CN105402180B - Proportional multi-way valve, arm support hydraulic control system and concrete mixer - Google Patents
Proportional multi-way valve, arm support hydraulic control system and concrete mixer Download PDFInfo
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- CN105402180B CN105402180B CN201410400846.4A CN201410400846A CN105402180B CN 105402180 B CN105402180 B CN 105402180B CN 201410400846 A CN201410400846 A CN 201410400846A CN 105402180 B CN105402180 B CN 105402180B
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Abstract
The present invention relates to a kind of proportional multi-way valve, arm support hydraulic control system and concrete mixer, proportional multi-way valve includes first valve body, tail connection valve body and at least one work connection valve body being arranged between first valve body and tail the connection valve body, it is characterized in that, pressure reducing valve is equipped with the tail connection valve body, the entrance of the pressure reducing valve is connected with the main oil feeding line, the outlet of the pressure reducing valve and the pilot control oil communication of the main reversing valve at least one work connection valve body, join the main reversing valve in valve body to each work and pilot control oil is provided, realize electrichydraulic control.The pressure reducing valve that the present invention is set in being joined by tail can be the configuration that proportional multi-way valve saves external guide's oil pump, and avoid setting guide structure in first as far as possible, and cause valve volume larger, the problem of processed complex, so as to optimize the pilot control structure of proportional multi-way valve.
Description
Technical field
The present invention relates to engineering machinery field, more particularly to a kind of proportional multi-way valve, arm support hydraulic control system and coagulation
Native pump truck.
Background technology
Concrete mixer is special-purpose vehicle pumping mechanism and boom system being integrated on automobile chassis.And concrete pump
The boom system of car is mainly used for conveying and the cloth of concrete, i.e., the expansion and gathering of arm support are controlled by oil cylinder, coordinates and turns
The revolution of platform, concrete conveyance is poured a little to what is specified.
Proportional multi-way valve is the core element of construction machinery hydraulic system, between pump and executive component.At present mixed
It is in the arm support hydraulic control system of solidifying soil pump truck to employ proportional multi-way valve more, and proportional multi-way valve is frequently with manual control commutation
Or proportion electro-magnet electrichydraulic control commutation, make the proportional change of the stroke of spool, so as to the flow of accuracy-control system, so that
Arm support is set to be unfolded by preferable speed.For the arm support hydraulic control system for employing load sensitive system, it will usually
Play balanced load using pressure-compensated valve, make all valve rod inlet outlet pressure differentials equal, ensure the work connection of proportional multi-way valve
Flow is only related with the stroke of the manipulation valve rod, and manipulator easily controls its composite move by the hope of oneself, keeps each execution
The independence of device movement.
In current proportional multi-way valve, guide structure has the row for using manual control, hydraulic control, automatically controlled form, making spool
The proportional change of journey.Pilot control can set guide by the way of external pilot control oil, or in the first of valve body
Structure, and then ratio control carries out spool stroke by the electrichydraulic control of guide, but the mode of external pilot control oil needs
Configure more hydraulic pumps, and guide structure is set in first, then again can be because of multiple hydraulic pressure in guide structure and first
The cooperation of element and cause valve volume larger, processing it is also increasingly complex.
In current load-sensitive proportional multi-way valve, when work joins work, the pressure corresponding to A, B mouth of load is logical
Cross spool cooperation position different from valve body to draw loaded work piece pressure, and feed back in system, compensation loads low work
Make the pressure joined, keep constant the pressure difference that main valve plug is imported and exported, and then make load flow proportional to spool stroke.Pressure is mended
Although repay valve arrangement can equally loaded, its each connection load feedback pressure is by the different cooperation position of spool, valve body
Pressure-compensated valve one end is fed back to, this can make spool, valve body structure extremely complex, and then increase difficulty of processing.
The content of the invention
The purpose of the present invention is to propose to a kind of proportional multi-way valve, arm support hydraulic control system and concrete mixer, Neng Gouyou
Change the pilot control structure of proportional multi-way valve.
