need not be by the way that high pressure drop be lowly come
Obtain, so that the power consumption penalty of hydraulic system itself also can accordingly reduce, while reducing CVT energy loss.
Finally it should be noted that：The above embodiments are merely illustrative of the technical solutions of the present invention, rather than its limitations；Although
The present invention is described in detail with reference to the foregoing embodiments, it will be understood by those within the art that：It still may be used
To be modified to the technical scheme described in foregoing embodiments, or equivalent substitution is carried out to which part technical characteristic；
And these modification or replace, do not make appropriate technical solution essence depart from various embodiments of the present invention technical scheme spirit and
Scope.
Claims (10)
1. a kind of buncher hydraulic system, it is characterised in that including：Oil pump electrical machinery, double-acting pump, high-pressure oil passage and low pressure
Oil circuit；
The Oil pump electrical machinery is connected with the double-acting pump, for driving the double-acting pump；
The double-acting pump includes two inlet ports and two oil-outs；Described two inlet ports are communicated with oil sump, and first
Oil-out is communicated with the high-pressure oil passage, and the second oil-out is communicated with the low pressure oil way；
The high-pressure oil passage include first pressure control valve, the first pressure control valve respectively with first oil-out, institute
The driving pulley assembly and passive belt wheel assembly stated on high-pressure oil passage are connected, the oil pressure for controlling the high-pressure oil passage；
The low pressure oil way include second pressure control valve, the second pressure control valve respectively with second oil-out and institute
The coupled clutch stated on low pressure oil way is connected, the oil pressure for controlling the low pressure oil way.
2. hydraulic system according to claim 1, it is characterised in that the Oil pump electrical machinery is additionally operable to real according to hydraulic system
When traffic demand actively adjust the rotating speed of Oil pump electrical machinery.
3. hydraulic system according to claim 1, it is characterised in that the low pressure oil way also includes and the first pressure
The first connected pilot solenoid valve of control valve, the outlet oil pressure for controlling the first pressure control valve.
4. hydraulic system according to claim 1, it is characterised in that the high-pressure oil passage also includes driving pulley pressure control
Valve and passive belt wheel pressure-control valve processed；The driving pulley pressure-control valve and the driving pulley in the driving pulley assembly
Cylinder is connected, the oil pressure for controlling the main belt wheel cylinder；The passive belt wheel pressure-control valve and the passive belt wheel assembly
In passive belt wheel cylinder be connected, the oil pressure for controlling the passive belt wheel cylinder.
5. hydraulic system according to claim 4, it is characterised in that the low pressure oil way also includes the second pilot solenoid valve
With the 3rd pilot solenoid valve；Second pilot solenoid valve is connected with the driving pulley pressure-control valve, described for controlling
The outlet oil pressure of driving pulley pressure-control valve；3rd pilot solenoid valve is connected with the passive belt wheel pressure-control valve,
Outlet oil pressure for controlling the passive belt wheel pressure-control valve.
6. hydraulic system according to claim 1, it is characterised in that the low pressure oil way also includes coupling clutch with described
The connected coupled clutch pressure-control valve of device, the oil pressure for controlling the coupled clutch.
7. hydraulic system according to claim 6, it is characterised in that the low pressure oil way also includes coupling clutch with described
The 4th connected pilot solenoid valve of device pressure-control valve, the outlet oil pressure for controlling the coupled clutch pressure-control valve.
8. the hydraulic system according to claim 3 or 5 or 7, it is characterised in that the low pressure oil way also includes the 3rd pressure
Control valve, the 3rd pressure-control valve respectively with first pilot solenoid valve, second pilot solenoid valve, the described 3rd
Pilot solenoid valve is connected with the 4th pilot solenoid valve, for controlling first pilot solenoid valve, described second first conductive
The import oil pressure of magnet valve, the 3rd pilot solenoid valve and the 4th pilot solenoid valve.
9. hydraulic system according to claim 1, it is characterised in that the coupled clutch is wet clutch, described
One end of wet clutch is connected with engine, the other end is connected with the input shaft of the buncher.
10. hydraulic system according to claim 1, it is characterised in that the first pressure control valve is pilot-operated type overflow
Valve, the second pressure control valve is definite value overflow valve, and the 3rd pressure-control valve is fixed pressure reducing valve.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710197812.3A CN107061671A (en) | 2017-03-29 | 2017-03-29 | A kind of buncher hydraulic system |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710197812.3A CN107061671A (en) | 2017-03-29 | 2017-03-29 | A kind of buncher hydraulic system |
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| CN107061671A true CN107061671A (en) | 2017-08-18 |
Family
ID=59620704
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| CN201710197812.3A Pending CN107061671A (en) | 2017-03-29 | 2017-03-29 | A kind of buncher hydraulic system |
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