CN106870473B - A kind of pressure-transforming energy-saving four-way proportional flow commutator of recyclable inertia kinetic energy - Google Patents
A kind of pressure-transforming energy-saving four-way proportional flow commutator of recyclable inertia kinetic energy Download PDFInfo
- Publication number
- CN106870473B CN106870473B CN201710223227.6A CN201710223227A CN106870473B CN 106870473 B CN106870473 B CN 106870473B CN 201710223227 A CN201710223227 A CN 201710223227A CN 106870473 B CN106870473 B CN 106870473B
- Authority
- CN
- China
- Prior art keywords
- valve
- mouths
- control
- overflow
- pressure
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
- 239000012530 fluid Substances 0.000 claims description 56
- 239000007788 liquid Substances 0.000 claims description 24
- 230000006835 compression Effects 0.000 claims description 11
- 238000007906 compression Methods 0.000 claims description 11
- 230000008676 import Effects 0.000 claims description 8
- 230000009466 transformation Effects 0.000 claims description 6
- 230000007246 mechanism Effects 0.000 claims description 5
- 230000017105 transposition Effects 0.000 claims description 3
- 238000011084 recovery Methods 0.000 abstract description 4
- 239000003921 oil Substances 0.000 description 32
- 230000008859 change Effects 0.000 description 9
- 238000010438 heat treatment Methods 0.000 description 5
- 238000000034 method Methods 0.000 description 5
- 230000008569 process Effects 0.000 description 4
- 230000009471 action Effects 0.000 description 2
- 230000033228 biological regulation Effects 0.000 description 2
- 238000006243 chemical reaction Methods 0.000 description 2
- 238000010276 construction Methods 0.000 description 2
- 230000001276 controlling effect Effects 0.000 description 2
- 238000001816 cooling Methods 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 238000004134 energy conservation Methods 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 239000002828 fuel tank Substances 0.000 description 2
- 230000017525 heat dissipation Effects 0.000 description 2
- 239000010720 hydraulic oil Substances 0.000 description 2
- 230000006872 improvement Effects 0.000 description 2
- 238000005259 measurement Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 238000005299 abrasion Methods 0.000 description 1
- 230000001133 acceleration Effects 0.000 description 1
- 230000032683 aging Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000013527 convolutional neural network Methods 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000020169 heat generation Effects 0.000 description 1
- 238000005213 imbibition Methods 0.000 description 1
- 230000003647 oxidation Effects 0.000 description 1
- 238000007254 oxidation reaction Methods 0.000 description 1
- 238000010422 painting Methods 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 238000011105 stabilization Methods 0.000 description 1
- 238000012546 transfer Methods 0.000 description 1
- 239000002699 waste material Substances 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B3/00—Intensifiers or fluid-pressure converters, e.g. pressure exchangers; Conveying pressure from one fluid system to another, without contact between the fluids
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/14—Energy-recuperation means
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Servomotors (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention discloses a kind of pressure-transforming energy-saving four-way proportional flow commutator of recyclable inertia kinetic energy, including hydraulic transformer, valve plate corner oil cylinder, overflow control angular valve, pressure difference control angular valve, check valve, the proportional reversing valve that surges, inertia overflow selector valve and shuttle valve；Valve plate corner is driven by valve plate corner oil cylinder, the control signal of overflow control angular valve is derived from the U mouths of inertia overflow selector valve, the G mouths and H mouths of overflow control angular valve connect two control ports of valve plate corner oil cylinder, the E mouths and F mouths of overflow control angular valve connect the K mouths and L mouths of pressure difference control angular valve, the J mouths of pressure difference control angular valve connect hydraulic power source, I mouth connected tanks, two control ports of pressure difference control corner valve core are connected with the C mouths and D mouths of proportional reversing valve respectively.The present invention can realize the mechanical energy of proportionality velocity modulation control, and can recovery inertia kinetic energy and negative load under conditions of valve port pressure difference very little.
Description
Technical field
The present invention relates to a kind of pressure-transforming energy-saving four-way proportional flow commutator of recyclable inertia kinetic energy, belong to hydraulic drive
With control technology.
Background technology
Present hydraulic construction machine typically controls proportional reversing valve with manual pilot valve, then is controlled and loaded by proportional reversing valve
Commutation and speed.If system liquid supply pressure is more much bigger than load pressure, fluid falls very big pressure through proportional reversing valve throttling
Difference, very big power loss is produced, the efficiency of system is very low, and causes the rise of oil liquid temperature.For driving very big inertia
The load of operating mechanism, such as excavator rotary motor, in order to improve efficiency, allow hydraulic motor to accelerate to maximal rate, then cut
Cut-off liquid, the rotational kinetic energy of load are converted into the heat energy that hydraulic energy becomes fluid from overflow valve overflow, can also cause fluid temperature
The rise of degree.The rise of oil liquid temperature will decline hydraulic oil viscosity, accelerate the abrasion of hydraulic system internal moving parts, cause
System leak increase, volumetric efficiency decline；Hydraulic Elements produce thermal expansion, cause hydraulic valve work insensitive or stuck；Work as oil
When temperature is more than 55 DEG C, the oxidation of hydraulic oil will be aggravated, service life shortens.So it must be equipped with the heat dissipation equipment handle of relatively high power
Oil liquid temperature is reduced to the scope of system requirements, so increases the consumption of power again.