To achieve the above object, the present invention provides a kind of proportional multi-way valve, including first valve body, tail connection valve body and setting
At least one work between the first valve body and tail connection valve body joins valve body, wherein, it is equipped with decompression in the tail connection valve body
Valve, the entrance of the pressure reducing valve are connected with the main oil feeding line, and the outlet of the pressure reducing valve joins with least one work
The pilot control oil communication of main reversing valve in valve body, the main reversing valve joined to each work in valve body provide pilot control
Oil, realizes electrichydraulic control.
Further, the work connection valve body includes valve body body, is arranged on the intrinsic main reversing valve of the valve body, pressure
Force compensating valve and the first shuttle valve, the pressure-compensated valve carry out valve precompensation to the main reversing valve, and the valve body body has
Valve body oil inlet, valve body oil return opening and two load hydraulic fluid ports, two oil inlets of first shuttle valve are in work connection
The input of the load pressure of two load hydraulic fluid ports of the valve body body is received under working status respectively, first shuttle valve goes out
The load pressure filtered out is exported the spring side control chamber to the pressure-compensated valve by hydraulic fluid port.
Further, the valve body body also has load-sensitive hydraulic fluid port and load pressure input port, the valve body body
The second shuttle valve is inside additionally provided with, an oil inlet of second shuttle valve receives the input of the oil outlet of first shuttle valve, separately
One oil inlet receives the load pressure for joining valve body from operated adjacent inputted by the load pressure input port, and described the
The load pressure filtered out is output to the load-sensitive hydraulic fluid port by the oil outlet of two shuttle valves.
Further, two dampings are additionally provided with the valve body body, two load hydraulic fluid ports of the valve body body
Load pressure inputs to two oil inlets of first shuttle valve by described two dampings respectively.
Further, two the first overflow valves are additionally provided with the valve body body, valve body can be joined in the work and be in
Limit the load pressures of two load hydraulic fluid ports under working status respectively, the imports of described two first overflow valves is respectively with described the
Two oil inlets connection of one shuttle valve, exports the valve body oil return opening with the valve body body and connects.
Further, the oil inlet for being used for connecting oil feeding line is equipped with the valve body body of the first valve body and is used for
The oil return opening of oil return circuit is connected, is additionally provided with the valve body body of the first valve body for being exported to pump variable control mechanism
The drain tap of the load-sensitive output oil port of load-sensitive pressure and the load-sensitive pressure, also sets in the first valve body
Have the second overflow valve, the inlet and outlet of second overflow valve respectively with the oil inlet on the valve body body of the first valve body
Being connected with oil return opening, the load-sensitive output oil port is connected with the load-sensitive hydraulic fluid port of operated adjacent connection valve body, and described
Damping, the load-sensitive pressure are additionally provided between the load-sensitive hydraulic fluid port of load-sensitive output oil port and operated adjacent connection valve body
Drain tap pass through the solenoid directional control valve that is arranged in the first valve body and join the load-sensitive hydraulic fluid port of valve body with operated adjacent and connect
It is logical, and pass through the off-load of solenoid directional control valve control load-sensitive pressure.
Further, dynamic is additionally provided with the load-sensitive output oil port on the valve body body of the first valve body to hinder
Buddhist nun.
Further, the 3rd overflow valve, the inlet and outlet of the 3rd overflow valve are additionally provided with the first valve body
Connected respectively with the oil return opening in the control port of second overflow valve and the valve body body of the first valve body, described
Damping is additionally provided between oil inlet on the valve body body of the import of three overflow valves and the first valve body.
Further, the work connection valve body is additionally provided with manual control knobs, realizes that the master in the work connection valve body changes
Manual control to valve.
Further, the first valve body, tail connection valve body and at least one work connection valve body are joined by stud nut
Connect, and the O-ring of sealing is set between each valve body.
To achieve the above object, the present invention provides a kind of arm support hydraulic control system, including with pump control mechanism
Variable pump assembly and hydraulic oil container, wherein, foregoing proportional multi-way valve is further included, the proportional multi-way valve is joined by each work
The load hydraulic fluid port of valve body provides work fluid for each related executive component of arm support.
To achieve the above object, the present invention provides a kind of concrete mixer, including arm support and executive component, wherein, also
Including foregoing arm support hydraulic control system.
