CN207406559U - Torque distributing valve and wheel walking hydraulic control system - Google Patents
Torque distributing valve and wheel walking hydraulic control system Download PDFInfo
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- CN207406559U CN207406559U CN201721517156.2U CN201721517156U CN207406559U CN 207406559 U CN207406559 U CN 207406559U CN 201721517156 U CN201721517156 U CN 201721517156U CN 207406559 U CN207406559 U CN 207406559U
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- 230000006837 decompression Effects 0.000 claims abstract description 123
- 239000012530 fluid Substances 0.000 claims abstract description 35
- 230000009471 action Effects 0.000 claims abstract description 7
- 238000013016 damping Methods 0.000 claims description 24
- 239000002828 fuel tank Substances 0.000 claims description 8
- 239000007788 liquid Substances 0.000 claims description 8
- 230000002093 peripheral effect Effects 0.000 claims description 7
- 230000008859 change Effects 0.000 claims description 6
- 238000005192 partition Methods 0.000 claims description 6
- 239000000446 fuel Substances 0.000 claims description 5
- 239000003921 oil Substances 0.000 description 224
- 238000010586 diagram Methods 0.000 description 5
- 239000010720 hydraulic oil Substances 0.000 description 5
- 230000006835 compression Effects 0.000 description 4
- 238000007906 compression Methods 0.000 description 4
- 230000000694 effects Effects 0.000 description 4
- 230000005611 electricity Effects 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 1
- 230000000903 blocking effect Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 238000005213 imbibition Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000001502 supplementing effect Effects 0.000 description 1
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Abstract
The utility model provides a kind of torque distributing valve, including valve pocket, the spool being housed in valve pocket and the resetting spring being housed in valve pocket, spool includes first end and the second end opposite with first end, resetting spring provides pretightning force to the second end of spool, valve pocket is equipped with return port, decompression/overflow valve port and oil inlet valve port, the pressure of oil inlet valve port acts on the first end of spool after the decompression of spool ratio, the pressure of decompression/overflow valve port acts directly on the second end of spool through spool, and depressurize/pressure of overflow valve port enters decompression/overflow valve mouth by the fluid of oil inlet valve port and formed, return port is controlled under the action of the pressure that spool is subject at both ends, connected relation between decompression/overflow valve port and oil inlet valve port, the pressure of decompression/overflow valve port is made to be equal to pressure of the pressure of oil inlet valve port after the decompression of spool ratio.Above-mentioned torque distributing valve can carry out reasonable distribution to fluid.The utility model further relates to a kind of wheel walking hydraulic control system.
Description
Technical field
The utility model is related to technical field of hydraulic, more particularly to a kind of torque distributing valve and wheel walking hydraulic pressure
Control system.
Background technology
Self-travel type haulage equipment uses two hydraulic motors to be together in series and provides driving force for driving wheel.Self-travel type
Haulage equipment is not only straight line moving, it is necessary to turn in necessary occasion when mobile, left side drive wheel during turning
It is different with the radius of turn of right side drive wheel, drive the rotating speed of the left motor of driving wheel and the right motor of driving right side drive wheel
Rotating speed it is inconsistent.Assuming that in hydraulic control system, hydraulic pressure first flows into left motor and then is flowing into right motor, when vehicle to
During left-hand rotation, the rotating speed of left motor is less than the rotating speed of right motor, and hydraulic pressure can not meet the demand of right motor, and right motor will be inhaled
Sky, so that right motor generates shriek；When vehicle is turned right, the hydraulic pressure of left side motor outflow is far longer than right motor
Soakage can thus form on left motor and build the pressure, seriously reduce right motor life.
As shown in Figure 1, in the prior art, in order to solve the problems, such as motor suction in hydraulic system, usually in two horses
A unidirectional Fill valve is connected between reaching, but the technological means can not solve the problems, such as that motor builds the pressure.
As shown in Fig. 2, in the prior art, in order to solve the problems, such as that motor builds the pressure in hydraulic system, usually in two horses
Connect overflow valve between reaching, to reduce the phenomenon that builds the pressure, but immobilize after the pressure setting of overflow valve, it is impossible to the variation of load
And change, can also generate it is certain build the pressure, and cannot completely eliminate and build the pressure.
Utility model content
Based on this, it is necessary to provide a kind of torque distributing valve, apply in wheel walks hydraulic control system, to solve two
Build the pressure problem and the suction problem occurred during a motor series connection.