Furthermore because load pressure and system pressure change with load behavior, although proportional reversing valve control signal and valve element
Shift invariant, the pressure difference of proportional reversing valve restriction are also becoming, and the flow of proportional reversing valve output is becoming, and is controlled the speed of load
Also becoming, so that the maneuverability of equipment is poor, particularly multiple loads act simultaneously when, the multiple joysticks of one man operation,
It is difficult to coordinate the length velocity relation between load, cause device action inaccurate, or even accident occurs.Need to configure pressure for this
Unnecessary pressure is fallen in compensator, throttling, keeps proportional reversing valve valve port pressure constant, adds heating again.
The content of the invention
Goal of the invention：Present valve control hydraulic system, it is heat energy wave hydraulic energy transfer by flow restriction control loading speed
Expense is fallen so that hydraulic fluid temperature raises, in order to prevent fluid aging because of overheat, it is also necessary to set up cooling system, cooling is set
It is standby also to waste the energy.Therefore, the present invention designs a kind of pressure-transforming energy-saving of recyclable inertia kinetic energy for construction machinery hydraulic system
Four-way proportional flow commutator, it is adapted by transformation liquid supply pressure and load, and can guarantee that proportional reversing valve valve port pressure
Difference is constant, it is not necessary to pressure compensator, can also control the velocity-stabilization of load, device manipulation is good.Use this proportional flow
Commutator substantially reduces liquid energy loss.Four-way proportional flow commutator can also reclaim the hydraulic pressure of the rotational kinetic energy conversion of load
Energy.Therefore, the use of proportional flow commutator improves system effectiveness, reduces system heat generation and fluid temperature rise, reduces and is
Standby heat dissipation equipment specification under unified central planning.
Technical scheme：To achieve the above object, the technical solution adopted by the present invention is：
A kind of pressure-transforming energy-saving four-way proportional flow commutator of recyclable inertia kinetic energy, including hydraulic transformer, valve plate
Corner oil cylinder, overflow control angular valve, pressure difference control angular valve, check valve, the proportional reversing valve that surges, inertia overflow selector valve and
Shuttle valve, two hydraulic fluid ports of load are designated as R mouths and S mouths respectively；
The hydraulic transformer has three hydraulic fluid ports, is designated as P respectivelyAMouth, PBMouth and PTMouthful, PAMouth meets hydraulic power source, PBMouth order
The P mouths of oil-out and the proportional reversing valve that surges to valve, PTMouthful connected tank, the valve plate rotation angle mechanism of hydraulic transformer by with
Two control port input pressures difference control of flow table corner oil cylinder；
The proportional reversing valve that surges passes through elder generation for three six logical proportional servo valves, the spool position for the proportional reversing valve that surges
Control valve control is led, the proportional reversing valve that surges there are six hydraulic fluid ports, is designated as P mouths, T mouths, A mouths, B mouths, C mouths and D mouths respectively, and A mouths meet R
Mouthful, B mouths connect S mouths, and T mouths connect the export and import of oil cylinder, C mouths and D mouths respectively as throttle passage：When the left position work of valve element,
Fluid flows to B mouths from P mouths, and T mouths are flowed to from A mouths；When valve element middle position works, P mouths, A mouths and the closing of B mouths, T mouths, C mouths and D mouths
Mutual conduction；When the right position work of valve element, fluid flows to A mouths from P mouths, and T mouths are flowed to from B mouths；
It is 3-position 4-way proportional servo valve that the pressure difference, which controls angular valve, and the spool position of pressure difference control angular valve passes through pressure
Two control port pressure differentials control of difference control angular valve, it is logical that pressure difference controls two control ports of angular valve to connect throttling respectively
The export and import on road, pressure difference control angular valve have four hydraulic fluid ports, are designated as I mouths, J mouths, K mouths and L mouths, I mouth connected tanks, J respectively
Mouth connects hydraulic power source, and K mouths connect the E mouths of overflow control angular valve, and L mouths connect the F mouths of overflow control angular valve：When the left position work of valve element
When, fluid flows to I mouths from L mouths, and K mouths are flowed to from J mouths；When valve element middle position works, I mouths, J mouths, K mouths and L mouths are mutually not turned on；
When the right position work of valve element, fluid flows to I mouths from K mouths, and L mouths are flowed to from J mouths；
It is 3-position 4-way proportional servo valve that the overflow, which controls angular valve, and the spool position of overflow control angular valve is by overflowing
The control port input pressure of flow control angular valve and overflow control corner valve spring control, the control oil of overflow control angular valve
Mouth connects the U mouths of inertia overflow selector valve, and overflow control angular valve has four hydraulic fluid ports, is designated as E mouths, F mouths, G mouths and H mouths, G mouths respectively
Connect two control ports of valve plate corner oil cylinder respectively with H mouths：When the left position work of valve element, fluid flows to G mouths from F mouths, from H
Mouth flows to E mouths；When valve element middle position works, E mouths, F mouths, G mouths and H mouths are mutually not turned on；When the work of valve element right position, fluid from
G mouths flow to E mouths, and H mouths are flowed to from F mouths；
The inertia overflow selector valve is two-position three-way valve, and the spool position of inertia overflow selector valve passes through pilot-actuated valve
With selection valve spring control, inertia overflow selector valve has three hydraulic fluid ports, is designated as U mouths, W mouths and V mouths respectively, and W mouths meet going out for shuttle valve
Hydraulic fluid port O, V mouth connected tank：When the left position work of valve element, fluid flows to V mouths from U mouths；When the work of valve element right position, fluid is from W mouths
Flow to U mouths；
Two oil inlets of the shuttle valve connect R mouths and S mouths respectively.