Based on above-mentioned technical proposal, the present invention adds pressure reducing valve in tail connection, using pressure reducing valve to carrying out autonomous oil feeding line
Hydraulic oil depressurized to obtain satisfactory pilot control oil, and be supplied to each work to join valve body pilot control oil
Main reversing valve, to realize electrichydraulic control function.The pressure reducing valve that the present invention is set in being joined by tail can be that proportional multi-way valve saves
The configuration of external guide's oil pump is gone, and avoids setting guide structure in first as far as possible, and causes valve volume larger, is added
The problem of work is complicated, so as to optimize the pilot control structure of proportional multi-way valve.
Brief description of the drawings
Attached drawing described herein is used for providing a further understanding of the present invention, forms the part of the application, this hair
Bright schematic description and description is used to explain the present invention, does not form inappropriate limitation of the present invention.In the accompanying drawings：
Fig. 1 is the hydraulic principle schematic diagram of an embodiment of proportional multi-way valve of the present invention.
Fig. 2 is the valve body outline structural diagram of proportional multi-way valve embodiment of the present invention.
Fig. 3 is the outline structural diagram of the instantiation that tail joins valve body in proportional multi-way valve embodiment of the present invention.
Fig. 4 is the internal galleries schematic diagram of an instantiation of first valve body in proportional multi-way valve embodiment of the present invention.
Embodiment
Below by drawings and examples, technical scheme is described in further detail.
As shown in Figure 1, the hydraulic principle schematic diagram of the embodiment for proportional multi-way valve of the present invention.With reference to shown in Fig. 2
Valve body contour structures, the proportional multi-way valve in the present embodiment include first valve body 21, tail connection valve body 23 and are arranged on first valve body
At least one work connection valve body 22 between 21 and tail connection valve body 23.In the present embodiment, the not simple lid of tail connection valve body 23
Harden structure, but the pressure reducing valve 14 for being capable of providing pilot control oil, the entrance of pressure reducing valve 14 and main confession are set in tail joins valve body
Oily oil communication, and the outlet of pressure reducing valve 14 and the pilot control oil circuit of the main reversing valve 12 at least one work connection valve body 22
Connection, the main reversing valve 12 in valve body 22 is joined to each work and provides pilot control oil, realizes electrichydraulic control.
It is coupled in above-mentioned tail in structure, the pressure oil of the outlet of pump 1 first passes through P1 hydraulic fluid ports by the oil in each work connection valve body
Road reaches the entrance of the pressure reducing valve 14 in tail connection valve body 23, and by the decompression of pressure reducing valve 14, pressure reducing valve 14 will decompression by outlet
The pilot control oil for meeting pilot control oil pressure requirement afterwards passes through the oil between tail connection valve body 23 and each work connection valve body 22
Road is sent to the pilot control opening of each work connection valve body 22.And each work connection valve body 22 main reversing valve 12 can use than
Example pressure reducing valve a, b coordinates the size of input current signal to carry out ratio control, and the stroke of the spool of main reversing valve 12 can be with
The size of current signal is proportional, so as to reach the hydraulic fluid flow rate that proportional control passes through the main reversing valve 12.Join in tail
On valve body 23 in addition to pressure reducing valve 14 is set, the drain tap L of whole proportional multi-way valve, oil return inlet T 2 and external can also be set
Guide's hydraulic fluid port A0 etc..
In installing for proportional pressure-reducing valve, can the spring terminal of commutation connection valve body cover two proportional pressure-reducing valve a of installation,
B, and be in tilted layout.Pilot control oil can reach proportional pressure-reducing valve by the internal galleries that spring terminal covers, when ratio depressurizes
During valve no power, pressure oil cut-off.When proportional pressure-reducing valve is given electric signal, control pilot control that can be proportional is oily,
So as to the displacement of proportional control spool.In terms of the arrangement of proportional pressure-reducing valve, two proportional pressure-reducing valves a, b can be installed on
Proportional multi-way valve side so that structure is compacter, also allow on proportional pressure-reducing valve a, b electric wire arrangement.
It will be noted from fig. 1 that the proportional multi-way valve of the present embodiment can have it is multiple corresponding to different executive components
The corresponding executive component of three work connection valve bodies is oil cylinder 8,9,10 in work connection valve body, such as Fig. 1, and according to this implementation
The different application occasion of the proportional multi-way valve of example, the species and number of executive component and the requirement of corresponding load pressure can roots
Made choice according to needs, and each work connection valve body can use same or like internal structure and principle.
