CN104675807B - Differential hydraulic control system and method and crane - Google Patents
Differential hydraulic control system and method and crane Download PDFInfo
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- CN104675807B CN104675807B CN201510109673.5A CN201510109673A CN104675807B CN 104675807 B CN104675807 B CN 104675807B CN 201510109673 A CN201510109673 A CN 201510109673A CN 104675807 B CN104675807 B CN 104675807B
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- differential
- reversal valve
- valve
- hydro cylinder
- working position
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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
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/08—Servomotor systems incorporating electrically operated control means
-
- 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
- B66C13/16—Applications of indicating, registering, or weighing devices
-
- 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
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
- B66C23/00—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes
- B66C23/62—Constructional features or details
- B66C23/82—Luffing gear
-
- 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
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
-
- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/25—Pressure control functions
- F15B2211/253—Pressure margin control, e.g. pump pressure in relation to load pressure
Abstract
The embodiment of the invention discloses a kind of differential hydraulic control system and method and crane, relate to technical field of hydraulic pressure, wherein, system includes: the first reversal valve (1), the second reversal valve (2), check valve (3), limiter of moment (4) and controller (5), first reversal valve (1) is arranged on the oil circuit that the rodless cavity of differential hydro cylinder (7) connects with oil sources, and connects fuel tank；Second reversal valve (2) is respectively communicated with the first reversal valve (1), the rodless cavity of differential hydro cylinder (7) and rod chamber；Check valve (3) is arranged on the oil circuit that the second reversal valve (2) connects with fuel tank；Limiter of moment (4) is connected with controller (5), and the actual lift heavy amount detected is transferred to controller (5)；Controller (5) is connected with the control end of the second reversal valve (2), controls the second reversal valve (2) commutation, to realize differential hydro cylinder (7) differential state and the switching of non-differential state.
Description
Technical field
The present invention relates to technical field of hydraulic pressure, especially a kind of differential hydraulic control system and method,
And crane.
Background technology
Crane operation acts by turning round, luffing, stretch, the four kinds of actions that hoist form.Rise
The luffing action of heavy-duty machine is driven by hydraulic cylinder, and when hydraulic cylinder stretches out, crane work range becomes
Little, when hydraulic cylinder is retracted, crane work range increases.
The off working state such as crane transports, return the vehicle to the garage and knock off, the full reduced rear folding and unfolding of arm on chassis overhang,
Hydraulic cylinder is in stroke minimum position.Before crane enters duty, operator operates crane
Carrying out luffing action makes crane movements to operating position, and this process belongs to auxiliary stroke (also referred to as
For inoperative stroke).During auxiliary stroke, operator wishes the speed of hydraulic cylinder, and The faster the better,
Service working time is reduced with this.
Crane arrives weight of slinging behind operating position, then carries out luffing action so that weight is to conjunction
Suitable position, now requires that hydraulic cylinder can provide bigger working thrust to meet craning weight of same
Need.At the same time it is wished that luffing fine motion is good, i.e. the speed of hydraulic cylinder is the smaller the better, to meet lift heavy
Action needs, and this process belongs to impulse stroke, it is desirable to crane hydraulic cylinder can provide big pushing away
Power and speed are relatively low.
Crane operator completes, crane amplitude variation action to be carried out arm folding and unfolding on chassis overhang,
This process belongs to auxiliary stroke, and The faster the better also to require speed.
In sum: crane amplitude variation action is divided into auxiliary stroke, impulse stroke two parts, auxiliary
Stroke wishes that hydraulic cylinder speed is fast, to reduce service working time；Impulse stroke wishes hydraulic cylinder energy
Enough provide big thrust and speed slow, to ensure the requirement of fine motion.
But, existing hydraulic system or be differential hydraulic system, or it is non-differential hydraulic system
System.In differential hydraulic system, hydraulic cylinder is in differential state, it is possible to meet the requirement of auxiliary stroke,
But the requirement of impulse stroke can not be met；Rather than in differential hydraulic system, hydraulic cylinder is in non-differential
State, it is possible to meet the requirement of impulse stroke, but the requirement of auxiliary stroke can not be met.Therefore,
Urgent needs one hydraulic system, can either meet the requirement of auxiliary stroke, it is also possible to meet work
The requirement of stroke.
Summary of the invention
One purpose of the embodiment of the present invention is: provide a kind of differential hydraulic control system and method and
Crane, can either meet the requirement of auxiliary stroke, it is also possible to meet the requirement of impulse stroke.