Preferably, the valve element of the proportional reversing valve that surges is by the valve spring centering that commutates, i.e., pilot-actuated valve is without output
During signal, the work of valve element middle position.
Preferably, the valve element of the pressure difference control angular valve is controlled by control valve spring and valve element both ends pressure difference, works as pressure difference
When controlling two control ports of angular valve without input, the valve element right position work of valve element under spring force of pressure difference control angular valve
Make；When pressure difference controls angular valve stable state, the two control port input pressures difference and valve element control area of pressure difference control angular valve
Product be equal to the pre-compression force of control valve spring, pressure difference is adjusted by the pre-compression force of adjustment control valve spring and controls angular valve
Two control port input pressures it is poor.
Preferably, the valve element of the overflow control angular valve controls corner valve spring and the pressure difference control of valve element both ends by overflow
System, when the control port of overflow control angular valve is without input, the valve element valve element under spring force of overflow control angular valve
Right position work；When overflow controls angular valve stable state, the control port input pressure and valve element control area of overflow control angular valve
Product be equal to overflow valve spring pre-compression force.
Preferably, the inertia overflow selector valve resets the right position work of back valve core by selector valve spring reset；Work as guide
When control valve has output signal, valve element transposition.
Beneficial effect：Existing proportional reversing valve, in control signal and the timing of valve core opening amount one, load pressure or system
When liquid supply pressure changes, the output flow fluctuation of valve is very big, and the maneuverability of equipment is poor, and system liquid supply pressure is more than load and pressed
During power, very big throttling is produced on valve, liquid energy loss is big, and fluid heating is serious.If it is configured with pressure to proportional reversing valve
Compensator, it can guarantee that valve port pressure difference is constant, when load pressure or system liquid supply pressure change, the output flow fluctuation very little of valve,
The maneuverability of equipment is good, but when system liquid supply pressure is more than load pressure, pressure compensator produces very big throttling, liquid energy loss
Greatly, fluid heating is also serious.Existing proportional reversing valve can not reclaim mechanical energy during negative load behavior, load input
Mechanical energy is totally converted for heat energy.
If only directly controlling load with present hydraulic transformer, operating personnel can only control the flow of hydraulic transformer
Disk pilot angle adjusts the liquid measure of output and loading speed, and system does not have restriction loss and heating, can reclaim negative load behavior yet
When mechanical energy and load inertia kinetic energy.But when load pressure or system liquid supply pressure change, hydraulic transformer output pressure
It will change, load acceleration or deceleration, in order to which proof load speed is constant, the required moment regulation hydraulic pressure transformation of operating personnel
The valve plate pilot angle of device eliminates the fluctuation of output flow, and the maneuverability of such equipment is very poor.
The pressure-transforming energy-saving four-way proportional flow commutator of the present invention is protected by adjusting the valve plate pilot angle of hydraulic transformer
It is constant the restriction pressure difference of proportional reversing valve is demonstrate,proved, in control signal and the timing of valve core opening amount one, load pressure or system supply
When hydraulic coupling changes, the output flow of valve does not fluctuate, and the maneuverability of equipment is good, and system liquid supply pressure is more than load pressure
When, pressure difference is dropped on hydraulic transformer, valve port chock pressure difference and liquid energy loss very little, fluid will not be caused seriously to generate heat.This
The inertia in mechanical energy and motor or oil cylinder braking process when hydraulic transformer can also reclaim negative load behavior in kind of commutator
Kinetic energy.