The pressure that the utility model provides the oil inlet valve port passes through spool ratio depressurization the first of the spool
End, the pressure of the decompression/overflow valve port act directly on the second end of the spool by spool, and the decompression/overflow
The pressure for flowing valve port is formed by the fluid of the oil inlet valve port after the decompression of spool ratio into the decompression/overflow valve mouth,
The first end of the spool is identical with the pressure application surface product of second end, and the spool is under the action of the pressure at two ends described in control
Connected relation between return port, the decompression/overflow valve port and the oil inlet valve port, makes the decompression/overflow valve port
Pressure be equal to pressure of the pressure Jing Guo first end of the spool ratio depressurization in the spool of the oil inlet valve port.
Further, the valve pocket acts on the control chamber of the spool first end equipped with pressure and pressure acts on institute
The feedback cavity of spool second end is stated, is equipped with described in the first oil duct connected with the oil inlet valve port and connection and subtracts in the spool
Second oil duct of pressure/overflow valve port and the feedback cavity, the first end of the spool be equipped with connect first oil duct with it is described
First damping hole of control chamber is additionally provided with second for connecting with the control chamber and being connected with the return port on the valve pocket
Damping hole.
Further, first damping hole is equal with the liquid resistance of second damping hole.
Further, the peripheral wall of the spool is equipped with the first oil groove, first oil groove along the spool it is axial to
The both ends extension of the spool, first oil groove are connected with second oil duct, first oil groove and the decompression/overflow
Valve port connects, and the decompression/overflow valve port is connected by first oil groove with the return port and oil inlet valve port, described
Spool controls the conducting and partition of first oil groove and the return port under the action of pressure at two ends, and controls described the
The conducting and partition of one oil groove and the oil inlet valve port.
Further, the peripheral wall of the spool is additionally provided with the second oil groove, in the axial direction of the spool, second oil groove
It is arranged at intervals with first oil groove, first oil duct is connected by second oil groove with the oil inlet valve port.
Further, the first end of the spool is equipped with orifice plug, and first damping hole is arranged on the orifice plug.
Further, filter screen is equipped in first oil duct.
The utility model also provides a kind of wheel walking hydraulic control system, including：
Three-way four-position solenoid directional control valve, for controlling the advance of self-travel type haulage equipment and retrogressing, including main oil inlet,
Main oil return opening, work oil inlet and work oil return opening, main oil inlet and the hydraulic pump of the three-way four-position solenoid directional control valve connect
It connects, the main oil return opening of the three-way four-position solenoid directional control valve is connected with fuel tank；
First motor and the second motor being connected in series with first motor, first motor and the three-way four-position
The work oil inlet connection of solenoid directional control valve, the work oil return opening of second motor and the three-way four-position solenoid directional control valve connect
It connects；
Shuttle valve, including the first oil inlet, the second oil inlet and oil outlet, the first oil inlet and the threeway of the shuttle valve
The work oil inlet connection of four solenoid directional control valves, the work of second oil inlet of shuttle valve and the three-way four-position solenoid directional control valve
Make oil return opening connection；
Above-mentioned torque distributing valve, the oil inlet valve port are connected with the oil outlet of the shuttle valve, the return port and oil
Case connects, and the decompression/overflow valve port is connected between first motor and second motor.
Further, further include two four-way electromagnetic reversing valves, two four-way electromagnetic reversing valves include main oil inlet,
Main oil return opening, work oil inlet and work oil return opening, wherein, the main oil inlet and described three of two four-way electromagnetic reversing valves
The work oil return opening connection of logical four solenoid directional control valves, work oil return opening and the threeway of two four-way electromagnetic reversing valves
The work oil inlet connection of four solenoid directional control valves, one end of first motor and the work of the three-way four-position solenoid directional control valve
Make oil inlet connection, the other end of first motor is connected with the work oil inlet of two four-way electromagnetic reversing valves, institute
One end of the second motor is stated to be connected with decompression/overflow valve port of the torque distributing valve, one end of second motor also with institute
The main oil return opening connection of two four-way electromagnetic reversing valves is stated, the other end of second motor is connected to the three-way four-position electromagnetism
On the work oil return opening of reversal valve, when two four-way electromagnetic reversing valves power off, first motor and second motor
Series connection.