According to an aspect of the present invention, it is provided that a kind of differential hydraulic control system, including: first changes
To valve, the second reversal valve, check valve, limiter of moment and controller, wherein: described first changes
It is arranged on the oil circuit that the rodless cavity of differential hydro cylinder connects with oil sources to valve, and connects fuel tank；
Described second reversal valve is respectively communicated with described first reversal valve, the rodless cavity of differential hydro cylinder and has bar
Chamber；Described check valve is arranged on the oil circuit that described second reversal valve connects with described fuel tank；Described
Limiter of moment is connected with described controller, and the actual lift heavy amount detected is transferred to described control
Device；The control end of described controller and the second reversal valve connects, and controls described second reversal valve commutation,
To realize differential hydro cylinder differential state and the switching of non-differential state.
In one embodiment, described second reversal valve is pilot operated directional control valve；Described system also includes:
Solenoid directional control valve, described solenoid directional control valve is arranged on hydraulic control end and the hydraulic oil of described second reversal valve
On oil circuit between source, and the control end of described solenoid directional control valve is connected with controller.
In one embodiment, connect with the rodless cavity of differential hydro cylinder at described first reversal valve
Balanced valve it is provided with on oil circuit.
In one embodiment, also including overflow valve, the oil-in of described overflow valve connects described oil
Source, the oil-out connection fuel tank of described overflow valve.
In one embodiment, described second reversal valve includes the first working position and the second working position；
Described second reversal valve when the first working position, the rod chamber of described differential hydro cylinder and rodless cavity it
Between oil communication；Described second reversal valve when the second working position, having of described differential hydro cylinder
Oil communication between bar chamber and described first reversal valve.
In one embodiment, described first reversal valve includes middle position, the first working position and the second work
Make position；Described second reversal valve includes the first working position and the second working position；Described first reversal valve
The first working position, described second reversal valve at the first working position time, the rodless cavity of differential hydro cylinder
And the oil circuit between the oil communication between oil sources, and the rod chamber of differential hydro cylinder and rodless cavity
Connection；Described first reversal valve the first working position, described second reversal valve at the second working position time,
Oil communication between rodless cavity and the oil sources of differential hydro cylinder, and described differential hydro cylinder have
Oil communication between bar chamber and described first reversal valve；Described first reversal valve the second working position,
Described second reversal valve is when the first working position, between rodless cavity and the described fuel tank of differential hydro cylinder
Oil communication, and the rod chamber of differential hydro cylinder and rodless cavity and between oil communication；Institute
State the first reversal valve the second working position, described second reversal valve at the second working position time, differential liquid
Oil communication between rodless cavity and the described fuel tank of cylinder pressure, and described differential hydro cylinder have bar
Oil communication between chamber and described first reversal valve.
In one embodiment, described first reversal valve is three-position four-way valve.
In one embodiment, described second reversal valve is two position three-way valve.
According to a further aspect in the invention, it is provided that a kind of crane, carry including any of the above-described embodiment
The differential hydraulic control system of confession.
According to another aspect of the invention, it is provided that a kind of differential hydraulic based on any of the above-described embodiment
The differential hydraulic control method of control system, including controlling process as follows: limiter of moment will detection
To actual lift heavy amount be transferred to controller；Described controller is according to actual lift heavy amount and preset value
Relation, controls the second reversal valve commutation, to realize differential hydro cylinder differential state and non-differential state
Between mutual switching.
In one embodiment, described controller is when actual lift heavy amount is less than preset value, and it is poor to control
Hydrodynamic cylinder pressure is in differential state；Described controller, when actual lift heavy amount is more than preset value, controls
Differential hydro cylinder is in non-differential state.
In one embodiment, in the case of differential hydro cylinder is in the state of stretching out, described control
Device, when actual lift heavy amount is less than preset value, controls differential hydro cylinder and is in and differential stretches out state；Institute
State controller when actual lift heavy amount is more than preset value, control differential hydro cylinder and be in non-differential stretch out
State；In the case of differential hydro cylinder is in retracted mode, described controller is in actual lift heavy amount
During less than preset value, control differential hydro cylinder and be in differential retracted mode；Described controller is in reality
When lift heavy amount is more than preset value, controls differential hydro cylinder and be in non-differential retracted mode.
The embodiment of the present invention at least has the advantages that
On the one hand, according to the actual lift heavy amount of power limit device detection, it may be determined that current working condition requirement,
Such that it is able to carry out according to the actual requirements between the differential state of differential hydro cylinder and non-differential state
Switching, can either meet the requirement of auxiliary stroke, it is also possible to meet the requirement of impulse stroke.Auxiliary
Stroke can provide low-voltage high speed operating mode, improves working performance；Impulse stroke can provide height to force down
Speed operating mode, meets high thrust, the requirement of fine motion in operation.