By taking 9 corresponding work of oil cylinder in Fig. 1 joins valve body as an example, work connection valve body includes valve body body, is arranged on valve body
Intrinsic main reversing valve 12,17 and first shuttle valve 16 of pressure-compensated valve, pressure-compensated valve 17 can carry out main reversing valve 12
Valve precompensation so that the front and rear pressure difference of main reversing valve 12 is constant, and then makes work connection flow and the spool of main reversing valve 12
Stroke is proportional, and unrelated with load.And the valve body body of work connection valve body has valve body oil inlet, valve body oil return opening and two
A load hydraulic fluid port A, B, two oil inlets of the first shuttle valve 16 are in the in running order lower valve body body of reception respectively of work connection
The input of the load pressure of two load hydraulic fluid ports A, B, the oil outlet of the first shuttle valve 16 export the load pressure filtered out to pressure
The spring side control chamber of force compensating valve 17.What the first shuttle valve 16 played is two load hydraulic fluid ports of relatively this work connection valve body structure
A, the pressure of B, and the effect that relatively large load pressure is exported is taken out, and larger load pressure is exported to pressure-compensated valve 17
Spring side control chamber, can stablize 17 both ends pressure difference of pressure-compensated valve, it is ensured that the compensation function of pressure-compensated valve 17 is stablized,
Reduce impact.
Existing work connection valve body structure mentioned above is generally required by spool cooperation position different from valve body come defeated
Go out corresponding loaded work piece pressure, such as when being currently in load condition, it is necessary to export A mouthfuls of load pressures for A mouthfuls, it is necessary to by valve
Core is moved to specific location, and to carry out coordinating with the structure on valve body can be by A mouthfuls of load pressure for the structure on spool
Power is drawn, and when being in load condition for B mouthful, then and needs spool moving another specific location, utilizes spool and valve body
Fit structure draws B mouthfuls of load pressure, in order to realize the extraction of the above-mentioned certain loads pressure under certain working status, often
Need to design complicated structure on valve body and spool, so as to add difficulty of processing.And in contrast, the present embodiment is used
The first shuttle valve load pressure screening structure in the case where work connection is in loaded state at the same time by two load hydraulic fluid ports
Pressure is all drawn, recycle the first shuttle valve filter out load pressure it is larger export, this function corresponds to spool and valve
The complexity of the fit structure of body is much lower, reduces difficulty of processing accordingly.
Except by the way of load pressure is drawn from single work connection valve body and in addition to structure, shuttle valve can also be used
The load pressure that each work connection valve body is drawn is compared by network, quick as loading to filter out maximum load pressure
Sense signal is supplied to the variable control mechanism of pump.To realize this function, it can join to set on the body of valve body in each work and bear
Sensitive hydraulic fluid port and load pressure input port are carried, correspondingly, the second shuttle valve 18 is set in valve body body, one of the second shuttle valve 18
Oil inlet receives the input of the oil outlet of first shuttle valve 16, another oil inlet is received by being inputted from load pressure input port
Load pressure from operated adjacent connection valve body, the oil outlet of the second shuttle valve 18 is using the load pressure filtered out as load-sensitive
Pressure output is to load-sensitive hydraulic fluid port.
It will be noted from fig. 1 that the second shuttle valve 18 of leftmost work connection valve body to the maximum load pressure of this connection (i.e.
The maximum load pressure of A, B mouthfuls of this connection filtered out by the first shuttle valve 16) and tail connection oil return circuit pressure be compared, to sieve
Select maximum load pressure it is adjacent to right side as load-sensitive pressure transmission work join in the second shuttle valve 18, so by
Connection compares, and feeds back to the variable control mechanism of pump 1 by first in the maximum load-sensitive pressure of the work connection output of the rightmost side.
In addition, being additionally provided with two dampings in the valve body body of work connection valve body, 15 and damping 19 are respectively damped, respectively
Corresponding to load hydraulic fluid port A, B, the load pressure of load hydraulic fluid port A, B input to the first shuttle valve 16 through overdamp 15 and damping 19 respectively
Two oil inlets.Damping 15 and damping 19 can be to carrying out the compression shock of self-supported hydraulic fluid port A, B into row buffering.
