CN205478592U - Pressure control hydraulic system economizer - Google Patents
Pressure control hydraulic system economizer Download PDFInfo
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- CN205478592U CN205478592U CN201620087136.5U CN201620087136U CN205478592U CN 205478592 U CN205478592 U CN 205478592U CN 201620087136 U CN201620087136 U CN 201620087136U CN 205478592 U CN205478592 U CN 205478592U
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Abstract
The utility model provides a pressure control hydraulic system economizer, including variable pump, oil tank, with this variable the communicating energy storage ware of hydraulic fluid port pumps and set up in check valve between energy storage ware and the variable pump, the variable pump is by its discharge capacity of variable cylinder control, the no pole chamber of variable hydro -cylinder is through first damping jogged joint to oil tank, its characterized in that: still include an energy -saving control valves, the energy -saving control valves passes through the oil circuit intercommunication between pressure signal oil pipe and energy storage ware and the check valve, this scheme is passed through pressure signal oil pipe and is transmitted the valves for energy -saving control with energy storage ware entry pressure signal for when the inlet pressure of energy storage ware was higher than the upper limit value of energy -saving control valves settlement, the variable pump was in low pressure float volume standby state, when the inlet pressure of energy storage ware was less than the lower limit value of energy -saving control valves settlement, the variable pump resumeed big discharge capacity again and supplyes fluid to the system, and whole process can reduce the energy consumption, make system's work more stable.
Description
Technical field
This utility model relates to technical field of hydraulic, refers more particularly to a kind of force control hydraulic pressure energy saving of system device.
Background technology
See shown in accompanying drawing 1, existing common force control hydraulic pressure system its typically include variable pump 1e, variable oil cylinder 2e,
Check valve 3e, accumulator 4e, the first damping hole 5e, fuel tank 6e, the second damping hole 7e, pressure valve 8e and overflow valve 9e, become
To accumulator 4e feed flow when amount pump 1e starts, when the outlet pressure of variable pump 1e reach pressure valve 8e spring pressure setting value with
During the setup pressure value sum of overflow valve 9e, the left station of described pressure valve 8e works, and variable pump 1e outlet fluid passes through pressure valve
8e is communicated to variable oil cylinder 2e rodless cavity and variable pump 1e discharge capacity is reduced, and now variable pump 1e is in the standby shape of high-pressure small-displacement
State, its problem being primarily present of above-mentioned force control hydraulic pressure system: during variable pump holding state, its outlet is constantly in high pressure conditions,
Waste energy.In view of this, standby and allow the system more stable Pressure Control Technology of work for how searching out a kind of low pressure
Means are just particularly important.
Summary of the invention
For the deficiencies in the prior art, this utility model aims to provide a kind of force control hydraulic pressure energy saving of system device.
For achieving the above object, this utility model also provides for a kind of force control hydraulic pressure energy saving of system device, including variable pump,
Accumulator that the variable oil cylinder being connected with this variable pump communicates with this variable pump oil-out and be arranged at described accumulator and variable
Check valve between pump, described variable oil cylinder rodless cavity is connected to fuel tank by the first damping hole, and described variable pump oil-out is respectively
Connect with variable cylinder rod chamber and energy-saving control valve group, described energy-saving control valve group the most respectively with fuel tank, variable oil cylinder rodless cavity
And the connection of accumulator entrance, it is characterised in that: include an energy-saving control valve group, and connect described energy-saving control valve group and storage
The pressure signal oil pipe of energy device entrance.
