CN108980130A - Differential pressure regulating valve unit, hydraulic control system and engineering machinery - Google Patents
Differential pressure regulating valve unit, hydraulic control system and engineering machinery Download PDFInfo
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- CN108980130A CN108980130A CN201810886399.6A CN201810886399A CN108980130A CN 108980130 A CN108980130 A CN 108980130A CN 201810886399 A CN201810886399 A CN 201810886399A CN 108980130 A CN108980130 A CN 108980130A
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- 230000001105 regulatory effect Effects 0.000 title claims abstract description 17
- 239000010720 hydraulic oil Substances 0.000 claims abstract description 17
- 230000001276 controlling effect Effects 0.000 claims abstract description 7
- 230000008450 motivation Effects 0.000 claims description 3
- 230000000694 effects Effects 0.000 description 6
- 230000009466 transformation Effects 0.000 description 5
- 238000000034 method Methods 0.000 description 4
- 239000003921 oil Substances 0.000 description 4
- 239000012530 fluid Substances 0.000 description 3
- 230000008901 benefit Effects 0.000 description 2
- 238000006243 chemical reaction Methods 0.000 description 2
- 230000005611 electricity Effects 0.000 description 1
- 210000000635 valve cell Anatomy 0.000 description 1
Classifications
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- 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
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
- B66C13/00—Other constructional features or details
- B66C13/18—Control systems or devices
- B66C13/20—Control systems or devices for non-electric drives
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- General Engineering & Computer Science (AREA)
- Automation & Control Theory (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention relates to the technical field of hydraulic pressure, and discloses a differential pressure adjusting unit, a hydraulic control system and engineering machinery. The hydraulic control system includes: the hydraulic pump is used for supplying hydraulic oil to the actuating element under the driving of the engine; a main valve for controlling an actual output flow rate of the hydraulic oil from the hydraulic pump to the actuator; a differential pressure regulating valve comprising: the variable valve is provided with a constant pressure element at a first end; the variable valve is arranged at the second end of the variable valve and used for adjusting the pressure difference at two ends of the main valve under different rotating speeds of the engine so as to enable the maximum output flow of the main valve in the output flow range adjusted by the handle to be equal to the output flow of the hydraulic pump; and the controller is connected with the engine and the variable pressure valve and used for receiving the rotating speed of the engine and controlling the output pressure of the variable pressure valve according to the rotating speed of the engine. The invention can give consideration to high-speed operation and good jogging performance of the whole machine.
Description
Technical field
The present invention relates to technical field of hydraulic pressure, and in particular, to a kind of differential regulating valuve unit, hydraulic control system and work
Journey is mechanical.
Background technique
Variable pump load sensitive system has preferable energy saving and stability, has obtained generally answering on autocrane
With.System pressure difference Δ P is set as higher pressure by the method that variable pump load sensitive system generallys use constant pressure difference control at present
Power, it is ensured that the pressure oil of engine peak speed variations per hour pump output all passes through main valve；But it is (or low in engine idling
Revolving speed) when, due to the pressure differential deltap P higher of setting, when handle is less than total travel, just had reached by the actual flow of main valve idle
The flow of fast (or slow-speed of revolution) variable pump output.In this case, continue to pull handle, although the pressure of handle control has
Variation, but (being still the flow of variable pump output) is not changed by the flow of main valve, therefore make the reality of handle that can manipulate model
It encloses and narrows, that is to say, that there are larger idle strokes for handle, greatly influence the speed regulation of whole system, cause whole system
Handling is deteriorated.
Summary of the invention
The object of the present invention is to provide a kind of differential regulating valuve unit, hydraulic control system and it is provided with the hydraulic control
The engineering machinery of system can ensure that under any revolving speed of engine, in the output flow range that main valve is adjusted by handle
Maximum output flow is consistent with the output flow of hydraulic pump, to avoid handle, there are idle strokes, combines the height of complete machine
Speed operating and good fretting performance.