So the pressure-transforming energy-saving four-way proportional flow commutator of invention can realize ratio under conditions of valve port pressure difference very little
The mechanical energy of example speed regulating control, and can recovery inertia kinetic energy and load.Its control performance and energy-conservation are better than present ratio
Reversal valve and hydraulic transformer.
Brief description of the drawings
Fig. 1 is the structural representation of the pressure-transforming energy-saving four-way proportional flow commutator of the recyclable inertia kinetic energy of the present invention；
Fig. 2 is the functional symbol signal of the pressure-transforming energy-saving four-way proportional flow commutator of the recyclable inertia kinetic energy of the present invention
Figure.
Embodiment
The present invention is further described below in conjunction with the accompanying drawings.
It is as shown in Figure 1 a kind of pressure-transforming energy-saving four-way proportional flow commutator of recyclable inertia kinetic energy, including hydraulic pressure becomes
Depressor 1, valve plate corner oil cylinder 2, overflow controls angular valve 3, pressure difference control angular valve 4, check valve 5, surge proportional reversing valve
6th, inertia overflow selector valve 7 and shuttle valve 8, load as motor 9, two hydraulic fluid ports of motor 9 are designated as R mouths and S mouths respectively.
The hydraulic transformer 1 has three hydraulic fluid ports, is designated as P respectivelyAMouth, PBMouth and PTMouthful, PAMouth connects hydraulic power source 10, PBMouth connects
The P mouths of the oil-out of check valve 5 and the proportional reversing valve 6 that surges, PTMouth connected tank, the valve plate rotation angle mechanism of hydraulic transformer 1
Pass through two control port input pressures difference control of valve plate corner oil cylinder 2.
The proportional reversing valve 6 that surges passes through for three six logical proportional servo valves, the spool position for the proportional reversing valve 6 that surges
Pilot-actuated valve controls, and the proportional reversing valve 6 that surges has six hydraulic fluid ports, is designated as P mouths, T mouths, A mouths, B mouths, C mouths and D mouths, A mouths respectively
R mouths are connect, B mouths connect S mouths, and T mouths connect the export and import of oil cylinder, C mouths and D mouths respectively as throttle passage：When the left position work of valve element
When, fluid flows to B mouths from P mouths, and T mouths are flowed to from A mouths；When valve element middle position works, P mouths, A mouths and the closing of B mouths, T mouths, C mouths and D
Mouth mutual conduction；When the right position work of valve element, fluid flows to A mouths from P mouths, and T mouths are flowed to from B mouths.The proportional reversing valve 6 that surges
Valve element by the valve spring centering that commutates, i.e. pilot-actuated valve non-output signal when, valve element middle position work.
The pressure difference control angular valve 4 is 3-position 4-way proportional servo valve, and the spool position of pressure difference control angular valve 4 passes through
Two control port pressure differentials control of pressure difference control angular valve 4, two control ports of pressure difference control angular valve 4 connect section respectively
The export and import of logical circulation road, pressure difference control angular valve 4 have four hydraulic fluid ports, are designated as I mouths, J mouths, K mouths and L mouths respectively, I mouths connect oil
Case, J mouths connect hydraulic power source 10, and K mouths connect the E mouths of overflow control angular valve 3, and L mouths connect the F mouths of overflow control angular valve 3：When valve element is left
During the work of position, fluid flows to I mouths from L mouths, and K mouths are flowed to from J mouths；When valve element middle position works, I mouths, J mouths, K mouths and L mouths are mutual
It is not turned on；When the right position work of valve element, fluid flows to I mouths from K mouths, and L mouths are flowed to from J mouths.The valve of the pressure difference control angular valve 4
Core is controlled by control valve spring and valve element both ends pressure difference, when two control ports of pressure difference control angular valve 4 are without input, pressure difference
Control the valve element right position work of valve element under spring force of angular valve 4；When pressure difference controls 4 stable state of angular valve, pressure difference control turns
Two control port input pressures difference of angle valve 4 and the product of valve element control area are equal to the pre-compression force of control valve spring, lead to
Two control port input pressures for overregulating the pre-compression force regulation pressure difference control angular valve 4 of control valve spring are poor.
The overflow control angular valve 3 is 3-position 4-way proportional servo valve, and the spool position of overflow control angular valve 3 passes through
The control port input pressure of overflow control angular valve 3 and overflow control corner valve spring control, overflow control the control of angular valve 3
Liquefaction mouth connects the U mouths of inertia overflow selector valve 7, and overflow control angular valve 3 has four hydraulic fluid ports, is designated as E mouths, F mouths, G mouths and H respectively
Mouth, G mouths and H mouths connect two control ports of valve plate corner oil cylinder 2 respectively：When the left position work of valve element, fluid flows to from F mouths
G mouths, E mouths are flowed to from H mouths；When valve element middle position works, E mouths, F mouths, G mouths and H mouths are mutually not turned on；When the right position work of valve element
When, fluid flows to E mouths from G mouths, and H mouths are flowed to from F mouths.The valve element of the overflow control angular valve 3 controls angular valve bullet by overflow
Spring and the control of valve element both ends pressure difference, when the control port of overflow control angular valve 3 is without input, overflow controls the valve of angular valve 3
The core right position work of valve element under spring force；When overflow controls 3 stable state of angular valve, overflow controls the control port of angular valve 3
The product of input pressure and valve element control area is equal to the pre-compression force of overflow valve spring.