Preferably, described energy-saving control valve group include pressure valve, pilot operated directional control valve, the second damping hole, proportional pressure valve,
Pressure transducer and controller, the described variable pump outlet pressure signal collected is passed to described control by described pressure transducer
Device, described controller sends instruction to described proportional pressure valve and can adjust it and set pressure as P5 value or P6 value, described hydraulic control
The pressure P5 value sum that the spring pressure P4 value that reversal valve sets sets with described proportional pressure valve is set to P1 value, and described hydraulic control is changed
The pressure P6 value sum that the spring pressure P4 value set to valve sets with described proportional pressure valve is set to P2 value, and described pressure valve sets
Fixed spring pressure is P3 value, and when described variable pump starts, described pressure valve and described pilot operated directional control valve are right working position work,
The output of described variable pump huge discharge is to described accumulator energy supply, when described variable pump outlet pressure is more than P3 value, described pressure valve
Left station works, and when described accumulator inlet pressure is more than P1 value, the left station of described pilot operated directional control valve works, described variable pump
Outlet high-voltage oil liquid connects with described variable oil cylinder rodless cavity and described variable pump discharge capacity is reduced, described closed check valve, institute
State variable pump outlet pressure to reduce and cause described controller to send instructions to described proportional pressure valve making its force value be P6, described change
Amount pump discharge pressure continues to drop to P3 value, and the most described variable pump is in low pressure small displacement holding state；When described accumulator enters
When mouth pressure is less than P2 value, described pilot operated directional control valve right working position works, and described variable oil cylinder rodless cavity connects described fuel tank, described
Variable pump discharge capacity increases, and described variable pump outlet pressure increases and causes described controller to send instructions to described proportional pressure valve making it
Force value is P5, and when described accumulator inlet pressure is again more than P1 value, whole process circulates successively, automatically adjusts.
Preferably, described energy-saving control valve group includes pressure valve, the first pilot operated directional control valve, the second pilot operated directional control valve, the first elder generation
Lead overflow valve, the second precursor overflow valve, the second damping hole, the 3rd damping hole, the 4th damping hole, described first pilot operated directional control valve
The pressure P5 value sum that the spring pressure P4 value set sets with described first precursor overflow valve is set to P1 value, described first hydraulic control
The pressure P6 value sum that the spring pressure P4 value that reversal valve sets sets with the second precursor overflow valve is set to P2 value, described pressure valve
The spring pressure set as P3 value, described variable pump huge discharge output to described accumulator energy supply, described second liquid when just starting
Station work under control reversal valve, described first pilot operated directional control valve right working position work so that the hydraulic coupling at described pressure valve spool two ends
Equal, under the promotion of its right-hand member spring force, described pressure valve right working position works, until described accumulator inlet pressure is more than P1
During value, described first pilot operated directional control valve left station work, the left station of described pressure valve works, described variable pump outlet high-voltage oil liquid
Connect with described variable oil cylinder rodless cavity and described variable pump discharge capacity is reduced, described closed check valve, going out of described variable pump
Mouth pressure decline causes station work on described second pilot operated directional control valve, and described variable pump outlet pressure continues to drop to P3 value, this
Shi Suoshu variable pump is in low pressure small displacement holding state；When described accumulator inlet pressure is less than P2 value, described first hydraulic control
Reversal valve and described pressure valve are all in right working position work, and described variable pump discharge capacity increases to accumulator energy supply, the second liquid controlled reversing
Station work under valve, when described accumulator inlet pressure is again more than P1 value, whole process circulates successively, automatically adjusts.
Preferably, described energy-saving control valve group include pressure valve, pilot operated directional control valve, throttled directional valve, precursor overflow valve,
Two damping holes, the 3rd damping hole, the 4th damping hole, described pilot operated directional control valve sets spring pressure as P4 value, described guide's overflow
Valve sets pressure as P5 value, described throttled directional valve spool keep left work time produce pressure differential P6 value, its left station works time institute
Stating the 3rd damping hole to be shorted, P4 value, P5 value and P6 value sum are set as that described P1 value, P4 value are set as with P5 value sum
Described P2 value, the spring pressure that described pressure valve sets is as P3 value, when just starting described variable pump, described pressure valve right working position
Work, described throttled directional valve spool keeps left work, and described pilot operated directional control valve right working position works, and described variable pump huge discharge exports
To described accumulator energy supply, when described variable pump outlet pressure is more than P3 value, the left station of described pressure valve works, until described
When accumulator inlet pressure is more than P1 value, the left station of described pilot operated directional control valve works, and described variable pump outlet high-voltage oil liquid is through institute
State pressure valve, pilot operated directional control valve is communicated to described variable oil cylinder rodless cavity and described variable pump discharge capacity is reduced, described check valve
Closing, the outlet pressure decline of described variable pump causes the left station of described throttled directional valve to work, and described variable pump outlet pressure continues
Continuing and drop to P3 value, the most described variable pump is in low pressure small displacement holding state；When described accumulator inlet pressure is less than P2
During value, described pilot operated directional control valve right working position works, and described variable oil cylinder rodless cavity connects described fuel tank, and described variable pump discharge capacity increases
Big to accumulator energy supply, described throttled directional valve spool keeps left, when described accumulator inlet pressure is again more than P1 value, whole
Process circulates successively, automatically adjusts.