On the other hand, it is not necessary to carry out the switching of state according to the operating experience of operator, can effectively keep away
Exempt from maloperation, safe and efficient and intelligence degree is high.
Another aspect, this hydraulic control system conventional hydraulic components based on crane and control unit
Part, simple in construction, it is easy to accomplish.
Below by drawings and Examples, technical scheme is described in further detail.
Accompanying drawing explanation
In order to be illustrated more clearly that the embodiment of the present invention or technical scheme of the prior art, below will
The accompanying drawing used required in embodiment or description of the prior art is briefly described, it is clear that
Ground, the accompanying drawing in describing below is only some embodiments of the present invention, skill common for this area
From the point of view of art personnel, on the premise of not paying creative work, it is also possible to obtain according to these accompanying drawings
Obtain other accompanying drawing.
Fig. 1 is the structural representation of one embodiment of differential hydraulic control system of the present invention；
Fig. 2 is the structural representation of differential hydraulic another embodiment of control system of the present invention.
Detailed description of the invention
Below in conjunction with the accompanying drawing in the embodiment of the present invention, to the technical scheme in the embodiment of the present invention
It is clearly and completely described, it is clear that described embodiment is only that a part of the present invention is real
Execute example rather than whole embodiments.Based on the embodiment in the present invention, ordinary skill
The every other embodiment that personnel are obtained under not making creative work premise, broadly falls into this
The scope of invention protection.
Unless specifically stated otherwise, the parts illustrated the most in these embodiments and the phase of step
Layout, numerical expression and numerical value are not limited the scope of the invention.
Simultaneously, it should be appreciated that for the ease of describing, the chi of the various piece shown in accompanying drawing
Very little is not to draw according to actual proportionate relationship.
May not make in detail for technology, method and apparatus known to person of ordinary skill in the relevant
Thin discussion, but in the appropriate case, described technology, method and apparatus should be considered to authorize to be said
A part for bright book.
Shown here with in all examples discussed, any occurrence should be construed as merely
Exemplary rather than conduct limits.Therefore, other example of exemplary embodiment can have
There is different values.
It should also be noted that similar label and letter expression similar terms in following accompanying drawing, therefore,
The most a certain Xiang Yi accompanying drawing is defined, then need not it is carried out in accompanying drawing subsequently
Discussed further.
First the technical term related in the present invention is explained.
Differential hydro cylinder: for pressure oil in the rodless cavity of single-piston-rod hydraulic cylinder, by rod chamber
The oil discharged takes back rodless cavity, referred to as differential hydro cylinder again, and it utilizes the effective of hydraulic cylinder two ends
Difference in areas carries out transmission.
Luffing: from the horizontal range of autocrane rings center line to crane rotation centrage,
The i.e. radius of gyration of lifted weight or the radius of clean-up, referred to as work range, changes work range
Size is referred to as luffing.
Gravity fall: when crane work range changes from small to big (when luffing falls), luffing
Power produced by the deadweight such as arm, referred to as gravity fall.
Limiter of moment (is called for short power limit device): independent is complete by computer-controlled safety behaviour
Make system, can automatically detect the angle residing for the quality of the hung load of crane and crane arm, and
The angle residing for its nominal load capacity and real load, the radius of clean-up, crane arm can be demonstrated.
Monitoring crane operating mode, carries diagnostic function, and can carry out quick hazard condition warning applications in real time
Sound control.Additionally, also have black box function, dangerous working condition during record operation automatically,
Process for accident analysis and foundation is provided.
Power limit device, controller are the vitals of crane.Under non-lift heavy state, power limit device shows
Show is suspension hook weight, and under lift heavy state, power limit device is shown that suspension hook and adds the weight of lift heavy.
Controller is the control centre of crane, can control the various actions of crane.
Crane operator wishes (that is, auxiliary stroke), the speed of hydraulic cylinder under non-lift heavy state
Degree is big, thrust is little, belongs to low-voltage high speed operating mode；Under lift heavy state (that is, impulse stroke),
The speed of hydraulic cylinder is little, thrust big, meets fine motion requirement, belongs to high pressure speed operation.
Fig. 1 is the structural representation of one embodiment of differential hydraulic control system of the present invention.Such as Fig. 1
Shown in, this system includes: first reversal valve the 1, second reversal valve 2, check valve 3, moment limit
Device 4 and controller 5, wherein:
First reversal valve 1 is arranged on the oil circuit that the rodless cavity of differential hydro cylinder 7 connects with oil sources,
And connect fuel tank；Second reversal valve 2 is respectively communicated with first reversal valve 1, differential hydro cylinder 7
Rodless cavity and rod chamber；Check valve 3 is arranged on the oil circuit that the second reversal valve 2 connects with fuel tank；
Limiter of moment 4 is connected with controller 5, and the actual lift heavy amount detected is transferred to controller 5；
Controller 5 is connected with the control end of the second reversal valve 2, controls the second reversal valve 2 and commutates, with reality
Existing differential hydro cylinder 7 differential state and the switching of non-differential state.