To achieve the goals above, the present invention provides a kind of hydraulic control system, which includes: hydraulic
Pump, for providing hydraulic oil to executive component under the driving of engine；Main valve is held for controlling from the hydraulic pump to described
The reality output flow of the hydraulic oil of units；Pressure-difference valve, the pressure-difference valve include: variable flow valve, and the of the variable flow valve
One end is provided with level pressure element；And variable pressure valve, the variable pressure valve are set to the second end of the variable flow valve, for starting described
Under the different revolving speed of machine, the pressure difference between the main valve both ends is adjusted, so that the output flow range that the main valve is adjusted by handle
Interior maximum output flow is equal with the output flow of the hydraulic pump；And controller, with the engine and the transformation
Valve is connected, and for receiving the revolving speed of the engine, and controls according to the revolving speed of the engine output pressure of the variable pressure valve
Power.
Optionally, the level pressure element is valve core spring.
Optionally, the variable pressure valve is electric proportional pressure-reducing valve.
Optionally, the pressure differential deltap P=F between the main valve both endsBullet/S-Pf, wherein FBulletFor the default of the valve core spring
Spring force, S are the area of the first end of the variable flow valve, PfFor the pressure of the electric proportional pressure-reducing valve output.
Optionally, the output pressure P of the variable pressure valvefRelationship with the revolving speed v of the engine includes: to start when described
When the revolving speed v of machine increases, the output pressure P of the variable pressure valvefConstantly reduce.
Optionally, the output pressure P of the variable pressure valvefRelationship with the revolving speed v of the engine includes:Wherein vmaxFor the maximum (top) speed of the engine, P0For the output level pressure of the level pressure element.
Optionally, the output flow of the main valveWherein K is discharge coefficient, and A is the main valve
Area of passage, pressure difference of the Δ P between the main valve both ends.
Correspondingly, the differential regulating valuve unit includes: that pressure difference is adjusted the present invention also provides a kind of differential regulating valuve unit
Valve, the pressure-difference valve include: variable flow valve, and the first end of the variable flow valve is provided with level pressure element；And variable pressure valve, the variable pressure valve
It is set to the second end and controller of the variable flow valve, which is connected with engine and the variable pressure valve, wherein institute
Pressure-difference valve is stated under the different revolving speed of the engine, adjusts the pressure difference between main valve both ends so that the main valve by
The maximum output flow in output flow range that handle is adjusted is equal with the output flow of hydraulic pump；The controller is for connecing
The revolving speed of the engine is received, and controls the output pressure of the variable pressure valve, the hydraulic pump according to the revolving speed of the engine
Hydraulic oil is provided to executive component under the driving of the engine；The main valve is held for controlling from the hydraulic pump to described
The reality output flow of the hydraulic oil of units.
Optionally, the level pressure element is valve core spring.
Optionally, the variable pressure valve is electric proportional pressure-reducing valve.
Optionally, the output pressure P of the variable pressure valvefRelationship with the revolving speed v of the engine includes: to start when described
When the revolving speed v of machine increases, the output pressure P of the variable pressure valvefConstantly reduce.
Optionally, the output pressure P of the variable pressure valvefRelationship with the revolving speed v of the engine includes:Wherein vmaxFor the maximum (top) speed of the engine, P0For the output level pressure of the level pressure element.
Correspondingly, the engineering machinery is provided with above-mentioned hydraulic control system the present invention also provides a kind of engineering machinery.
Optionally, which is crane.
Through the above technical solutions, the present invention creatively passes through the level pressure element and transformation that the both ends of variable flow valve are arranged in
Pressure difference between valve regulation main valve both ends, wherein the output pressure of variable pressure valve is controlled by controller according to the revolving speed of engine,
So that maximum output flow in the output flow range that main valve is adjusted by handle under the different rotating speeds of engine with it is hydraulic
The output flow of pump is equal, and thus no matter engine is that high speed is in idling, in whole strokes of the handle of main valve
The flow of main valve adjusts that gain is small, and fine motion is good when the interior adjusting, i.e. idling that can realize flow, the flow of main valve when high speed
It is big to adjust gain, meets the requirement of big flow high speed.
Other features and advantages of the present invention will the following detailed description will be given in the detailed implementation section.