Further, 2/2-way solenoid valve is further included, the 2/2-way solenoid valve is connected to second motor
Between the decompression of one end and the torque distributing valve/overflow valve port, in the 2/2-way solenoid valve and described two four energizations
When magnetic reversal valve powers on simultaneously, first motor is connected in parallel with second motor, and the 2/2-way solenoid valve is closed,
Disconnect the connection between decompression/overflow valve port of the torque distributing valve and one end of second motor.
The application of Pass through above-mentioned technical proposal, the utility model have the following advantages that compared to the prior art：
Torque distributing valve and wheel the walking hydraulic control system of the utility model, can be according to decompression/overflow valve port
Pressure change, the connected relation of adjustment decompression/between overflow valve port and oil inlet valve port and the opening and closing of return port, and
When decompression/overflow valve port becomes larger, the connection of decompression/overflow valve port and oil inlet valve port is blocked, return port is opened, decompression/
Fluid in overflow valve port flows back to fuel tank through return port, in decompression/overflow valve port, increases decompression/overflow valve port and inlet valve
Connection area between mouthful, while return port is closed, the fluid of oil inlet valve port is made to pass through the external system of portion of decompression/overflow valve port
System provides fluid, so as to fulfill the distribution to torque.
Description of the drawings
Fig. 1 and Fig. 2 is wheel walking hydraulic control system of the prior art.
Fig. 3 is the structure diagram of the torque distributing valve of the utility model.
Fig. 4 is the function schematic symbol diagram of the torque distributing valve of the utility model.
Fig. 5 and Fig. 6 is the torque distribution principle schematic diagram of the torque distributing valve of the utility model.
Fig. 7 is enlarged drawing at the V in Fig. 6.
Fig. 8 is the pressure distribution principle figure of the control chamber in the torque distributing valve of the utility model.
Fig. 9 is the structure diagram of the wheel walking hydraulic control system of the utility model first embodiment.
Figure 10 is the structure diagram of the wheel walking hydraulic control system of the utility model second embodiment.
Specific embodiment
The following is a combination of the drawings in the embodiments of the present utility model, and the technical scheme in the embodiment of the utility model is carried out
It clearly and completely describes, it is clear that described embodiment is the implementation of the utility model part of the embodiment rather than whole
Example.Based on the embodiment in the utility model, those of ordinary skill in the art are obtained without making creative work
The every other embodiment obtained, shall fall within the protection scope of the present invention.
Incorporated by reference to reference to Fig. 3-6, the utility model provides a kind of torque distributing valve 100, including valve pocket 1, is housed in valve
Cover the spool 2 in 1 and the resetting spring 3 being housed in valve pocket 1.Spool 2 includes first end and the second end opposite with first end,
Resetting spring 3 provides pretightning force to the second end of spool 2.Valve pocket 1 be equipped with return port B1, decompression/overflow valve port C1 and into
The pressure of fuel tap mouth A1, oil inlet valve port A1 act on the first end of spool 2, decompression/overflow valve port after the decompression of spool ratio
The pressure of C1 acts directly on the second end of spool 2 by spool, and depressurize/pressure of overflow valve port C1 is by oil inlet valve port A1
Fluid formed after the decompression of spool ratio into decompression/overflow valve port C1.The pressure of the first end and second end of spool 2 is made
Identical with area, spool 2 controls return port B1, decompression/overflow valve port C1 and oil inlet valve port under the action of pressure at two ends
Connected relation between A1 makes pressure of the pressure of decompression/overflow valve port C1 equal to oil inlet valve port A1 be depressurized by spool ratio
Act on the pressure of the first end of spool 2.