Actual lift heavy amount G that limiter of moment detects can be reacted crane and is in lift heavy shape
State is in non-lift heavy state.Specifically, threshold value G can be set ', such as can be by
Threshold value G ' it is set as suspension hook weight or more than suspension hook weight.
Controller can read actual lift heavy amount G that limiter of moment detects, and by actual lift heavy
Amount G and threshold value G ' compare, when actual lift heavy amount G is less than threshold value G ' time, it may be determined that lifting
Machine is in non-lift heavy state, i.e. auxiliary stroke, therefore controls the second reversal valve commutation, to control
Differential hydro cylinder is in differential state, thus meets the need of the low-voltage high speed operating mode of big speed low thrust
Ask.Certainly, if current differential hydro cylinder is already at differential state, controller is then without controlling
Second reversal valve commutation.
When actual lift heavy amount G is more than threshold value G ' time, it may be determined that crane is in lift heavy state,
I.e. impulse stroke, therefore controls the second reversal valve commutation, is in non-differential controlling differential hydro cylinder
State, thus meet the demand of the high pressure speed operation of little speed high thrust.Certainly, if currently
Differential hydro cylinder is already at non-differential state, and controller is then without controlling the second reversal valve commutation again.
The embodiment of the present invention is according to the actual lift heavy amount of power limit device detection, it may be determined that current operating mode
Requirement, such that it is able to carry out the differential state of differential hydro cylinder and non-differential state according to the actual requirements
Between switching, the requirement of auxiliary stroke can either be met, it is also possible to meet the requirement of impulse stroke.
Auxiliary stroke can provide low-voltage high speed operating mode, improves working performance；Impulse stroke can provide high
Pressure speed operation, meets high thrust, the requirement of fine motion in operation.It addition, without according to operation
The operating experience of person carries out the switching of state, can be prevented effectively from maloperation, safe and efficient and intelligent
Degree is high.Additionally, this hydraulic control system conventional hydraulic components based on crane and control unit
Part, simple in construction, it is easy to accomplish.
The differential hydraulic control system that the embodiment of the present invention provides is suitable to but is not limited under crane gravity
The changing-breadth system fallen, owing to can be switched to differential state according to practical situation, it is possible to solve existing
Gravity declines changing-breadth system in the slow problem of luffing falling speed by a small margin.When reality is applied, with
As a example by crane amplitude variation action, unloaded (not lift heavy) luffing of crane auxiliary stroke correspondence crane
Action；Impulse stroke correspondence craning weight of same luffing action.Due to crane auxiliary stroke, work
Have between stroke hoist, turn round, the action, i.e. crane zero load luffing, luffing with payload such as stretch
Between have certain operating interval, therefore controller can be read power limit device actual lift heavy amount G
Time interval be set smaller than this operating interval, such that it is able to avoid the differential shape of differential hydro cylinder
The hydraulic shock that switching between state and non-differential state causes.
It should be noted that the function of the controller in the present invention can be realized by software, also
Can realize by the way of hardware.As an example of the implementation of hardware, such as,
Comparator can be used to realize the function of controller.Specifically, comparator can compare actual hanging
Weight G and threshold value G ' size, when actual lift heavy amount is less than threshold value, send out to the second reversal valve
Send low level signal, be in differential state controlling differential hydro cylinder；In actual lift heavy amount more than threshold
During value, send high level signal to the second reversal valve, be in non-differential shape controlling differential hydro cylinder
State.
Should be understood that the second reversal valve is connecing if the original state of differential hydro cylinder is differential state
When receiving low level signal, it is not necessary to commutation；If the original state of differential hydro cylinder is non-differential shape
State, the second reversal valve, when receiving low level signal, needs commutation to realize differential hydro cylinder by non-
Differential state is to the switching of differential state.
It addition, can also be in turn to the control mode of the second reversal valve, i.e. in actual lift heavy amount
During less than threshold value, send high level signal to the second reversal valve；When actual lift heavy amount is more than threshold value,
Low level signal is sent to the second reversal valve.Implement with reference to above description.
It is pointed out that, as a non-limiting example, above-mentioned oil sources such as can pass through liquid
Press pump and fuel tank realize, or can also be other any form of oil sources.