Preferably, described energy-saving control valve group include pressure valve, the first pilot operated directional control valve, the second pilot operated directional control valve, first
Precursor overflow valve, the second precursor overflow valve, the second damping hole, the 3rd damping hole, the spring that described first pilot operated directional control valve sets
The pressure P5 value sum that pressure P4 value and described first precursor overflow valve set is set to P1 value, and described first pilot operated directional control valve sets
The pressure P6 value sum that sets of spring pressure P4 value and described second precursor overflow valve be set to P2 value, the setting of described pressure valve
Spring pressure is P3 value, and when just starting, described variable pump huge discharge exports and to described accumulator energy supply, described second liquid controlled reversing
Station work under valve, described first pilot operated directional control valve and described pressure valve are all in right working position work, when described variable pump outlet pressure
When power is more than P3 value, the left station of described pressure valve works, during until described accumulator inlet pressure is more than P1 value, and described first
The left station of pilot operated directional control valve works, and described variable pump outlet high-voltage oil liquid connects with described variable oil cylinder rodless cavity and makes described change
Amount pumpage reduces, described closed check valve, and the outlet pressure decline of described variable pump causes work on described second pilot operated directional control valve
Position work, described variable pump outlet pressure continues to drop to P3 value, and the most described variable pump is in low pressure small displacement holding state；
When described accumulator inlet pressure is less than P2 value, described first pilot operated directional control valve right working position work, described variable pump discharge capacity increases
Station work under accumulator energy supply, the second pilot operated directional control valve, when described accumulator inlet pressure is again more than P1 value, whole
Process circulates successively, automatically adjusts.
This programme passes through the control to accumulator inlet pressure of the energy-saving control valve group so that when accumulator inlet pressure is higher than setting
Higher limit time, variable pump is in low pressure small displacement holding state；When accumulator inlet pressure is less than the lower limit set, become
Amount pump huge discharge again supplements fluid to system, and whole process Automatic Cycle adjusts, it is possible to reduces energy consumption and makes system work more stable.
Accompanying drawing explanation
Fig. 1 is existing force control hydraulic pressure system principle structural representation.
Fig. 2 is force control hydraulic pressure energy saving of system principle of device structure chart of the present utility model.
Fig. 3 is the force control hydraulic pressure energy saving of system device embodiment 1 structural principle schematic diagram in this utility model.
Fig. 4 is the force control hydraulic pressure energy saving of system device embodiment 2 structural principle schematic diagram in this utility model.
Fig. 5 is the force control hydraulic pressure energy saving of system device embodiment 3 structural principle schematic diagram in this utility model.
Fig. 6 is the force control hydraulic pressure energy saving of system device embodiment 4 structural principle schematic diagram in this utility model.
Detailed description of the invention
Below in conjunction with the accompanying drawings and specific embodiment, the utility model will be further described, in order to clearer understands this
The technological thought that utility model is claimed.