In order to limit highest system pressure of the spool of main reversing valve 12 at left and right operating position, may be used also in valve body body
, can be negative in the in running order lower limitation respectively two of work connection valve body further to set two the first overflow valves 13,11
Carry the load pressure of hydraulic fluid port A, B, two oil inlets of the imports of two the first overflow valves 13,11 respectively with the first shuttle valve 16 connect
Logical, outlet is connected with the valve body oil return opening of valve body body.It is right that first overflow valve 13,11 can join valve body institute according to each work
Different preset pressures is arrived in the difference for the load answered, setting.
For the main reversing valve 12 for the connection valve body that works in embodiment illustrated in fig. 1, when spool is switched to left position work
When, the oil inlet of work connection valve body is connected with load hydraulic fluid port A, and oil cylinder 9 can be entered by carrying out the hydraulic oil of autonomous oil inlet oil circuit
Rodless cavity, and the oil return opening for the connection valve body that works is connected with load hydraulic fluid port B, the hydraulic oil of the rod chamber of oil cylinder 9 will pass through oil return opening
Fuel tank is flowed back to, loads hydraulic fluid port A at this time also by the oil inlet and the first overflow valve 13 with the first shuttle valve 16 respectively of damping 15
Inlet communication, and load hydraulic fluid port B and pass through 19 another oil inlet and the first overflow valve 11 with the first shuttle valve 16 respectively of damping
Inlet communication.And when spool is switched to right position work, the oil inlet of work connection valve body is connected with load hydraulic fluid port B, is come from
The hydraulic oil of main oil inlet oil circuit can enter the rod chamber of oil cylinder 9, and the oil return opening for the connection valve body that works connects with load hydraulic fluid port A
Logical, the hydraulic oil of the rodless cavity of oil cylinder 9 will flow back to fuel tank by oil return opening, load hydraulic fluid port A at this time still through the difference of damping 15
With an oil inlet of the first shuttle valve 16 and the inlet communication of the first overflow valve 13, and load hydraulic fluid port B still through damping 19 points
Not with another oil inlet of the first shuttle valve 16 and the inlet communication of the first overflow valve 11.In the spool of main reversing valve 12 is in
During position, load hydraulic fluid port A, B are in the state disconnected, and two oil inlets of the first shuttle valve 16 are interconnected, and are connected to valve body
The oil return opening of body, the load-sensitive pressure that the connection valve body of the work at this time is exported is return pressure.
Carry out illustratively first valve body 21 in conjunction with Fig. 1 below.It is equipped with the valve body body of first valve body 21 and is used to connect
The oil inlet P 1 of oil feeding line and the oil return inlet T 1 for connecting oil return circuit are connect, is also set on the valve body body of first valve body 21
It is useful for the load-sensitive output oil port LS from the variable control mechanism output loading sensitive pressure to pump 1 and load-sensitive pressure of
Drain tap, the drain tap join the drain tap L on valve body with tail by the oil duct in each valve body and communicate.Also set in first valve body 21
Have the second overflow valve 5, the inlet and outlet of the second overflow valve 5 respectively with the oil inlet P 1 on the valve body body of first valve body 21 and
Oil return inlet T 1 connects, and load-sensitive output oil port LS is connected with the load-sensitive hydraulic fluid port of operated adjacent connection valve body, and quick loading
Damping 3, the draining of load-sensitive pressure are additionally provided between the load-sensitive hydraulic fluid port of sense output oil port LS and operated adjacent connection valve body
Mouth is connected by the solenoid directional control valve 7 being arranged in first valve body 21 with the load-sensitive hydraulic fluid port of operated adjacent connection valve body, and is led to
Cross the off-load that solenoid directional control valve 7 controls load-sensitive pressure.
, can be in first valve in order to alleviate the impact that the change of load-sensitive pressure causes the variable control mechanism to pump 1
Dynamic antivibration 2 is set at the load-sensitive output oil port LS on the valve body body of body 21.Furthermore it is also possible to set in first valve body
The 3rd overflow valve 6 is put, and with the second overflow valve 5 for main overflow valve, the 3rd overflow valve 6 is secondary overflow valve.Wherein, the 3rd overflow
The inlet and outlet of valve 6 respectively with the oil return inlet T 1 in the control port of the second overflow valve 5 and the valve body body of first valve body 21
Connect, damping 4 is additionally provided between the oil inlet P 1 in the import of the 3rd overflow valve 6 and the valve body body of first valve body 21.