In the differential hydraulic control system of the present invention, the second reversal valve 2 both can be solenoid directional control valve,
Can also be pilot operated directional control valve, below both of these case be illustrated respectively.
In the case of one, seeing Fig. 1, the second reversal valve 2 can be solenoid directional control valve, controller
Its commutation can be controlled, it is achieved differential hydro cylinder 7 is poor by sending the signal of telecommunication to solenoid directional control valve
Dynamic state and the switching of non-differential state.Concrete handoff procedure may refer to the description of above example.
In the case of another kind, another reality of differential hydraulic control system of the present invention shown in Figure 2
Executing example, the second reversal valve 2 can be pilot operated directional control valve.Correspondingly, this system also includes: electromagnetism
Reversal valve 10, this solenoid directional control valve 10 is arranged on hydraulic control end and the hydraulic oil source of the second reversal valve 2
Between oil circuit on, and the control end of solenoid directional control valve 10 is connected with controller 5.Here,
Hydraulic oil source can be oil sources as shown in Figure 2, it is also possible to take from other stable oil sources.
In this case, by by differential state as a example by non-differential state switches, when needs control the
When two reversal valves 2 commutate, such as, controller can send the signal of telecommunication to solenoid directional control valve 10,
Make solenoid directional control valve 10 be operated in left position, then control fluid and act on through solenoid directional control valve 10
In the hydraulic control end of pilot operated directional control valve 2, pilot operated directional control valve 2 is made to be in right position, hydraulic pressure in ends with system
The differential state of oil cylinder, makes hydraulic jack be in non-differential state, and now hydraulic jack provides high pressure
Speed operation, meets the requirement of crane high thrust, fine motion.Similarly, people in the art
Member may determine that, by non-differential state when differential state switches, controller is to solenoid directional control valve 10
With the control situation of the second reversal valve 2, do not repeat them here.
As a specific embodiment, the second reversal valve 2 can include the first working position and the second work
Make position, when the second reversal valve 2 is at the first working position, the rod chamber of differential hydro cylinder 7 with without bar
Oil communication between chamber, now, differential hydro cylinder is in differential state；When the second reversal valve 2
When the second working position, the oil circuit between rod chamber and first reversal valve 1 of differential hydro cylinder 7 is even
Logical, now, differential hydro cylinder is in non-differential state.
As another specific embodiment, the first reversal valve 1 can include middle position, the first working position
With the second working position, the second reversal valve 2 can include the first working position and the second working position.Such as,
First reversal valve 1 can be three-position four-way valve, and the second reversal valve 2 can be two position three-way valve.So
And, the present invention is not limited to this, it is also possible to realize the first reversal valve and the second commutation by other valves
The function of valve.
Differential hydro cylinder, when stretching out or retract, all can realize differential state and non-differential state
Switching.By controlling the working position of the first reversal valve, stretching out or contracting of differential hydro cylinder can be controlled
The state of returning.
Below in conjunction with the first reversal valve and the working position of the second reversal valve, differential to differential hydro cylinder
Stretch out/retracted mode with non-differential stretch out/retracted mode illustrates.
When the first reversal valve 1 the first working position, the second reversal valve 2 at the first working position time, poor
Oil communication between rodless cavity and the oil sources of hydrodynamic cylinder pressure 7, and differential hydro cylinder 7 have bar
Oil communication between chamber and rodless cavity.Now, differential hydro cylinder 7 is in and differential stretches out state.
Hydraulic oil from oil sources passes through the first reversal valve 1 and enters the rodless cavity of differential hydro cylinder 7, differential
The hydraulic oil of the rod chamber of hydraulic cylinder 7 can be flowed by a part of hydraulic oil after the second reversal valve 2
To the rodless cavity of differential hydro cylinder 7, increase differential hydro cylinder 7 stretches out speed.
When the first reversal valve 1 the first working position, the second reversal valve 2 at the second working position time, poor
Oil communication between rodless cavity and the oil sources of hydrodynamic cylinder pressure 7, and differential hydro cylinder 7 have bar
Oil communication between chamber and the first reversal valve 1.Now, differential hydro cylinder 7 is in non-differential stretch
Do well.From oil sources hydraulic oil by the first reversal valve 1 enter differential hydro cylinder 7 without bar
Chamber, the hydraulic oil of the rod chamber of differential hydro cylinder 7 flows to the first commutation by after the second reversal valve 2
Valve 1, and then flow into fuel tank.
When the first reversal valve 1 the second working position, the second reversal valve 2 at the first working position time, poor
Oil communication between rodless cavity and the fuel tank of hydrodynamic cylinder pressure 7, and differential hydro cylinder 7 have bar
Chamber and rodless cavity and between oil communication.Now, differential hydro cylinder 7 is in differential retracted mode.