With reference to Fig. 2, the present embodiment provides a kind of force control hydraulic pressure energy saving of system device, including variable pump 1 and this change
The accumulator 4 that communicates with this variable pump 1 oil-out of variable oil cylinder 2 that amount pump 1 connects and be arranged at described accumulator 4 and become
Check valve 3 between amount pump 1, described variable oil cylinder 2 rodless cavity is connected to fuel tank 6, described variable pump by the first damping hole 5
1 oil-out connects with variable oil cylinder 2 rod chamber and energy-saving control valve group 7 respectively, described energy-saving control valve group 7 the most respectively with fuel tank
6, variable oil cylinder 2 rodless cavity and the connection of accumulator 4 entrance, it is characterised in that: include an energy-saving control valve group 7, Yi Jilian
Meet the pressure signal oil pipe v of described energy-saving control valve group 7 and accumulator 4 entrance.
Embodiment 1:
With reference to Fig. 3, above-mentioned energy-saving control valve group 7 includes pressure valve 8a, pilot operated directional control valve 9a, the second damping hole 10a, ratio pressure
Power valve 11a, pressure transducer 12a and controller 13a, the described variable pump 1 collected is exported by described pressure transducer 12a
Pressure signal transmission is sent instruction to described controller 13a, described controller 13a and adjusts its setting to described proportional pressure valve 11a
Pressure is P5 value or P6 value, and the spring pressure P4 value that described pilot operated directional control valve 9a sets sets with described proportional pressure valve 11a
Pressure P5 value sum be set to P1 value, spring pressure P4 value that described pilot operated directional control valve 9a sets and described proportional pressure valve 11a
The pressure P6 value sum set is set to P2 value, and the spring pressure that described pressure valve 8a sets opens as P3 value, described variable pump 1
Time dynamic, described pressure valve 8a and described pilot operated directional control valve 9a are right working position work, and described variable pump 1 huge discharge exports to institute
Stating accumulator 4 energy supply, when described variable pump 1 outlet pressure is more than P3 value, the left station of described pressure valve 8a works, works as institute
When stating accumulator 4 inlet pressure more than P1 value, the described left station of pilot operated directional control valve 9a works, and described variable pump 1 exports high pressure
Fluid connects with described variable oil cylinder 2 rodless cavity and described variable pump 1 discharge capacity is reduced, and described check valve 3 is closed, described
Variable pump 1 outlet pressure reduces and causes described controller 13a to send instructions to described proportional pressure valve 11a making its setup pressure value
For P6, described variable pump 1 outlet pressure continues to drop to P3 value, and the most described variable pump 1 is in the standby shape of low pressure small displacement
State；When described accumulator 4 inlet pressure is less than P2 value, described pilot operated directional control valve 9a right working position works, described variable oil cylinder 2
Rodless cavity connects described fuel tank 6, and described variable pump 1 discharge capacity increases, and the increase of described variable pump 1 outlet pressure causes described controller
13a sends instructions to described proportional pressure valve 11a makes its setup pressure value be P5, when described accumulator 4 inlet pressure is the biggest
When P1 value, whole process circulates successively, automatically adjusts.
Embodiment 2:
With reference to Fig. 4, above-mentioned energy-saving control valve 7 groups include pressure valve 8b, the first pilot operated directional control valve 9b, the second pilot operated directional control valve 10b,
First precursor overflow valve 11b, the second precursor overflow valve 12b, the second damping hole 13b, the 3rd damping hole 14b, the 4th damping hole
15b, the pressure that the spring pressure P4 value that described first pilot operated directional control valve 9b sets sets with described first precursor overflow valve 11b
P5 value sum is set to P1 value, the spring pressure P4 value of described first pilot operated directional control valve 9b setting and the second precursor overflow valve 12b
The pressure P6 value sum set is set to P2 value, and the spring pressure that described pressure valve 8b sets is as P3 value, described change when just starting
Amount pump 1 huge discharge output station work under the energy supply of described accumulator 4, described second pilot operated directional control valve 10b, described first
Pilot operated directional control valve 9b right working position works so that the hydraulic coupling at described pressure valve 8b spool two ends is equal, at its right-hand member spring force
Under promotion, described pressure valve 8b right working position works, until described accumulator 4 inlet pressure is more than P1 value, described first hydraulic control
The left station of reversal valve 9b works, and the left station of described pressure valve 8b works, and described variable pump 1 exports high-voltage oil liquid and described variable
Oil cylinder 2 rodless cavity connects and described variable pump 1 discharge capacity is reduced, and described check valve 3 is closed, the outlet of described variable pump 1
Pressure decline causes station work on described second pilot operated directional control valve 10b, and described variable pump 1 outlet pressure continues to drop to P3 value,
The most described variable pump 1 is in low pressure small displacement holding state；When described accumulator 4 inlet pressure is less than P2 value, described the
One pilot operated directional control valve 9b and described pressure valve 8b are all in right working position work, and the increase of described variable pump 1 discharge capacity supplies to accumulator 4
Can, station work under the second pilot operated directional control valve 10b, when described accumulator 4 inlet pressure is again more than P1 value, whole process
Circulate successively, automatically adjust.