Detailed description of the invention
The drawings are intended to provide a further understanding of the invention, and constitutes part of specification, with following tool
Body embodiment is used to explain the present invention together, but is not construed as limiting the invention.In the accompanying drawings:
Fig. 1 is the structure chart of hydraulic system in the prior art；
Fig. 2 is hydraulic system in the prior art in engine peak speed variations per hour pump output flow, main valve through-current capacity
The theory relation curve formed with handle；
Fig. 3 is hydraulic system in the prior art in engine idling variations per hour pump output flow, main valve through-current capacity and hand
Handle type at theory relation curve；
Fig. 4 is hydraulic system in the prior art in engine different rotating speeds variations per hour pump output flow, main valve through-current capacity
The theory relation curve formed with handle；
Fig. 5 is the structure chart for the hydraulic control system that one embodiment of the present invention provides；
Fig. 6 is the structure chart for the hydraulic system that one embodiment of the present invention provides；
Fig. 7 is that the hydraulic system that one embodiment of the present invention provides pumps output stream in engine peak speed variations per hour
The theory relation curve that amount, main valve through-current capacity and handle are formed；
Fig. 8 is the hydraulic system of one embodiment of the present invention offer in engine idling variations per hour pump output flow, master
The theory relation curve that valve through-current capacity and handle are formed；
Fig. 9 is hydraulic system in the prior art in engine different rotating speeds variations per hour pump output flow, main valve through-current capacity
The theory relation curve formed with handle；And
Figure 10 is the structure chart for the hydraulic regulation unit that one embodiment of the present invention provides.
Description of symbols
10 hydraulic pump, 11 variable flow valve
12 main valve, 110 valve core spring
50 hydraulic pump, 51 main valve
52 pressure-difference valve, 53 controller
520 variable flow valve, 521 level pressure element
522 variable pressure valve, 60 hydraulic pump
61 main valve, 62 variable flow valve
63 controller, 64 engine
The electric proportional pressure-reducing valve of 620 valve core spring 621
Specific embodiment
Below in conjunction with attached drawing, detailed description of the preferred embodiments.It should be understood that this place is retouched
The specific embodiment stated is merely to illustrate and explain the present invention, and is not intended to restrict the invention.
Fig. 1 is the structure chart of hydraulic system in the prior art.The hydraulic system specifically includes that hydraulic pump 10, variable flow valve
11 and main valve 12 etc..Wherein, outlet (pressure herein is P) phase of the left end of the variable flow valve 11 and the hydraulic pump 10
Even, (its pre-set springs power is F for right end and valve core spring 110Bullet) and main valve 12 load feedback hydraulic fluid port LS (pressure herein,
I.e. load pressure is PLS) be connected.The working principle of the hydraulic pump 10 is as follows: the output flow Q of hydraulic pump 10 passes through main valve section
Head piece introduces executive component (oil cylinder or motor), the pressure differential deltap P=P-P between 12 both ends of main valveLS, the output pressure of hydraulic pump 10
P acts on the left end of variable flow valve (or LS valve) 11, load pressure PLSWith pre-set springs power FBulletCollective effect is on the right side of variable flow valve 11
End；Pass through the flow (i.e. main valve through-current capacity) of main valveWherein K is discharge coefficient (it is definite value), A
For the area of passage (handle travel is directly proportional to main valve choke diameter) of the main valve 12, Δ P be 12 both ends of main valve it
Between pressure difference.For the main valve for having designed completion, the maximum slotted density A of main valvemaxFor definite value, therefore the maximum of main valve is defeated
Outflow (i.e. maximum through-current capacity)It but depends on the pressure differential deltap P between main valve both ends.Root
According to the formula of above-mentioned main valve through-current capacity it is found that working as Δ P < FBulletWhen/S, it is through-flow to show that the output flow of hydraulic pump is less than main valve maximum
Amount；As Δ P=FBullet/ S shows that the output flow of hydraulic pump is more than or equal to main valve maximum through-current capacity, and wherein S is the variable
The area of 11 right end of valve.