The inertia overflow selector valve 7 is two-position three-way valve, and the spool position of inertia overflow selector valve 7 passes through pilot control
Valve and selection valve spring control, inertia overflow selector valve 7 have three hydraulic fluid ports, are designated as U mouths, W mouths and V mouths respectively, and W mouths connect shuttle valve 8
Oil-out O, V mouth connected tank：When the left position work of valve element, fluid flows to V mouths from U mouths；When the work of valve element right position, fluid from
W mouths flow to U mouths.The inertia overflow selector valve 7 resets the right position work of back valve core by selector valve spring reset；When guide is controlled
When valve processed has output signal, valve element transposition.
Two oil inlets of the shuttle valve 8 connect R mouths and S mouths respectively.
In this case, the piston rod of valve plate corner oil cylinder 2 is connected with the valve plate rotation angle mechanism of hydraulic transformer 1, that is, matches somebody with somebody
Flow table corner is driven by valve plate corner oil cylinder 2, and the control signal of overflow control angular valve 3 is derived from the U of inertia overflow selector valve 7
Mouthful, the G mouths and H mouths of overflow control angular valve 3 connect two control ports of valve plate corner oil cylinder 2, overflow control angular valve 3
E mouths and F mouths connect the K mouths and L mouths of pressure difference control angular valve 4, and the J mouths of pressure difference control angular valve 4 connect hydraulic power source 10, I mouth connected tanks,
Two control ports of the pressure difference control valve element of angular valve 4 are connected with the C mouths and D mouths of proportional reversing valve 6 respectively.
If the left end of proportional reversing valve 6 has control signal, valve element moves to right, and amount of opening is proportional to control signal size, i.e.,
The left position work of valve, the fluid of the B mouths output of proportional reversing valve 6 enter the band dynamic load of the drive motor of motor 9 and rotated, and motor 9 is fuel-displaced
A mouths through proportional reversing valve 6 are to T mouth oil return boxes.Now inertia overflow selector valve 7 changes to left position in the presence of control signal,
The oil-out O for connecing shuttle valve 8 is blocked.Overflow control angular valve 3 is in right position, pressure difference control angular valve 4 under action of reset spring
Two actuator ports connect two hydraulic fluid ports of valve plate corner oil cylinder 2, the pressure difference control valve element of angular valve 4 across overflow control angular valve 3
The inlet and outlet pressure of measurement scale reversal valve 6 is poor, pressure differential and the sum of products pressure difference control corner of valve element control area in stable state
The pre-compression force of the spring of valve 4 is equal, i.e. the pre-compression force setting inlet and outlet pressure of proportional reversing valve 6 of spring is poor, is commutated in ratio
When the control signal of valve 6 and constant valve core opening amount, the flow that proportional reversing valve 6 exports is constant, and the speed of controlled motor 9 is constant,
The rotating speed of motor 9 does not change with load change and the change of system voltage supply power, and the maneuverability of equipment is good.
Load pressure increases performance analysis：If the constant spool displacement of the control signal of proportional reversing valve 6 and valve amount of opening are not
Become, and load pressure increases suddenly, the pressure difference of the P B mouths of proportional reversing valve 6 reduces, and the flow that proportional reversing valve 6 exports reduces,
The rotating speed of motor 9 diminishes.Pressure difference control angular valve 4 measurement scale reversal valve, 6 inlet and outlet pressures are poor, at this moment pressure difference control angular valve
The active force of 4 valve element left ends is more than the active force of right-hand member, and valve element moves to right, and 4 left position of pressure difference control angular valve is devoted oneself to work, and system supplies
Oil enters the left chamber of valve plate corner oil cylinder 2, the piston of corner oil cylinder 2 is moved right, and reduces the valve plate of hydraulic transformer 1
Pilot angle, also reduce the transformation ratio of pressure transformer 1, make the P of hydraulic transformer 1BMouth (throttling of proportional reversing valve 6 import)
Pressure rise, the inlet and outlet pressure difference of proportional reversing valve 6 return to the rotating speed of original value, the output flow of proportional reversing valve 6 and motor 9
Original size is returned to, the pressure difference control valve element of angular valve 4 returns to middle position, and the pilot angle of the valve plate of hydraulic transformer 1 is no longer
Change, at this moment the rotating speed of motor 9 caused by load pressure increases, which reduces, is restored.