Embodiment 3:
With reference to Fig. 5, above-mentioned energy-saving control valve group 7 includes pressure valve 8c, pilot operated directional control valve 9c, throttled directional valve 10c, Xian Daoyi
Stream valve 11c, the second damping hole 12c, the 3rd damping hole 13c, the 4th damping hole 14c, described pilot operated directional control valve 9c sets spring
Pressure P4 value, described precursor overflow valve 11c sets pressure P5 value, described throttled directional valve 10c spool keep left work time produce
Pressure differential P6 value, the 3rd damping hole 13c described in during the work of its left station is shorted, and P4 value, P5 value are set as with P6 value sum
Described P1 value, P4 value and P5 value sum be set as described P2 value, and described pressure valve 8c sets spring pressure as P3 value, just
When starting described variable pump 1, described pressure valve 8c right working position works, and described throttled directional valve 10c spool keeps left work, described
Pilot operated directional control valve 9c right working position works, and described variable pump 1 huge discharge exports to the energy supply of described accumulator 4, when described variable pump 1
When outlet pressure is more than P3 value, the left station of described pressure valve 8c works, during until described accumulator 4 inlet pressure is more than P1 value,
The described left station of pilot operated directional control valve 9c works, and described variable pump 1 exports high-voltage oil liquid through described pressure valve 8c, pilot operated directional control valve
9c is communicated to described variable oil cylinder 2 rodless cavity and described variable pump 1 discharge capacity is reduced, and described check valve 3 is closed, described change
The outlet pressure decline of amount pump 1 causes the described left station of throttled directional valve 10c to work, under described variable pump 1 outlet pressure continues
Being down to P3 value, the most described variable pump 1 is in low pressure small displacement holding state；When described accumulator 4 inlet pressure is less than P2
During value, described pilot operated directional control valve 9c right working position works, and described variable oil cylinder 2 rodless cavity connects described fuel tank 6, described variable pump
1 discharge capacity increases to accumulator 4 energy supply, and described throttled directional valve 10c spool keeps left, when described accumulator 4 inlet pressure is the biggest
When P1 value, whole process circulates successively, automatically adjusts.
Embodiment 4:
With reference to Fig. 6, above-mentioned energy-saving control valve 7 groups include pressure valve 8d, the first pilot operated directional control valve 9d, the second pilot operated directional control valve 10d,
First precursor overflow valve 11d, the second precursor overflow valve 12d, the second damping hole 13d, the 3rd damping hole 14d, described first liquid
The pressure P5 value sum that the spring pressure P4 value that control reversal valve 9d sets sets with described first precursor overflow valve 11d is set to P1
Value, the pressure P6 that the spring pressure P4 value that described first pilot operated directional control valve 9d sets sets with described second precursor overflow valve 12d
Value sum is set to P2 value, and the spring pressure that described pressure valve 8d sets is as P3 value, and when just starting, described variable pump 1 huge discharge is defeated
Go out and under the energy supply of described accumulator 4, described second pilot operated directional control valve 10d station work, described first pilot operated directional control valve 9d and
Described pressure valve 8d is all in right working position work, and when described variable pump 1 outlet pressure is more than P3 value, described pressure valve 8d is left
Station works, during until described accumulator 4 inlet pressure is more than P1 value, and described first pilot operated directional control valve 9d left station work,
Described variable pump 1 exports high-voltage oil liquid and connects with described variable oil cylinder 2 rodless cavity and described variable pump 1 discharge capacity is reduced, institute
Stating check valve 3 to close, the outlet pressure decline of described variable pump 1 causes station work on described second pilot operated directional control valve 10d,
Described variable pump 1 outlet pressure continues to drop to P3 value, and the most described variable pump 1 is in low pressure small displacement holding state；Work as institute
When stating accumulator 4 inlet pressure less than P2 value, described first pilot operated directional control valve 9d right working position work, described variable pump 1 discharge capacity
Increase station work under accumulator 4 energy supply, the second pilot operated directional control valve 10d, when described accumulator 4 inlet pressure is more than again
During P1 value, whole process circulates successively, automatically adjusts.