When carrying out matching primitives to main valve and hydraulic pump, it is necessary to assure through-flow energy of the main valve in engine peak speed
Power, that is to say, that in the case where engine peak speed, the maximum through-current capacity of main valve is equal to the output flow of hydraulic pump.?
In the case where engine peak speed, the pre-set springs power and the main valve 12 of the valve core spring 110 of 11 right end of variable flow valve
Load feedback hydraulic fluid port LS pressure collective effect and the pressure phase of the outlet of the hydraulic pump 10 of 11 left end of variable flow valve
Balance, i.e. FBullet+PLS× S1=P × S2, wherein S1, S2 are respectively the area of 11 right end of variable flow valve, left end, as shown in Figure 1.
In general, because of S1=S2=S, therefore P-PLS=FBullet/S.After the handle of main valve is moved to range, 12 through-current capacity of main valveAt this point, the pressure differential deltap P=P-P between 12 both ends of main valveLS=FBullet/ S (Δ P and FBulletAt
Direct ratio), that is to say, that the hydraulic oil of hydraulic pump output all passes through main valve introducing executive component and (such case is known as main valve
Matched with hydraulic pump, i.e. the maximum through-current capacity of output flow=main valve of hydraulic pump), therefore the flow exported by the main valve 12
Q can be by pre-set springs power FBulletTo adjust.To sum up, institute is controlled by the pre-set springs power of the valve core spring 110 of the variable flow valve 11
The pressure difference at 12 both ends of main valve is stated, introduces executive component through the restriction of the main valve to control the output flow of the hydraulic pump 10
(oil cylinder or motor).In the case where engine peak speed, the output flow of hydraulic pump is Qmax, main valve through-current capacity is with handle
The change curve of stroke is shown in Fig. 2.When handle reaches range (i.e. full stroke) C, main valve maximum through-current capacity also reaches
Qmax。
But in the case where engine idling (or low speed), due to being limited to the revolving speed of engine, the output stream of hydraulic pump
Measure Qm'axFar smaller than engine peak speed when output flow Qmax(or main valve maximum through-current capacity), at this time between main valve both ends
Pressure differential deltap P' < FBullet/S.After moving the handle into range, the practical through-current capacity of main valve is
In the case where engine idling, the output flow of hydraulic pump is Q'max, main valve through-current capacity with handle travel change curve exhibition
Show in Fig. 3.When handle travel is A, the output flow of hydraulic pump arrived Q'max, continue to increase with handle travel, main valve is logical
Flow can continue to increase, but the output flow of hydraulic pump has reached the maximum stream flow Q' under the revolving speedmax, so while handle row
Journey continues to increase, but the practical through-current capacity of main valve does not increase further, shows as handle idle stroke.In engine different rotating speeds
When, can handle idle stroke the phenomenon that, but with the increase of revolving speed, the ratio that handle idle stroke accounts for entire stroke is smaller and smaller,
When reaching maximum speed, the phenomenon that handle idle stroke, disappears, as shown in Figure 4.
When in the prior art in engine idling aiming at the problem that existing handle idle stroke, the present invention is in constant pressure difference control
On the basis of device, a kind of device that itself output pressure can be controlled according to the revolving speed of engine, i.e. variable pressure valve are added, so that
In engine different rotating speeds and only in handle full stroke, the maximum output flow of main valve is equal with the output flow of hydraulic pump, from
And avoid the appearance of handle idle stroke phenomenon.