It is understood that although the pressure of decompression/overflow valve port C1 enters decompression/overflow by the fluid of oil inlet valve port A1
Valve port C1 is formed, but torque distributing valve 100 is when being applied in hydraulic system, if the hydraulic-driven part in hydraulic system
Needing fluid demand, supply exceed demand, and the pressure of decompression/overflow valve port C1 is influenced to become larger suddenly be subject to external oil pressure, at this time valve
The pressure that 2 second end of core is subject to becomes larger, and spool 2 will be moved to the direction where the first end of spool 2, make oil inlet valve port A1 with subtracting
Pressure/overflow valve port C1 connection area reductions or both directly separate, and decompression/overflow valve port C1 is connected with return port B1, is returned
Fuel tap mouth B1 is opened, and extra fluid enters return port B1 through decompression/overflow valve port C1 in hydraulic system, then by return port
B1 oil return boxes, while depressurize/pressure of overflow valve port C1 reduces, the pressure of decompression/overflow valve port C1 is made to be equal to oil inlet valve port A1
Pressure through 2 ratio of spool decompression after pressure.On the contrary, if the hydraulic-driven part in hydraulic system needs fluid demand
Measure supply-less-than-demand, the pressure of decompression/overflow valve port C1 influenced to become smaller suddenly be subject to external oil pressure, at this time 2 second end of spool by
To pressure become smaller, spool 2 will to where the second end of spool 2 direction movement, make oil inlet valve port A1 and decompression/overflow valve port
C1 is connected or connection area increase, while the connection area of decompression/overflow valve port C1 and return port B1 is made to reduce or will
Return port B1 is closed, and the fluid of oil inlet valve port A1 is more externally exported into decompression/overflow valve port C1, while increase subtracts
The pressure of pressure/overflow valve port C1 makes pressure of the pressure equal to oil inlet valve port A1 of decompression/overflow valve port C1 subtract through 2 ratio of spool
Pressure after pressure.
In the present embodiment, when the torque distributing valve 100 of the utility model does not access oil pressure, that is, torque distributing valve
100 when in original state, and spool 2 opens return port B1, decompression/overflow under the pretightning force effect of resetting spring 3
Valve port C1 is turned on return port B1, while separates decompression/overflow valve port C1 and oil inlet valve port A1, that is, decompression/overflow
Cannot circulate fluid between valve port C1 and oil inlet valve port A1.It should be noted that the rigidity of resetting spring 3 is smaller, compression stress is firm
The gravity of spool 2 can be resisted well, 2 installation direction of spool is avoided to influence the position of spool 2, while the compression stress of resetting spring 3 is remote
Hydraulic pressure much smaller than fluid acts on the power that is generated on the active area of spool 2, thus resetting spring 3 functions only as resetting
Effect, further compression stress can be ignored.
Specifically, valve pocket 1 includes first end and the second end opposite with first end, return port B1, decompression/overflow valve port
C1 and oil inlet valve port A1 are successively set between the first end of valve pocket 1 and the second end of valve pocket 1.Valve pocket 1 is acted on equipped with pressure
The feedback cavity 12 of 2 second end of spool is acted in the control chamber 11 and pressure of 2 first end of spool, it is preferable that control chamber 11
Arranged on the first end of valve pocket 1, feedback cavity 12 is arranged on the second end of valve pocket 1, and the first end of spool 2 is housed in control chamber 11, makes
The pressure of control chamber 11 acts on the first end of spool 2, and the second end of spool 2 is housed in feedback cavity 12, makes feedback cavity 11
Pressure acts on the second end of spool 11.Be equipped with the first oil duct 21 connect with oil inlet valve port A1 in spool 2 and connection depressurize/
Overflow valve port C1 and the second oil duct 22 of feedback cavity 12, the first end of spool 2 are equipped with the first oil duct of connection 21 and control chamber 11
First damping hole 23.The second damping hole 13 for connecting with control chamber 11 and being connected with return port B1 is additionally provided on valve pocket 2.So
It sets, the pressure of inlet valve mouth A1 can be caused to pass through a certain proportion of depressurization in the first end of spool 2, decompression/overflow
The pressure of valve port C1 acts directly on the second end of spool 2, and can determine oil inlet valve port according to knowwhy is hindered according to liquid
The decompression ratio of A1, fluid, into the first oil duct 21, then enter control chamber 11, together through oil inlet valve port A1 through the first damping hole 23
When fluid also return to return port B1 by the second damping hole 13, then oil return box, in the process, as shown in figure 8, the first resistance
23 and second damping hole 13 of Buddhist nun hole and control chamber 11 form a hydraulic half-bridge, by the first damping hole 23 and the second damping hole 13
Liquid resistance is assumed to be R respectively1、R2, the pressure of control chamber 11 is PK, then hindering knowwhy according to liquid can obtain：PK=PL×
R1 2/R1 2+R2 2, in R1With R2Value determine after, and the interior pressure P of the first oil duct 21LIt is identical with the pressure of oil inlet valve port A1, it can be with
Determine the pressure proportional relation of the pressure and oil inlet valve port A1 in control chamber 11, and PKWith PLVariation and change, if R1
=R2, then the pressure P of decompression/overflow valve port C1KEqual to the pressure half of oil inlet valve port A1, i.e. the pressure of oil inlet valve port A1 passes through
The first end of spool 2 is acted on after the decompression half of spool 2.