Need to further illustrate: the pressure signal oil pipe in energy saver plays and passed to by accumulator inlet pressure signals
The effect of energy-saving control valve group, it is also possible to install pressure transducer or relay at accumulator entrance, pressure signal herein is adopted
It is converted into the signal of telecommunication after collecting and doing suitably process and passes to energy-saving control valve group, it is possible to achieve the pressure control function of equivalent；Simultaneously
As special circumstances, the P1 value that energy-saving control valve group sets can be equal to P2 value；And hydraulic system can be organized accumulation of energy more
Device, is respectively arranged with check valve between they and variable pump outlet, can draw pressure signal oil respectively from often organizing accumulator entrance
Pipe, to energy-saving control valve group, equally realizes pressure control function, all should be within protection domain.
This utility model can overcome variable pump in conventional pressure control system to be constantly in the problem of high-pressure work state, makes
Obtain the standby holding low pressure small displacement state at present of variable pump, energy consumption can be reduced and make system work more stable.
The examples of implementation of the above are only the preferred embodiment of this utility model, not limit reality of the present utility model with this
Executing scope, therefore the change that all shapes according to this utility model, principle are made, all should contain in protection domain of the present utility model.
Claims (5)
1. a force control hydraulic pressure energy saving of system device, including variable pump, the variable oil cylinder being connected with this variable pump, the accumulator that communicates with this variable pump oil-out and be arranged at the check valve between described accumulator and variable pump, described variable oil cylinder rodless cavity is connected to fuel tank by the first damping hole, described variable pump oil-out connects with variable cylinder rod chamber and energy-saving control valve group respectively, described energy-saving control valve group the most respectively with fuel tank, variable oil cylinder rodless cavity and the connection of accumulator entrance, it is characterized in that: include an energy-saving control valve group, and connect the pressure signal oil pipe of described energy-saving control valve group and accumulator entrance.
nullA kind of force control hydraulic pressure energy saving of system device the most according to claim 1，It is characterized in that: described energy-saving control valve group includes pressure valve、Pilot operated directional control valve、Second damping hole、Proportional pressure valve、Pressure transducer and controller，The described variable pump outlet pressure signal collected is passed to described controller by described pressure transducer，Described controller sends instruction to described proportional pressure valve and can adjust it and set pressure as P5 value or P6 value，The pressure P5 value sum that the spring pressure P4 value that described pilot operated directional control valve sets sets with described proportional pressure valve is set to P1 value，The pressure P6 value sum that the spring pressure P4 value that described pilot operated directional control valve sets sets with described proportional pressure valve is set to P2 value，The spring pressure that described pressure valve sets is as P3 value，When described variable pump starts，Described pressure valve and described pilot operated directional control valve are right working position work，Described variable pump huge discharge exports to described accumulator energy supply，When described variable pump outlet pressure is more than P3 value，The left station of described pressure valve works，When described accumulator inlet pressure is more than P1 value，The left station of described pilot operated directional control valve works，Described variable pump outlet high-voltage oil liquid connects with described variable oil cylinder rodless cavity and described variable pump discharge capacity is reduced，Described closed check valve，Described variable pump outlet pressure reduces and causes described controller to send instructions to described proportional pressure valve making its force value be P6，Described variable pump outlet pressure continues to drop to P3 value，The most described variable pump is in low pressure small displacement holding state；When described accumulator inlet pressure is less than P2 value, described pilot operated directional control valve right working position works, described variable oil cylinder rodless cavity connects described fuel tank, described variable pump discharge capacity increases, described variable pump outlet pressure increases and causes described controller to send instructions to described proportional pressure valve making its force value be P5, when described accumulator inlet pressure is again more than P1 value, whole process circulates successively, automatically adjusts.