As shown in figure 5, the structure chart for the hydraulic control system that one embodiment of the present invention provides.The hydraulic control system
System can include: hydraulic pump 50, for providing hydraulic oil to executive component under the driving of engine；Main valve 51, for control from
The hydraulic pump to the executive component hydraulic oil reality output flow；Pressure-difference valve 52, the pressure-difference valve 52 packet
Include: variable flow valve 520, the first end of the variable flow valve 520 are provided with level pressure element 521；And variable pressure valve 522, the variable pressure valve 522 are set
It is placed in the second end of the variable flow valve 520, for the handle full stroke in the different revolving speed of the engine and the main valve
In the case of, the pressure difference between 51 both ends of main valve is adjusted, so that the maximum output flow of the main valve 51 and the hydraulic pump 50
Output flow it is equal；And controller 53, it is connected with the engine and the variable pressure valve 522, for receiving described start
The revolving speed of machine, and control according to the revolving speed of the engine output pressure of the variable pressure valve 522.The present invention is being become by setting
The pressure difference between the level pressure element and transformation valve regulation main valve both ends at the both ends of valve is measured, wherein the output pressure of variable pressure valve passes through control
Device processed is controlled according to the revolving speed of engine, so that the output flow model that main valve is adjusted by handle under the different rotating speeds of engine
Maximum output flow in enclosing is equal with the output flow of hydraulic pump, and thus no matter engine is to be in height in idling
Speed, the flow adjusting gain of main valve is small when can realize the adjusting, i.e. idling of flow in whole strokes of the handle of main valve,
Fine motion is good, and it is big to adjust gain for the flow of main valve when high speed, meets the requirement of big flow high speed.
Wherein, the level pressure element can be valve core spring；And the variable pressure valve can be electric proportional pressure-reducing valve,.Below with
Variable pressure valve described in valve core spring 620 and electric proportional pressure-reducing valve 621 is respectively as can be to explain for level pressure element, variable pressure valve
The entire control process of bright hydraulic control system provided by the invention, as shown in Figure 6.The pre-set springs power F of valve core spring 620Bullet
With the pressure P of the load feedback hydraulic fluid port LS of the main valve 61LSRight end of the collective effect in the variable flow valve 62, the hydraulic pump 60
Outlet pressure P and the pressure P that exports of the electric proportional pressure-reducing valve 621fCollective effect is in the left end of the variable flow valve 62.When
When the pressure at 62 both ends of variable flow valve balances each other, i.e. FBullet+PLS× S1=P × S2+Pf× S2, wherein S1, S2 are respectively described
62 right end of variable flow valve, left end area.Usual S1=S2=S, therefore P-PLS=FBullet/ S-Pf。
When carrying out matching primitives to main valve 61 and hydraulic pump 60, it is necessary to assure main valve 61 is in 64 maximum speed of engine
Through-current capability, that is to say, that in the case where 64 maximum speed of engine, the maximum through-current capacity of main valve is equal to the defeated of hydraulic pump
Outflow.For the purpose of the present invention, i.e. any revolving speed of engine 64 and in the case where only reaching full stroke, the maximum of main valve
Through-current capacity is equal with the output flow of hydraulic pump, then needs to ensure that following formula is set up: Δ P=P-PLS=FBullet/ S-Pf, and electric ratio
The pressure P that pressure reducing valve 621 exportsfIt needs to be controlled by controller 63 according to the revolving speed of engine, specific control mode is as follows: hair
Motivation revolving speed is higher, controls the pressure P that electric proportional pressure-reducing valve 621 exportsfIt is smaller.Specifically, in 64 most high speed of engine,
The pressure P that electric proportional pressure-reducing valve 621 can be exportedfIt is set as 0, that is, acts on the pressure F of 62 right end of variable flow valveBullet/ S only by
Pre-set springs power provides；And in engine idling, the pressure P that electric proportional pressure-reducing valve 621 can be exportedfIt is set as maximum value
Pfmax, and the maximum value is related to the revolving speed of engine 64 at this time, at this point, act on the pressure of 62 right end of variable flow valve by
The maximum pressure P that pre-set springs power and electric proportional pressure-reducing valve 621 exportfmaxIt is common to provide, i.e. FBullet/ S-Pfmax.In engine idling
In the case where, the maximum pressure P of the electric output of proportional pressure-reducing valve 621fmaxThe pressure provided for offsetting a part of pre-set springs power.
The output pressure P of the electricity proportional pressure-reducing valve 621fWith the relationship of the revolving speed v of the engine can include:Wherein vmaxFor the maximum (top) speed of the engine, P0For the output level pressure of valve core spring 620
(as FBullet/S).The present embodiment directly receives the rotary speed information of engine, controls electric ratio further according to the received rotary speed information of institute
The output pressure of pressure reducing valve.