A part for the hydraulic oil of the rodless cavity of differential hydro cylinder 7 flows into fuel tank by the first reversal valve 1,
Another part flows to the rod chamber of differential hydro cylinder 7 by the second reversal valve 2, increases differential liquid
The retraction speed of cylinder pressure 7.
When the first reversal valve 1 the second working position, the second reversal valve 2 at the second working position time, poor
Oil communication between rodless cavity and the fuel tank of hydrodynamic cylinder pressure 7, and differential hydro cylinder 7 have bar
Oil communication between chamber and the first reversal valve 1.The hydraulic oil of the rodless cavity of differential hydro cylinder 7 leads to
Crossing the first reversal valve 1 and flow into fuel tank, the hydraulic oil in fuel tank is by check valve 3 and the second commutation
Valve 2 is to the rod chamber repairing of differential hydro cylinder 7.
It addition, as a concrete example of the first reversal valve 1, when the first reversal valve 1 is in middle position
Time, the second reversal valve 2 can be connected with fuel tank by the restriction in the valve rod of the first reversal valve 1.
Now, differential hydro cylinder 7 does not the most do and stretches out motion, does not the most do retraction movement.
In another embodiment of differential hydraulic control system of the present invention, see Fig. 1 or Fig. 2,
It is provided with balanced valve 8 on the oil circuit that first reversal valve 1 connects with the rodless cavity of differential hydro cylinder 7,
Steady to ensure differential hydro cylinder 7 speed when retracting, it is to avoid the generation of stall event.
In differential hydraulic control system further embodiment of the present invention, see Fig. 1 or Fig. 2, also
Bag can include overflow valve 9, the oil-in connection oil sources of overflow valve 9, the oil-out of overflow valve 9
Connection fuel tank.The supply pressure of system can be limited, such as at system pressure by arranging overflow valve
Open more than overflow valve during 20MPa, to reduce the supply pressure of system.
The differential hydraulic control of the differential hydraulic control system that the present invention provides based on any of the above-described embodiment
In one embodiment of method processed, including controlling process as follows:
The actual lift heavy amount detected is transferred to controller 5 by limiter of moment 4；Controller 5
Border lift heavy amount and the relation of preset value, control the second reversal valve 2 and commutate, to realize differential liquid factually
Mutual switching between cylinder pressure 7 differential state and non-differential state.
The present embodiment is according to the actual lift heavy amount of power limit device detection, it may be determined that current working condition requirement,
Such that it is able to carry out according to the actual requirements between the differential state of differential hydro cylinder and non-differential state
Switching, can either meet the requirement of auxiliary stroke, it is also possible to meet the requirement of impulse stroke.Auxiliary
Stroke can provide low-voltage high speed operating mode, improves working performance；Impulse stroke can provide height to force down
Speed operating mode, meets high thrust, the requirement of fine motion in operation.It addition, without according to operator's
Operating experience carries out the switching of state, can be prevented effectively from maloperation, safe and efficient and intelligence degree
High.
In another embodiment of differential hydraulic control method of the present invention, controller 5 is at actual lift heavy
When amount is less than preset value, by controlling the second reversal valve 2 so that the rod chamber of differential hydro cylinder 7
And the oil communication between rodless cavity, thus control differential hydro cylinder 7 and be in differential state；Control
Device 5 is when actual lift heavy amount is more than preset value, by controlling the second reversal valve 2 so that differential liquid
Oil communication between rod chamber and first reversal valve 1 of cylinder pressure 7, thus control differential hydro cylinder
7 are in non-differential state.
In another embodiment of differential hydraulic control method of the present invention, no matter differential hydro cylinder 7
It is in the state of stretching out and is in retracted mode, all can realize differential state and non-differential state
Switching, explains separately below.
Such as, at the second reversal valve when being in different working positions, differential hydro cylinder 7 is in be stretched
Go out or retracted mode.
In the case of differential hydro cylinder 7 is in the state of stretching out, controller 5 is little in actual lift heavy amount
When preset value, control differential hydro cylinder 7 and be in and differential stretch out state；Controller 5 hangs actual
When weight is more than preset value, controls differential hydro cylinder 7 and be in and non-differential stretch out state.
In the case of differential hydro cylinder 7 is in retracted mode, controller 5 is little in actual lift heavy amount
When preset value, control differential hydro cylinder 7 and be in differential retracted mode；Controller 5 hangs actual
When weight is more than preset value, controls differential hydro cylinder 7 and be in non-differential retracted mode.