In the present embodiment, the first damping hole 23 is equal with the liquid resistance of the second damping hole 13, the pressure warp of oil inlet valve port A1
Spool 2 depressurize half after act on the first end of spool 2, while make the pressure of decompression/overflow valve port C1 be equal to oil inlet valve port
The pressure half of A1.In other embodiments, the first damping hole 23 can not also be identical with the liquid resistance of the second damping hole 13.
In the present embodiment, the peripheral wall of spool 2 is equipped with the first oil groove 24, and the first oil groove 24 is along spool 2 axially to valve
The both ends extension of core 2, the first oil groove 24 are connected with the second oil duct 22, and the first oil groove 24 is connected with decompression/overflow valve port C1, is subtracted
Pressure/overflow valve port C1 is connected by the first oil groove 24 with return port B1 and oil inlet valve port A1, and spool 2 is in the work of pressure at two ends
With the lower conducting for controlling the conducting and partition of the first oil groove 24 and return port B1, and controlling the first oil groove 24 and oil inlet valve port A1
With partition.Specifically, the first oil groove 24 include first end and the second end opposite with first end, the first of the first oil groove 24
End connects for return port B1, and the second end of the first oil groove 24 with decompression/overflow valve port C1 for connecting, in torque distributing valve
100 original state, that is, when torque distributing valve 100 does not flow into fluid, 3 pretightning force of resetting spring is acted on spool 2, is made
The first end face return port B1 of first oil groove 24, return port B1 is opened, while is located at the second end of the first oil groove 24
Oil inlet valve port A1 separates the first oil groove 24 and oil inlet valve port A1 close to the outside of the one side of decompression/overflow valve port C1, spool 2,
So as to which decompression/overflow valve port C1 and oil inlet valve port A1 be separated, when the pressure that 2 first end of spool is subject to is more than the pressure of second end
When, when spool 2 is to direction movement where the second end of spool 2, the second end of the first oil groove 24 is moved to face with spool 2
During oil inlet valve port A1, the first oil groove 24 is connected with oil inlet valve port A1, and the first oil groove 24 forms one and the first oil groove 24 at this time
The pressure relief valve port A11 (as shown in Figure 7) of connection, and with the movement of spool 2, the first oil groove 24 is against the face of oil inlet valve port A1
Product is increasing, i.e. the circulation area of pressure relief valve port A11 is increasing, and the first end of the first oil groove 24 is as spool 2 is to valve
Direction movement where the second end of core 2, the first end and the facing area of return port B1 of the first oil groove 24 are less and less, directly
First end to the first oil groove 24 is moved to return port B1 close to the outside of the one side of decompression/overflow valve port C1, and spool 2 will return
Fuel tap mouth B1 is blocked with the first oil groove 24, and return port B1 is closed.The moving direction of spool 2 is on the contrary, then pressure relief valve port A11's is logical
Flow area tapers into, until spool 2 blocks the connection of the first oil groove 24 and oil inlet valve port A1, while return port B1 and the
The first end connection of one oil groove 24, and it is increasing to connect area.In the present embodiment, the first oil groove 24 is around the week of spool 2
The annular groove that wall opens up, with when installing spool 2, the first oil groove 24 can be connected easily with decompression/overflow valve port C1.At this
In example, the second oil duct 22 is set along the axial direction of spool 2, and one end of 2 second end of separate spool of the second oil duct 22 is for example set
There is the oil guiding hole 220 through spool 2, to realize that the second oil duct 22 is connected with the first oil groove 25.
In the present embodiment, the peripheral wall of spool 2 is additionally provided with the second oil groove 25, in the axial direction of spool 2, the second oil groove 25 with
First oil groove 24 is arranged at intervals, and the first oil duct 21 is connected by the second oil groove 25 with oil inlet valve port A1, to prevent leak-stopping oil.In this reality
In example, the first oil duct 21 is set along the axial direction of spool 2, and its one end is equipped with the peripheral wall oil guiding hole through spool 1, the first oil duct 21
It is connected by the oil guiding hole with the second oil groove 25.Second oil groove 25 is preferably annular groove.