Certainly, the hydraulic control system in the present invention may also include reception device, for receiving throttle signal；And conversion
Device, for obtaining engine rotational speed signal according to the throttle signal.The controller is used for according to indirect gain
Engine rotational speed signal adjusts the pressure difference between the variable pressure valve both ends.In the hydraulic control system, oil is directly received first
Then the received throttle signal of institute is converted to rotary speed information, finally controlled further according to the rotary speed information of indirect conversion by gate signal
The output pressure of variable pressure valve (such as electric proportional pressure-reducing valve).Compared with the hydraulic control system, above by directly received turn
The hydraulic control system that fast signal is controlled, structure is simpler, and can reach more real-time and be accurately controlled effect.
61 through-current capacity of main valveWherein K is discharge coefficient (it is definite value), and A is the master
The area of passage (handle travel is directly proportional to main valve choke diameter) of valve, pressure difference of the Δ P between the main valve both ends (are being sent out
Pressure differential deltap P=P-P when motivation different rotating speeds, between 61 both ends of main valveLS=FBullet/S-Pf).It is this by electric proportional pressure-reducing valve
The design at variable flow valve both ends is arranged in valve core spring, it is ensured that the spring force that valve core spring provides is larger, is encountering controller
In the case where failure, although electric proportional pressure-reducing valve can not provide its pressure that need to be exported, entire hydraulic control system can still pass through
Constant pressure difference control method in the prior art provides defined spring force and carrys out the pressure difference between control bound both ends, to guarantee system
It can operate normally.Due to Δ P (or Pf) it is a variable relevant to engine speed, therefore may be implemented in any turn of engine
When fast, lead to adjustment PfSize ensure the maximum in the flow and the output flow range that is adjusted by handle of main valve of hydraulic pump output
Through-current capacity is equal, to avoid the appearance of handle idle stroke phenomenon.
Specifically, the output flow of hydraulic pump is Q in the case where engine peak speedmax, main valve through-current capacity with
The curve of handle travel variation is shown in Fig. 7.As handle full stroke C, main valve maximum through-current capacity is also Qmax, and without hand
The appearance of handle idle stroke phenomenon.In the case where engine idling, the output flow of hydraulic pump is Q'max, main valve through-current capacity whips
The curve of handle stroke variation is shown in fig. 8.As handle full stroke C, main valve maximum through-current capacity is also Q'max, and without handle
The appearance of idle stroke phenomenon.In the case where engine different rotating speeds, main valve through-current capacity is shown with the curve that handle travel changes
In Fig. 9.Main valve maximum through-current capacity is equal with the output flow of corresponding hydraulic pump when engine different rotating speeds, and without hand
The appearance of handle idle stroke phenomenon.Thus no matter engine is that high speed is in idling, in whole rows of the handle of main valve
It can realize that the flow of the main valve when adjusting, i.e. idling of flow adjusts that gain is small, and fine motion is good in journey, main valve when high speed
Flow adjusting gain is big, meets the requirement of big flow high speed.
In conclusion the present invention creatively passes through the level pressure element that the both ends of variable flow valve are arranged in and transformation valve regulation master
Pressure difference between valve both ends, wherein the output pressure of variable pressure valve is controlled by controller according to the revolving speed of engine, so that
The output of maximum output flow and hydraulic pump in the output flow range that main valve is adjusted by handle under the different rotating speeds of engine
Flow is equal, and thus no matter engine is that high speed is in idling, is ok in whole strokes of the handle of main valve
The flow of main valve adjusts that gain is small, and fine motion is good when realizing the adjusting, i.e. idling of flow, and the flow of main valve adjusts gain when high speed
Greatly, meet the requirement of big flow high speed.
Certainly, the variable pressure valve in the present invention is not limited to above-mentioned electric proportional pressure-reducing valve, and other output pressures are adjustable
Device (such as proportion electro-magnet) is also feasible.