It is pointed out that when controlling differential hydro cylinder 7 and being in differential state or non-differential state,
The conducting situation of oil circuit is referred to the associated description of said system and/or embodiment of the method, at this
The most no longer it is described in detail.
Differential hydraulic control system of the present invention can be applied on crane.
In an embodiment of the crane of present invention offer, any of the above-described embodiment can be included
In hydraulic differential control system.
One of ordinary skill in the art will appreciate that: realize all or part of of said method embodiment
Step can be completed by the hardware that programmed instruction is relevant, and aforesaid program can be stored in a meter
In calculation machine read/write memory medium, this program upon execution, performs to include said method embodiment
Step；And aforesaid storage medium includes: ROM, RAM, magnetic disc or CD etc. are various can
To store the medium of program code.
In describing the invention, it is to be understood that use " first ", " second ",
Parts are limited, it is only for be easy to above-mentioned parts is distinguished, as not having Deng word
Stated otherwise, above-mentioned word is had not to have particular meaning, therefore it is not intended that the present invention is protected
Protect the restriction of scope.
Description of the invention is given for the sake of example and description, and is not exhaustively
Or it limit the invention to disclosed form.Many modifications and variations are for the common skill of this area
It is obvious for art personnel.Selecting and describing embodiment is the principle in order to the present invention is more preferably described
Apply with reality, and make those of ordinary skill in the art it will be appreciated that the present invention thus design is suitable
The various embodiments with various amendments in special-purpose.
Claims (12)
1. a differential hydraulic control system, it is characterised in that including: the first reversal valve (1),
Second reversal valve (2), check valve (3), limiter of moment (4) and controller (5), wherein:
The rodless cavity that described first reversal valve (1) is arranged on differential hydro cylinder (7) connects with oil sources
Oil circuit on, and connect fuel tank；Described second reversal valve (2) is respectively communicated with described first and changes
To valve (1), the rodless cavity of differential hydro cylinder (7) and rod chamber；Described check valve (3) is arranged
On the oil circuit that described second reversal valve (2) connects with described fuel tank；Described limiter of moment (4)
It is connected with described controller (5), the actual lift heavy amount detected is transferred to described controller
(5)；Described controller (5) is connected with the control end of the second reversal valve (2), controls described
Two reversal valves (2) commutate, to realize differential hydro cylinder (7) differential state and non-differential state
Switching.
System the most according to claim 1, it is characterised in that described second reversal valve (2)
For pilot operated directional control valve；
Described system also includes: solenoid directional control valve (10), and described solenoid directional control valve (10) is arranged
On oil circuit between hydraulic control end and the hydraulic oil source of described second reversal valve (2) and described
The control end of solenoid directional control valve (10) is connected with controller (5).
System the most according to claim 1, it is characterised in that at described first reversal valve
(1) it is provided with balanced valve (8) on the oil circuit that the rodless cavity with differential hydro cylinder (7) connects.
System the most according to claim 1, it is characterised in that also include overflow valve (9),
The oil-in of described overflow valve (9) connects described oil sources, and the oil-out of described overflow valve (9) is even
Logical fuel tank.
System the most according to claim 1, it is characterised in that described second reversal valve (2)
Including the first working position and the second working position；
Described second reversal valve (2) when the first working position, having of described differential hydro cylinder (7)
Oil communication between bar chamber and rodless cavity；Described second reversal valve (2) when the second working position,
Oil communication between rod chamber and described first reversal valve (1) of described differential hydro cylinder (7).
System the most according to claim 1, it is characterised in that described first reversal valve (1)
Including middle position, the first working position and the second working position；Described second reversal valve (2) includes first
Working position and the second working position；
Described first reversal valve (1) at the first working position, described second reversal valve (2) first
During working position, the oil communication between rodless cavity and the oil sources of differential hydro cylinder (7), and poor
Oil communication between rod chamber and the rodless cavity of hydrodynamic cylinder pressure (7)；Described first reversal valve (1)
The first working position, described second reversal valve (2) at the second working position time, differential hydro cylinder (7)
Rodless cavity and oil sources between oil communication, and the rod chamber of described differential hydro cylinder (7)
And the oil communication between described first reversal valve (1)；
Described first reversal valve (1) at the second working position, described second reversal valve (2) first
During working position, the oil communication between rodless cavity and the described fuel tank of differential hydro cylinder (7), and
And the oil communication between rod chamber and the rodless cavity of differential hydro cylinder (7)；Described first commutation
Valve (1) the second working position, described second reversal valve (2) at the second working position time, differential liquid
Oil communication between rodless cavity and the described fuel tank of cylinder pressure (7), and described differential hydro cylinder
(7) the oil communication between rod chamber and described first reversal valve (1).