When pump 1 is input in first valve body 21 by the oil inlet P 1 of first valve body 21, the pressure of oil inlet P 1 connects second
Overflow valve 5, while the pressure of oil inlet P 1 is followed by the 3rd overflow valve 6 by damping 4, by 6 off-load of the 3rd overflow valve, so as to control
5 off-load of the second overflow valve is made, hydraulic oil reaches oil return inlet T 1 after off-load.The load-sensitive pressure obtained from operated adjacent connection valve body
(i.e. LS pressure) is drawn through damping 3, dynamic antivibration 2, is connected to the control mouth of the variable control mechanism of pump 1, so as to control pump 1
After displacement variation, makes 1 output flow of pump meet the flow needed for system, and dynamic antivibration 2 alleviates LS compression shocks
1 control mouth of pump is re-introduced to, improves the stability of system and handling.On the other hand, LS pressure reaches solenoid directional control valve 7, leads to
The break-make of solenoid directional control valve 7 is crossed to control the off-load of LS pressure.
With reference to figure 2, manual control knobs can also be set on work connection valve body 22, to realize in work connection valve body 22
The manual control of main reversing valve 12.The concrete structure of handle can include handle end cap, handle, handle set, axis, ball head connecting rod,
Push rod etc., simple in structure, easy to operate, also sealed reliable.The quantity of work connection valve body can be according to the system need of practical application
Ask to determine, and first valve body 21, tail connection valve body 23 and at least one work connection valve body 22 can be joined by stud nut
Connect, such as 24 one end of studs is screwed in into first valve body 21, one end is tightened by nut 25.In first valve body 21, tail connection valve
The O-ring of sealing can also be set between each adjacent valve body of body 23 and each work connection valve body 22.
As shown in figure 3, join the contour structures of an instantiation of valve body for tail in proportional multi-way valve embodiment of the present invention
Schematic diagram.In the contour structures of tail connection valve body, through hole 42,44,47 is provided with the valve body body 41 of tail connection valve body, for pacifying
Studs is filled, and pressure reducing valve 45 can be installed on the end face of tail connection valve body, valve body body 41 of the pressure oil from tail connection valve body
On oil inlet P enter, after pressure reducing valve 45, to it is each offer pilot pressure, pressure reducing valve 45 can use inserting valve arrangement.Scheming
Element in 3 marked as 43,46 is the plug on valve body body 41.
As shown in figure 4, the internal galleries for an instantiation of first valve body in proportional multi-way valve embodiment of the present invention
Schematic diagram.With reference to the hydraulic schematic diagram of the first valve body on right side in Fig. 1, it can be seen that the pressure oil from pump 1 is from oil inlet P 1
Into by 33 internal galleries of spool of the second overflow valve 5, reaching its left end, while pressure oil passes through damping 4 and reaches main overflows
Valve core 33 carries the right end of 35 side of spring, and plug 36 then plays the role of spring end cap, while pressure oil is from the second overflow
The internal galleries of valve body body 32 of 33 right end of spool through first valve body 21 of valve 5 reach one end of the 3rd overflow valve 6, work as pressure
When reaching the set pressure of the 3rd overflow valve 6, pressure off-load, so that 5 off-load of the second overflow valve.Enter at the same time from oil inlet P 1
Pressure oil is drawn from the inside hydraulic fluid port of the valve body body 32 of first valve body 21, and pressure oil is provided to each work connection valve body.Oil return
Mouth T1 is then communicated by the inside hydraulic fluid port of the valve body body 32 of first valve body 21 with the oil return opening of each work connection valve body.And LS pressure
Solenoid directional control valve 7 is reached, is commutated by solenoid directional control valve 7, control LS pressure carries out off-load.Solenoid directional control valve 7 can also use spiral shell
Line inserted valve form.The element marked as 31,34 is the plug on valve body body 32 in Fig. 4.