Load pressure reduces, liquid supply pressure increase or reduction performance analysis are similar to load pressure increase performance analysis, no
Tire out again and state.
The right-hand member of proportional reversing valve 6 has control signal, and valve element moves to left, and amount of opening is proportional to control signal size, i.e., valve is right
Position access loop works, the fluid drive motor 9 that proportional reversing valve 6 exports invert.Load or liquid supply pressure change are to 9 turns of motor
Speed can also produce disturbance, and the analysis of rotating speed recovery process has the analysis process of control signal similar to the left end of proportional reversing valve 6.
In this process if pressure needed for motor 9 is less than system liquid supply pressure, hydraulic transformer 1 pressure step-down,
There is no the difference pressuring loss of restriction loss, the only restriction of passing ratio reversal valve 6, this pressure difference is to control stability of flow required
, but this pressure difference very little only has 0.5-1MPa, and this pressure loss is little for high-pressure system.
When proportional reversing valve 6 does not have control signal suddenly in the rotation process of motor 9,6 liang of actuator port A of proportional reversing valve
Shut with B, because the load inertia of motor 9 is big, motor 9 is rotated further, and the great rise of pressure of the oil return opening of motor 9, is now used to
The left end blackout of property overflow selector valve 7, returns to right position, the fluid of the oil return opening of motor 9 is through shuttle in the presence of right-hand member spring force
Valve 8, inertia overflow selector valve 7, check valve 5 enter the P of hydraulic transformer 1BMouthful, act also on the overflow control valve element of angular valve 3
Left end, overflow control angular valve 3 left position work, the left chamber of valve plate corner oil cylinder 2 enters high pressure, make the piston of corner oil cylinder 2 to
Move right, reduce the pilot angle of the valve plate of hydraulic transformer 1, also reduce the transformation ratio of pressure transformer 1, make hydraulic pressure transformation
The P of device 1BMouthful pressure reaches the spring set pressure of the overflow control valve element right-hand member of angular valve 3, and hydraulic transformer 1 is from PAMouth discharge is high
Hydraulic fluid imports system, and the rotational kinetic energy that motor 9 loads without throttling is thus recovered as the hydraulic energy that is used for system, avoided
Fluid heating and temperature rise.
Analyzed more than, the pressure-transforming energy-saving four-way proportional flow commutator of invention can realize the ratio stream of load
Amount control, and the very little that throttles, moreover it is possible to the inertia kinetic energy for reclaiming load is converted into the hydraulic energy of system, has reached the purpose of energy-conservation,
Flow diverter is by pressure-transforming energy-saving, has four liquid in-out main channels, output or input flow rate to be controlled by the ratio of signal,
So it is named as the pressure-transforming energy-saving four-way proportional flow commutator of recyclable inertia kinetic energy.
In order to simplify the technique of painting of the pressure-transforming energy-saving four-way proportional flow commutator in hydraulic system, this of the present invention is defined
The functional symbol of commutator is shown in Fig. 2, and 2 (a) is entrance throttle governing circuit, and 2 (b) is meter out speed governing, meter out speed governing
Controlled available for the flow for bearing load behavior, can also reclaim the mechanical energy of load.The rectangular boxes of outside represent ratio and changed
To valve, the ellipse of two semicircles and upper and lower line composition in rectangular boxes represents hydraulic transformer, rectangular boxes or so
Dotted line represent proportional flow control signal input, there be two reversal valve centralizing springs left and right.A and B represent commutator
Two actuator ports, connect the oil inlet and oil return mouth of load (motor or oil cylinder), P mouth welding system feed flows, and T represents what commutator was connected with fuel tank
Interface, the interface that the inertia kinetic energy reclaimed is converted into hydraulic energy can be represented from fuel tank imbibition or discharge opeing, O mouths by this mouth.PA
Line between PB and section liquid symbol represent that commutator is the line and black three between OP by valve port flow restriction control flow
Angle represents the passage of the hydraulic energy of recovery inertia kinetic energy conversion, and the valve plate control of hydraulic transformer is represented with the arrow that line intersects
Angle processed is adjustable.
Described above is only the preferred embodiment of the present invention, it should be pointed out that：For the ordinary skill people of the art
For member, under the premise without departing from the principles of the invention, some improvements and modifications can also be made, these improvements and modifications also should
It is considered as protection scope of the present invention.