nullA kind of force control hydraulic pressure energy saving of system device the most according to claim 1，It is characterized in that: described energy-saving control valve group includes pressure valve、First pilot operated directional control valve、Second pilot operated directional control valve、First precursor overflow valve、Second precursor overflow valve、Second damping hole、3rd damping hole、4th damping hole，The pressure P5 value sum that the spring pressure P4 value that described first pilot operated directional control valve sets sets with described first precursor overflow valve is set to P1 value，The pressure P6 value sum that the spring pressure P4 value that described first pilot operated directional control valve sets sets with described second precursor overflow valve is set to P2 value，The spring pressure that described pressure valve sets is as P3 value，When just starting, described variable pump huge discharge exports and to described accumulator energy supply，Station work under described second pilot operated directional control valve，Described first pilot operated directional control valve right working position work，The hydraulic coupling making described pressure valve spool two ends is equal，Under the promotion of its right-hand member spring force，Described pressure valve right working position works，During until described accumulator inlet pressure is more than P1 value，Described first pilot operated directional control valve left station work，The left station of described pressure valve works，Described variable pump outlet high-voltage oil liquid connects with described variable oil cylinder rodless cavity and described variable pump discharge capacity is reduced，Described closed check valve，The outlet pressure decline of described variable pump causes station work on described second pilot operated directional control valve，Described variable pump outlet pressure continues to drop to P3 value，The most described variable pump is in low pressure small displacement holding state；When described accumulator inlet pressure is less than P2 value, described first pilot operated directional control valve and described pressure valve are all in right working position work, described variable pump discharge capacity increases to accumulator energy supply, station work under second pilot operated directional control valve, when described accumulator inlet pressure is again more than P1 value, whole process circulates successively, automatically adjusts.
nullA kind of force control hydraulic pressure energy saving of system device the most according to claim 1，It is characterized in that: described energy-saving control valve group includes pressure valve、Pilot operated directional control valve、Throttled directional valve、Precursor overflow valve、Second damping hole、3rd damping hole、4th damping hole，Described pilot operated directional control valve sets spring pressure as P4 value，Described precursor overflow valve sets pressure as P5 value，Described throttled directional valve spool keep left work time produce pressure differential P6 value，3rd damping hole described in during the work of its left station is shorted，P4 value、P5 value and P6 value sum are set as P1 value，P4 value and P5 value sum are set as P2 value，Described pressure valve sets spring pressure as P3 value，When just starting described variable pump，Described pressure valve right working position works，Described throttled directional valve spool keeps left work，Described pilot operated directional control valve right working position works，Described variable pump huge discharge exports to described accumulator energy supply，When described variable pump outlet pressure is more than P3 value，The left station of described pressure valve works，During until described accumulator inlet pressure is more than P1 value，The left station of described pilot operated directional control valve works，Described variable pump outlet high-voltage oil liquid is through described pressure valve、Pilot operated directional control valve is communicated to described variable oil cylinder rodless cavity and described variable pump discharge capacity is reduced，Described closed check valve，The outlet pressure decline of described variable pump causes the left station of described throttled directional valve to work，Described variable pump outlet pressure continues to drop to P3 value，The most described variable pump is in low pressure small displacement holding state；When described accumulator inlet pressure is less than P2 value, described pilot operated directional control valve right working position works, described variable oil cylinder rodless cavity connects described fuel tank, described variable pump discharge capacity increases to accumulator energy supply, described throttled directional valve spool keeps left, when described accumulator inlet pressure is again more than P1 value, whole process circulates successively, automatically adjusts.