Each embodiment of the invention described above proportional multi-way valve can be applied to all kinds of hydraulic control systems, such as apply in arm
In frame hydraulic control system, i.e., a kind of arm support hydraulic control system, including variable pump assembly and hydraulic pressure with pump control mechanism
Fuel tank, further includes the embodiment of any proportional multi-way valve noted earlier, and proportional multi-way valve joins valve body by each work
Load hydraulic fluid port provide work fluid for each related executive component of arm support.The arm support hydraulic control system can also be applied to all kinds of
Using the engineering mechanical device of arm support, such as concrete mixer, i.e., a kind of concrete mixer, including arm support and executive component, also
Including foregoing arm support hydraulic control system.
Finally it should be noted that:The above embodiments are merely illustrative of the technical scheme of the present invention and are not intended to be limiting thereof；To the greatest extent
The present invention is described in detail with reference to preferred embodiments for pipe, those of ordinary skills in the art should understand that：Still
It can modify to the embodiment of the present invention or equivalent substitution is carried out to some technical characteristics；Without departing from this hair
The spirit of bright technical solution, it should all cover among the claimed technical solution scope of the present invention.
Claims (12)
1. a kind of proportional multi-way valve, including first valve body, tail join valve body and are arranged between first valve body and tail the connection valve body
At least one work connection valve body, it is characterised in that is equipped with pressure reducing valve, the entrance of the pressure reducing valve and master in tail connection valve body
Oil feeding line connects, so that pressure oil is by the pressure reducing valve in the oil duct arrival tail connection valve body in each work connection valve body
Entrance, the outlet of the pressure reducing valve and the pilot control oil communication of the main reversing valve at least one work connection valve body,
The pilot control oil for meeting pilot control oil pressure requirement after decompression is joined valve body by the pressure reducing valve by exporting by the tail
The oil duct joined with each work between valve body is sent to the pilot control opening of each work connection valve body, to join to each work in valve body
Main reversing valve provide pilot control oil, realize electrichydraulic control.
2. proportional multi-way valve according to claim 1, it is characterised in that the work connection valve body includes valve body body, sets
Put in the intrinsic main reversing valve of the valve body, pressure-compensated valve and the first shuttle valve, the pressure-compensated valve is to the main commutation
Valve carries out valve precompensation, and the valve body body has valve body oil inlet, valve body oil return opening and two load hydraulic fluid ports, first shuttle
Two oil inlets of valve are in the in running order lower two load oil for receiving the valve body body respectively of work connection valve body
The input of the load pressure of mouth, the oil outlet of first shuttle valve export the load pressure filtered out to the pressure-compensated valve
Spring side control chamber.
3. proportional multi-way valve according to claim 2, it is characterised in that the valve body body also has load-sensitive hydraulic fluid port
With load pressure input port, the second shuttle valve is additionally provided with the valve body body, an oil inlet of second shuttle valve receives
The input of the oil outlet of first shuttle valve, another oil inlet is received comes from phase by what the load pressure input port inputted
The load pressure of neighbour's work connection valve body, it is quick that the load pressure filtered out is output to the load by the oil outlet of second shuttle valve
Feel hydraulic fluid port.
4. the proportional multi-way valve according to Claims 2 or 3, it is characterised in that be additionally provided with two in the valve body body
Damping, the load pressure of two load hydraulic fluid ports of the valve body body input to first shuttle by described two dampings respectively
Two oil inlets of valve.
5. the proportional multi-way valve according to Claims 2 or 3, it is characterised in that two are additionally provided with the valve body body
One overflow valve, can join the in running order lower load pressure for limiting two load hydraulic fluid ports respectively of valve body, institute in the work
The import for stating two the first overflow valves is connected with two oil inlets of first shuttle valve respectively, outlet with the valve body body
Valve body oil return opening connection.
6. proportional multi-way valve according to claim 3, it is characterised in that be equipped with the valve body body of the first valve body
For connecting the oil inlet of oil feeding line and oil return opening for connecting oil return circuit, on the valve body body of the first valve body
It is additionally provided with for the load-sensitive output oil port to pump variable control mechanism output loading sensitive pressure and the load-sensitive pressure
The drain tap of power, is additionally provided with the second overflow valve in the first valve body, the inlet and outlet of second overflow valve respectively with
Oil inlet on the valve body body of the first valve body is connected with oil return opening, and the load-sensitive output oil port joins with operated adjacent
The load-sensitive hydraulic fluid port connection of valve body, and in the load-sensitive output oil port and the load-sensitive hydraulic fluid port of operated adjacent connection valve body
Between be additionally provided with damping, the drain tap of the load-sensitive pressure by the solenoid directional control valve that is arranged in the first valve body with
The load-sensitive hydraulic fluid port connection of operated adjacent connection valve body, and pass through the off-load of solenoid directional control valve control load-sensitive pressure.