Correspondingly, as shown in Figure 10, the present invention also provides a kind of differential regulating valuve unit, which can be wrapped
Include: pressure-difference valve, the pressure-difference valve include: variable flow valve, and the first end of the variable flow valve is provided with level pressure element；And transformation
Valve, the variable pressure valve are set to the second end and controller of the variable flow valve, the controller and engine and the variable pressure valve phase
Even, wherein the pressure-difference valve is used under the different revolving speed of the engine, adjusts the pressure difference between main valve both ends, with
Maximum output flow in the output flow range for adjusting the main valve by handle is equal with the output flow of hydraulic pump；The control
Device processed is used to receive the revolving speed of the engine, and the output pressure of the variable pressure valve is controlled according to the revolving speed of the engine,
The hydraulic pump provides hydraulic oil to executive component under the driving of the engine；The main valve is for controlling from described hydraulic
It pumps to the reality output flow of the hydraulic oil of the executive component.The differential regulating valuve unit can directly receive the revolving speed of engine
Signal and the pressure difference that coupled main valve both ends are automatically adjusted according to the tach signal so that the main valve adjusted by handle it is defeated
The maximum output flow of hydraulic oil is equal with the output flow of hydraulic oil provided by hydraulic pump within the scope of outflow.The pressure difference tune
It is simple to save valve cell structure, and can reach more real-time and be accurately controlled effect.
Detail and benefit in relation to differential regulating valuve unit provided by the invention see above-mentioned for hydraulic control
The description of system, repeats no more in this.
Certainly, the differential regulating valuve unit provided by the invention is not limited to receive the tach signal of engine, connects and may be used also
To receive other signals (such as throttle signal) relevant to tach signal；In addition, also applying to any in addition to main valve
In the device or system for needing to carry out pressure difference adjusting.
Correspondingly, the present invention also provides a kind of engineering machinery, which is provided with above-mentioned hydraulic hydraulic control system
System.
Optionally, which is crane.
It is described the prefered embodiments of the present invention in detail above in conjunction with attached drawing, still, the present invention is not limited to above-mentioned realities
The detail in mode is applied, within the scope of the technical concept of the present invention, a variety of letters can be carried out to technical solution of the present invention
Monotropic type, these simple variants all belong to the scope of protection of the present invention.
It is further to note that specific technical features described in the above specific embodiments, in not lance
In the case where shield, it can be combined in any appropriate way.In order to avoid unnecessary repetition, the present invention to it is various can
No further explanation will be given for the combination of energy.
In addition, various embodiments of the present invention can be combined randomly, as long as it is without prejudice to originally
The thought of invention, it should also be regarded as the disclosure of the present invention.
Claims (14)
1. a kind of hydraulic control system, which is characterized in that the hydraulic control system includes:
Hydraulic pump, for providing hydraulic oil to executive component under the driving of engine；
Main valve, for controlling the reality output flow from the hydraulic pump to the hydraulic oil of the executive component；
Pressure-difference valve, the pressure-difference valve include: variable flow valve, and the first end of the variable flow valve is provided with level pressure element；And become
Pressure valve, the variable pressure valve are set to the second end of the variable flow valve, for adjusting the master under the different revolving speed of the engine
Pressure difference between valve both ends so that maximum output flow in the output flow range that the main valve is adjusted by handle with it is described hydraulic
The output flow of pump is equal；And
Controller is connected with the engine and the variable pressure valve, for receiving the revolving speed of the engine, and according to the hair
The revolving speed of motivation controls the output pressure of the variable pressure valve.
2. hydraulic control system according to claim 1, which is characterized in that the level pressure element is valve core spring.
3. hydraulic control system according to claim 1, which is characterized in that the variable pressure valve is electric proportional pressure-reducing valve.
4. hydraulic control system according to claim 2 or 3, which is characterized in that the pressure differential deltap P between the main valve both ends
=FBullet/S-Pf, wherein FBulletFor the pre-set springs power of the valve core spring, S is the area of the first end of the variable flow valve, PfFor institute
State the pressure of electric proportional pressure-reducing valve output.