Claims (5)
- A kind of 1. pressure-transforming energy-saving four-way proportional flow commutator of recyclable inertia kinetic energy, it is characterised in that：Including hydraulic pressure transformation Device (1), valve plate corner oil cylinder (2), overflow control angular valve (3), pressure difference control angular valve (4), check valve (5), surge ratio Two hydraulic fluid ports of load are designated as R mouths and S mouths by example reversal valve (6), inertia overflow selector valve (7) and shuttle valve (8) respectively；The hydraulic transformer (1) has three hydraulic fluid ports, is designated as P respectivelyAMouth, PBMouth and PTMouthful, PAMouth meets hydraulic power source (10), PBMouth connects The P mouths of the oil-out of check valve (5) and the proportional reversing valve (6) that surges, PTMouth connected tank, the valve plate of hydraulic transformer (1) turn Two control port input pressures difference control that angle mechanism passes through valve plate corner oil cylinder (2)；The proportional reversing valve that surges (6) is three six logical proportional servo valves, and the spool position of the proportional reversing valve that surges (6) passes through Pilot-actuated valve controls, and the proportional reversing valve that surges (6) has six hydraulic fluid ports, is designated as P mouths, T mouths, A mouths, B mouths, C mouths and D mouths, A respectively Mouth connects R mouths, and B mouths connect S mouths, and T mouths connect the export and import of oil cylinder, C mouths and D mouths respectively as throttle passage：When the left position work of valve element When making, fluid flows to B mouths from P mouths, and T mouths are flowed to from A mouths；When valve element middle position works, P mouths, A mouths and the closing of B mouths, T mouths, C mouths With D mouth mutual conductions；When the right position work of valve element, fluid flows to A mouths from P mouths, and T mouths are flowed to from B mouths；The pressure difference control angular valve (4) is 3-position 4-way proportional servo valve, and the spool position of pressure difference control angular valve (4) passes through Two control port pressure differentials control of pressure difference control angular valve (4), two control ports difference of pressure difference control angular valve (4) The export and import of throttle passage is connect, pressure difference control angular valve (4) there are four hydraulic fluid ports, is designated as I mouths, J mouths, K mouths and L mouths, I respectively Mouth connected tank, J mouths connect hydraulic power source (10), and K mouths connect the E mouths of overflow control angular valve (3), and L mouths connect overflow control angular valve (3) F mouths：When the left position work of valve element, fluid flows to I mouths from L mouths, and K mouths are flowed to from J mouths；When valve element middle position works, I mouths, J mouths, K Mouth and L mouths are mutually not turned on；When the right position work of valve element, fluid flows to I mouths from K mouths, and L mouths are flowed to from J mouths；The overflow control angular valve (3) is 3-position 4-way proportional servo valve, and the spool position of overflow control angular valve (3) passes through The control port input pressure of overflow control angular valve (3) and overflow control corner valve spring control, overflow control angular valve (3) Control port connect the U mouths of inertia overflow selector valve (7), overflow control angular valve (3) has four hydraulic fluid ports, is designated as E mouths, F respectively Mouth, G mouths and H mouths, G mouths and H mouths connect two control ports of valve plate corner oil cylinder (2) respectively：When the left position work of valve element, oil Liquid flows to G mouths from F mouths, and E mouths are flowed to from H mouths；When valve element middle position works, E mouths, F mouths, G mouths and H mouths are mutually not turned on；Work as valve When the right position of core works, fluid flows to E mouths from G mouths, and H mouths are flowed to from F mouths；The inertia overflow selector valve (7) is two-position three-way valve, and the spool position of inertia overflow selector valve (7) passes through pilot control Valve and selection valve spring control, inertia overflow selector valve (7) have three hydraulic fluid ports, are designated as U mouths, W mouths and V mouths respectively, and W mouths connect shuttle valve (8) oil-out O, V mouth connected tank：When the left position work of valve element, fluid flows to V mouths from U mouths；When the right position work of valve element, oil Liquid flows to U mouths from W mouths；Two oil inlets of the shuttle valve (8) connect R mouths and S mouths respectively.
- 2. the pressure-transforming energy-saving four-way proportional flow commutator of recyclable inertia kinetic energy according to claim 1, its feature exist In：When the valve element of the proportional reversing valve that surges (6) is by the valve spring centering that commutates, i.e. pilot-actuated valve non-output signal, valve Core middle position works.
- 3. the pressure-transforming energy-saving four-way proportional flow commutator of recyclable inertia kinetic energy according to claim 1, its feature exist In：The valve element of the pressure difference control angular valve (4) is controlled by control valve spring and valve element both ends pressure difference, when pressure difference controls angular valve (4) when two control ports are without input, the valve element right position work of valve element under spring force of pressure difference control angular valve (4)； When pressure difference controls angular valve (4) stable state, two control port input pressures difference and the valve element chain of command of pressure difference control angular valve (4) Long-pending product is equal to the pre-compression force of control valve spring, and adjusting pressure difference by the pre-compression force of adjustment control valve spring controls corner Two control port input pressures of valve (4) are poor.
- 4. the pressure-transforming energy-saving four-way proportional flow commutator of recyclable inertia kinetic energy according to claim 1, its feature exist In：The spool position of the overflow control angular valve (3) controls the control port input pressure of angular valve (3) by overflow and overflow Flow control corner valve spring controls, when the control port of overflow control angular valve (3) is without input, overflow control angular valve (3) Valve element valve element right position work under spring force；When overflow controls angular valve (3) stable state, overflow control angular valve (3) The product of control port input pressure and valve element control area is equal to the pre-compression force of overflow valve spring.