7. proportional multi-way valve according to claim 6, it is characterised in that negative on the valve body body of the first valve body
Carry and be additionally provided with dynamic antivibration at sensitive output oil port.
8. proportional multi-way valve according to claim 6, it is characterised in that be additionally provided with the 3rd overflow in the first valve body
Valve, the inlet and outlet of the 3rd overflow valve respectively with the control port of second overflow valve and the valve of the first valve body
Oil return opening connection on body body, the oil inlet in the import of the 3rd overflow valve and the valve body body of the first valve body
Between be additionally provided with damping.
9. proportional multi-way valve according to claim 1, it is characterised in that the work connection valve body is additionally provided with control hand manually
Handle, realizes the manual control of the main reversing valve in the work connection valve body.
10. proportional multi-way valve according to claim 1, it is characterised in that the first valve body, tail connection valve body and at least one
A work connection valve body is coupled by stud nut, and the O-ring of sealing is set between each valve body.
11. a kind of arm support hydraulic control system, including variable pump assembly and hydraulic oil container with pump control mechanism, its feature exist
In further including any proportional multi-way valve of claim 1~10, the proportional multi-way valve passes through each work and joins valve body
Load hydraulic fluid port provides work fluid for each related executive component of arm support.
12. a kind of concrete mixer, including arm support and executive component, it is characterised in that further include the arm described in claim 11
Frame hydraulic control system.
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Families Citing this family (12)
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|---|---|---|---|---|
| CN106762905B (en) * | 2016-12-27 | 2018-05-25 | 恒天九五重工有限公司 | Pilot hydraulic control system and drilling machine based on multi-joint shuttle valve group |
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| CN108679014B (en) * | 2018-08-03 | 2024-08-06 | 中国铁建重工集团股份有限公司 | Drilling machine and full-hydraulic manual control valve station thereof |
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Family Cites Families (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3443354A1 (en) * | 1984-11-28 | 1986-05-28 | Robert Bosch Gmbh, 7000 Stuttgart | HYDRAULIC SYSTEM |
| DE4432850C1 (en) * | 1994-09-15 | 1995-08-31 | Daimler Benz Ag | Automatic gear changing control for vehicle automatic transmission |
| CN201326773Y (en) * | 2008-12-04 | 2009-10-14 | 中山市钜通机电技术有限公司 | Proportion multitandem valve |
| CN102032233B (en) * | 2011-01-08 | 2013-05-15 | 四川省宜宾普什驱动有限责任公司 | Multifunctional proportional multi-way valve |
| CN102506030B (en) * | 2011-09-26 | 2014-11-19 | 三一重型装备有限公司 | Multi-way valve and tunnel boring machine |
| CN202612725U (en) * | 2012-05-24 | 2012-12-19 | 圣邦有限公司 | Electro-hydraulic proportional control multi-way valve |
| CN103047208B (en) * | 2012-12-27 | 2015-02-18 | 徐工集团工程机械股份有限公司江苏徐州工程机械研究院 | Load-sensitive electro-hydraulic proportional multi-way valve |
| CN203114764U (en) * | 2012-12-27 | 2013-08-07 | 徐工集团工程机械股份有限公司江苏徐州工程机械研究院 | Load-sensitive electro-hydraulic proportional multi-way valve |
| CN103267147B (en) * | 2013-05-28 | 2015-02-11 | 卢宇 | Small-flow high-pressure load sensitive proportional multi-way valve |
| CN103771305B (en) * | 2014-01-16 | 2016-04-20 | 杭州爱知工程车辆有限公司 | A kind of hydraulic control proportionality velocity modulation energy-saving control system for aerial platform and control method thereof |
| CN204099323U (en) * | 2014-08-12 | 2015-01-14 | 徐工集团工程机械股份有限公司 | Proportional multi-way valve, jib hydraulic control system and concrete mixer |
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