5. hydraulic control system according to claim 1, which is characterized in that the output pressure P of the variable pressure valvefWith it is described
The relationship of the revolving speed v of engine includes: the output pressure P of the variable pressure valve when the revolving speed v of engine increasefConstantly
Reduce.
6. hydraulic control system according to claim 1, which is characterized in that the output pressure P of the variable pressure valvefWith it is described
The relationship of the revolving speed v of engine includes:Wherein vmaxFor the maximum (top) speed of the engine, P0
For the output level pressure of the level pressure element.
7. hydraulic control system according to claim 1, which is characterized in that the output flow of the main valveWherein K is discharge coefficient, and A is the area of passage of the main valve, and Δ P is between the main valve both ends
Pressure difference.
8. a kind of differential regulating valuve unit, which is characterized in that the differential regulating valuve unit includes:
Pressure-difference valve, the pressure-difference valve include:
Variable flow valve, the first end of the variable flow valve are provided with level pressure element；And
Variable pressure valve, the variable pressure valve are set to the second end of the variable flow valve, and
Controller, the controller are connected with engine and the variable pressure valve,
Wherein, the pressure-difference valve is used under the different revolving speed of the engine, adjusts the pressure difference between main valve both ends, with
Maximum output flow in the output flow range for adjusting the main valve by handle is equal with the output flow of hydraulic pump；The control
Device processed is used to receive the revolving speed of the engine, and the output pressure of the variable pressure valve is controlled according to the revolving speed of the engine,
The hydraulic pump provides hydraulic oil to executive component under the driving of the engine；The main valve is for controlling from described hydraulic
It pumps to the reality output flow of the hydraulic oil of the executive component.
9. differential regulating valuve unit according to claim 8, which is characterized in that the level pressure element is valve core spring.
10. differential regulating valuve unit according to claim 8, which is characterized in that the variable pressure valve is electric proportional pressure-reducing valve.
11. differential regulating valuve unit according to claim 8, which is characterized in that the output pressure P of the variable pressure valvefWith institute
The relationship for stating the revolving speed v of engine includes: the output pressure P of the variable pressure valve when the revolving speed v of engine increasefNo
It is disconnected to reduce.
12. differential regulating valuve unit according to claim 8, which is characterized in that the output pressure P of the variable pressure valvefWith institute
The relationship for stating the revolving speed v of engine includes:Wherein vmaxFor the maximum (top) speed of the engine,
P0For the output level pressure of the level pressure element.
13. a kind of engineering machinery, which is characterized in that the engineering machinery is provided with according to claim 1 described in any one of -7
Hydraulic control system.
14. engineering machinery according to claim 13, which is characterized in that the engineering machinery is crane.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810886399.6A CN108980130A (en) | 2018-08-06 | 2018-08-06 | Differential pressure regulating valve unit, hydraulic control system and engineering machinery |
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| CN201810886399.6A CN108980130A (en) | 2018-08-06 | 2018-08-06 | Differential pressure regulating valve unit, hydraulic control system and engineering machinery |
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| CN108980130A true CN108980130A (en) | 2018-12-11 |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113928980A (en) * | 2021-09-17 | 2022-01-14 | 中联重科股份有限公司 | Closed system, hoisting equipment and crawler-type walking equipment |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN202808201U (en) * | 2012-10-16 | 2013-03-20 | 中联重科股份有限公司 | Hydraulic control system and crane with same |
| CN103727082A (en) * | 2013-12-27 | 2014-04-16 | 三一汽车起重机械有限公司 | Hydraulic system and engineering machine |
-
2018
- 2018-08-06 CN CN201810886399.6A patent/CN108980130A/en active Pending
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN202808201U (en) * | 2012-10-16 | 2013-03-20 | 中联重科股份有限公司 | Hydraulic control system and crane with same |
| CN103727082A (en) * | 2013-12-27 | 2014-04-16 | 三一汽车起重机械有限公司 | Hydraulic system and engineering machine |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113928980A (en) * | 2021-09-17 | 2022-01-14 | 中联重科股份有限公司 | Closed system, hoisting equipment and crawler-type walking equipment |
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