- 5. the pressure-transforming energy-saving four-way proportional flow commutator of recyclable inertia kinetic energy according to claim 1, its feature exist In：The inertia overflow selector valve (7) resets the right position work of back valve core by selector valve spring reset；When pilot-actuated valve has During output signal, valve element transposition.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710223227.6A CN106870473B (en) | 2017-04-07 | 2017-04-07 | A kind of pressure-transforming energy-saving four-way proportional flow commutator of recyclable inertia kinetic energy |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710223227.6A CN106870473B (en) | 2017-04-07 | 2017-04-07 | A kind of pressure-transforming energy-saving four-way proportional flow commutator of recyclable inertia kinetic energy |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN106870473A CN106870473A (en) | 2017-06-20 |
| CN106870473B true CN106870473B (en) | 2018-04-03 |
Family
ID=59160910
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710223227.6A Expired - Fee Related CN106870473B (en) | 2017-04-07 | 2017-04-07 | A kind of pressure-transforming energy-saving four-way proportional flow commutator of recyclable inertia kinetic energy |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN106870473B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116733794B (en) * | 2023-06-09 | 2024-06-14 | 江苏汇智高端工程机械创新中心有限公司 | Load self-adaptive rotary buffer valve and hydraulic system |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104235003B (en) * | 2013-12-13 | 2017-03-15 | 江苏恒立液压科技有限公司 | Plunger pump control valve and its control method |
| JP2015190518A (en) * | 2014-03-27 | 2015-11-02 | 日立建機株式会社 | Constant pressure control hydraulic driving device |
| CN104179734B (en) * | 2014-08-27 | 2016-06-29 | 浙江德泰机电工程有限公司 | A kind of constant-pressure control device for hydraulic pump and control method |
| CN104930006B (en) * | 2015-06-12 | 2017-01-11 | 力源液压（苏州）有限公司 | Variable displacement control device of hydraulic pump |
| CN105156391B (en) * | 2015-09-17 | 2017-11-14 | 徐州工业职业技术学院 | A kind of composite variable pump and the hydraulic control system with composite variable pump |
-
2017
- 2017-04-07 CN CN201710223227.6A patent/CN106870473B/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| CN106870473A (en) | 2017-06-20 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN100593646C (en) | Unpowered oil supplied direct drive displacement control electrohydraulic servo- closed type oil source system | |
| CN102588358B (en) | High-performance energy saving type electro-hydraulic servo control oil line | |
| CN101709725B (en) | Downhole anti-explosion hoisting machine hydraulic control system adopting multi-pump combination technique | |
| CN102030266B (en) | Crane and hydraulic control system thereof | |
| CN105697436B (en) | The small volume cell pressure control hydraulic system that a kind of flow is preferentially supplied | |
| CN103790874A (en) | Valveless hydraulic servo system and control method thereof | |
| CN106032261A (en) | Tension control device of high-power hydraulic winch | |
| CN106907364A (en) | A kind of closed type hydraulic system of development machine | |
| CN107816465A (en) | Hydraulic means is pushed up with push pipe owner in a kind of colliery | |
| CN104632794A (en) | Electro-hydraulic servo system of direct drive type hydraulic hoist | |
| CN203516249U (en) | Load-sensitive feedback control system for top drive drilling machine hydraulic pump station | |
| CN106884824B (en) | A kind of pressure-transforming energy-saving threeway proportional flow commutator | |
| CN107461516A (en) | A kind of differential type electric-hydraulic proportion uniform-pressure-drop valve | |
| CN105402182B (en) | Load sensing multiple directional control valve and loader hydraulic control system | |
| CN109654079A (en) | The outlet throttling load port separate control valves that full switch valve group is closed | |
| CN101875301A (en) | Crane and controllable radiation system thereof | |
| CN106870473B (en) | A kind of pressure-transforming energy-saving four-way proportional flow commutator of recyclable inertia kinetic energy | |
| CN201405725Y (en) | Crane and controllable cooling system thereof | |
| CN103738396A (en) | Constant flow steering system and engineering machinery | |
| CN207660915U (en) | A kind of coal mine push pipe owner top hydraulic device | |
| CN203717495U (en) | Rotating and pushing self-adaptation hydraulic loop for of hydraulic drill carriage drill rod mounting and dismounting | |
| CN109210024A (en) | Minus flow hydraulic control oil circuit and hydraulic system and excavator | |
| CN105545839A (en) | Oil cylinder reversing and volume speed adjusting hydraulic system | |
| CN106168234B (en) | A kind of constant displacement pump variable delivery hydraulic system | |
| CN208651322U (en) | A kind of dam paver screw material-distributing closed type hydraulic system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20180403 |