nullA kind of force control hydraulic pressure energy saving of system device the most according to claim 1，It is characterized in that: described energy-saving control valve group includes pressure valve、First pilot operated directional control valve、Second pilot operated directional control valve、First precursor overflow valve、Second precursor overflow valve、Second damping hole、3rd damping hole，The pressure P5 value sum that the spring pressure P4 value that described first pilot operated directional control valve sets sets with described first precursor overflow valve is set to P1 value，The pressure P6 value sum that the spring pressure P4 value that described first pilot operated directional control valve sets sets with described second precursor overflow valve is set to P2 value，The spring pressure that described pressure valve sets is as P3 value，When just starting, described variable pump huge discharge exports and to described accumulator energy supply，Station work under described second pilot operated directional control valve，Described first pilot operated directional control valve and described pressure valve are all in right working position work，When described variable pump outlet pressure is more than P3 value，The left station of described pressure valve works，During until described accumulator inlet pressure is more than P1 value，Described first pilot operated directional control valve left station work，Described variable pump outlet high-voltage oil liquid connects with described variable oil cylinder rodless cavity and described variable pump discharge capacity is reduced，Described closed check valve，The outlet pressure decline of described variable pump causes station work on described second pilot operated directional control valve，Described variable pump outlet pressure continues to drop to P3 value，The most described variable pump is in low pressure small displacement holding state；When described accumulator inlet pressure is less than P2 value, described first pilot operated directional control valve right working position work, described variable pump discharge capacity increases station work under accumulator energy supply, the second pilot operated directional control valve, when described accumulator inlet pressure is again more than P1 value, whole process circulates successively, automatically adjusts.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201620087136.5U CN205478592U (en) | 2016-01-28 | 2016-01-28 | Pressure control hydraulic system economizer |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201620087136.5U CN205478592U (en) | 2016-01-28 | 2016-01-28 | Pressure control hydraulic system economizer |
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| Publication Number | Publication Date |
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| CN205478592U true CN205478592U (en) | 2016-08-17 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201620087136.5U Withdrawn - After Issue CN205478592U (en) | 2016-01-28 | 2016-01-28 | Pressure control hydraulic system economizer |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105485067A (en) * | 2016-01-28 | 2016-04-13 | 邓贲 | Energy-saving method and energy-saving device of pressure control hydraulic system |
| CN108104183A (en) * | 2017-12-28 | 2018-06-01 | 潍柴动力股份有限公司 | A kind of hydraulic excavator bucket regenerating unit and hydraulic crawler excavator |
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2016
- 2016-01-28 CN CN201620087136.5U patent/CN205478592U/en not_active Withdrawn - After Issue
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN105485067A (en) * | 2016-01-28 | 2016-04-13 | 邓贲 | Energy-saving method and energy-saving device of pressure control hydraulic system |
| CN107313995A (en) * | 2016-01-28 | 2017-11-03 | 邓贲 | A kind of force control hydraulic pressure energy saving of system method and its energy saver |
| CN107327426A (en) * | 2016-01-28 | 2017-11-07 | 邓贲 | A kind of force control hydraulic pressure energy saving of system method and its energy saver |
| CN107524642A (en) * | 2016-01-28 | 2017-12-29 | 邓贲 | A kind of force control hydraulic pressure energy saving of system method and its energy saver |
| CN107313995B (en) * | 2016-01-28 | 2018-10-19 | 广东天恒液压机械有限公司 | A kind of force control hydraulic pressure energy saving of system method and its energy saver |
| CN107327426B (en) * | 2016-01-28 | 2018-10-19 | 佛山市佛锐达机电科技有限公司 | A kind of force control hydraulic pressure energy saving of system method and its energy saver |
| CN108104183A (en) * | 2017-12-28 | 2018-06-01 | 潍柴动力股份有限公司 | A kind of hydraulic excavator bucket regenerating unit and hydraulic crawler excavator |
| CN108104183B (en) * | 2017-12-28 | 2020-07-28 | 潍柴动力股份有限公司 | Bucket rod regenerating device of hydraulic excavator and hydraulic excavator |
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