System the most according to claim 1, it is characterised in that described first reversal valve (1)
For three-position four-way valve.
System the most according to claim 1, it is characterised in that described second reversal valve (2)
For two position three-way valve.
9. a crane, it is characterised in that include described in claim 1-8 any one
Differential hydraulic control system.
10. a difference based on the differential hydraulic control system described in claim 1-8 any one
Hydrodynamic pressure control method, it is characterised in that include controlling as follows process:
The actual lift heavy amount detected is transferred to controller (5) by limiter of moment (4)；Described
Controller (5), according to the relation of actual lift heavy amount Yu preset value, controls the second reversal valve (2) and changes
To, to realize the mutual switching between differential hydro cylinder (7) differential state and non-differential state.
11. methods according to claim 10, it is characterised in that
Described controller (5), when actual lift heavy amount is less than preset value, controls differential hydro cylinder (7)
It is in differential state；
Described controller (5), when actual lift heavy amount is more than preset value, controls differential hydro cylinder (7)
It is in non-differential state.
12. methods according to claim 10, it is characterised in that
In the case of differential hydro cylinder (7) is in the state of stretching out, described controller (5) is in reality
When border lift heavy amount is less than preset value, controls differential hydro cylinder (7) and be in and differential stretch out state；Institute
State controller (5) actual lift heavy amount more than preset value time, control differential hydro cylinder (7) be in
Non-differential stretch out state；
In the case of differential hydro cylinder (7) is in retracted mode, described controller (5) is in reality
When border lift heavy amount is less than preset value, controls differential hydro cylinder (7) and be in differential retracted mode；Institute
State controller (5) actual lift heavy amount more than preset value time, control differential hydro cylinder (7) be in
Non-differential retracted mode.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201510109673.5A CN104675807B (en) | 2015-03-12 | 2015-03-12 | Differential hydraulic control system and method and crane |
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| CN201510109673.5A CN104675807B (en) | 2015-03-12 | 2015-03-12 | Differential hydraulic control system and method and crane |
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| CN104675807A CN104675807A (en) | 2015-06-03 |
| CN104675807B true CN104675807B (en) | 2017-01-04 |
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Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN105041745A (en) * | 2015-06-29 | 2015-11-11 | 南阳二机石油装备(集团)有限公司 | Differential control system of double-acting single-stage piston hydraulic cylinder |
| CN105201938A (en) * | 2015-09-15 | 2015-12-30 | 芜湖市汽车产业技术研究院有限公司 | Reversing system for machining tool |
| CN108561358B (en) * | 2018-01-22 | 2020-05-08 | 威海钰辉机械有限公司 | Differential circuit switching valve and hydraulic differential circuit |
| CN108999820A (en) * | 2018-08-27 | 2018-12-14 | 中国空气动力研究与发展中心高速空气动力研究所 | A kind of soft wall coordinated control system of wind-tunnel and method |
| CN109650252B (en) * | 2018-12-25 | 2024-01-09 | 浙江中锐重工科技有限公司 | Hydraulic grab system and grab device |
| CN110005660A (en) * | 2019-04-02 | 2019-07-12 | 哈工新欧(岳阳)测控装备有限公司 | A kind of hydraulic differential circuit of pressure control switching |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| JP2010078035A (en) * | 2008-09-25 | 2010-04-08 | Caterpillar Japan Ltd | Hydraulic cylinder control circuit of utility machine |
| CN203730423U (en) * | 2014-03-10 | 2014-07-23 | 中联重科股份有限公司 | Telescoping control loop for hydraulic cylinder and engineering machinery |
| CN204061372U (en) * | 2014-08-11 | 2014-12-31 | 徐州工业职业技术学院 | A kind of oil hydraulic cylinder quick-expansion control loop |
| CN204082721U (en) * | 2014-09-17 | 2015-01-07 | 托普威尔石油技术股份公司 | A kind of fluid pressure drive device of lifting machine |
| CN104295545A (en) * | 2014-09-18 | 2015-01-21 | 芜湖高昌液压机电技术有限公司 | Differential speed increasing loop for gantry hoist |
| CN204572645U (en) * | 2015-03-12 | 2015-08-19 | 徐州重型机械有限公司 | Differential hydraulic control system and hoist |
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Address after: 221000 68 Gaoxin Road, Xuzhou economic and Technological Development Zone, Jiangsu Patentee after: Xuzhou Heavy Machinery Co., Ltd. Address before: No. 165, Tongshan Road, Xuzhou, Jiangsu Province Patentee before: Xuzhou Heavy Machinery Co., Ltd. |