In the present embodiment, the first end of spool 2 is equipped with orifice plug 26, and the first damping hole 23 is arranged on orifice plug 26.
Further, filter screen 27 is equipped in the first oil duct 21, to be carried out to the hydraulic oil in the first oil duct of oil inlet 21
Filter.
It should be noted that the torque distributing valve 100 of the utility model further includes valve deck 110, valve deck 110 is mounted on valve pocket
1 is equipped with one end of control chamber 11, and the both ends of valve pocket 1 are additionally provided with the elements such as valve pocket seal receptacle, the effect of valve pocket seal receptacle and installation side
Formula is the general technology of this field, and details are not described herein.
For the torque distributing valve 100 of the utility model after accessing in hydraulic circuit, fluid enters first through oil inlet valve port A1
Oil duct 21 is filtered by strainer 27, then enters control chamber 11 through the first damping hole 23, while fluid also passes through the second damping hole
13 return to return port B1, then oil return box.It throttles due to not passing through between the first oil duct 21 and oil inlet valve port A1, therefore the
The interior pressure P of one oil duct 21LIt is identical with the pressure of oil inlet valve port A1, i.e. the pressure of oil inlet valve port A1 into after control chamber 11,
It is reduced to PKThe first end of spool 2 is acted on, at this time pressure PKSpool 2 will be promoted to be moved to the direction where the second end of spool 2,
And compression reseting spring 3 simultaneously, at this time spool 2 no longer block the connection of oil inlet valve port A1 and decompression/overflow valve port C1.Decompression/
When overflow valve port C1 is connected with oil inlet valve port A1, the pressure relief valve port A11 formed in decompression/overflow valve port C1 and oil inlet valve port A1 connects
It is logical.
Fluid in oil inlet valve port A1 is entering decompression/overflow valve port C1 through pressure relief valve port A11 into the first oil groove 24,
Due to the throttling action of pressure relief valve port A11, the pressure into decompression/overflow valve port C1 will decline, the fluid of the first oil groove 24
Enter feedback cavity 12 by the second oil duct 22, after establishing oil pressure in feedback cavity 12, the pressure of feedback cavity 12 is PS, due to second
Oil duct 22 without throttle effect, so the pressure P of feedback cavity 12SEqual to the pressure of decompression/overflow valve port C1, that is, depressurize/overflow
The pressure of stream valve port C1 acts on the second end of spool 2.When the oil pressure in feedback cavity 12 is just established, the pressure P of control chamber 11K
More than the pressure P of feedback cavity 12S, spool 2 will continue to move down, and the flow area of pressure relief valve port A11 will increase at this time, at this time
The pressure of decompression/overflow valve port C1 increases with the increase of the flow area of pressure relief valve port A11, decompression/overflow valve port C1's
Pressure transmission is to feedback cavity so that the pressure P of feedback cavity 12SAlso incrementally increase, until PS=PK, at this time spool 2 not movement stop
Only in some position, the pressure that can obtain decompression/overflow valve port C1 at this time is equal to the pressure P of control chamber 11K.In pressure balance
After foundation, when certain extraneous factor causes the pressure of decompression/overflow valve port C1 to increase the pressure P more than control chamber 11 suddenlyKWhen,
The pressure of decompression/overflow valve port C1 is immediately passed to feedback cavity 12, i.e. PS＞ PK, spool 2 will be towards the first of spool 2 at this time
Direction movement where end, pressure relief valve port A11 is closed, that is, spool 2 is by decompression/overflow valve port C1's and oil inlet valve port A1
Connection blocks, while return port B1 is opened, the part oil hydrorrhea stream return port B1 oil returns in decompression/overflow valve port C1
Case, the pressure of decompression/overflow valve port C1 reduces, until the pressure of decompression/overflow valve port C1 is equal to the pressure P of control chamber 11K。
Certainly, after pressure balance foundation, when certain extraneous factor causes the pressure of decompression/overflow valve port C1 to be less than suddenly
PKWhen, the pressure of decompression/overflow valve port C1 is immediately passed to feedback cavity 12, i.e. PS<PK, spool 2 will be towards spool 2 at this time
Direction movement where second end, return port B1 is closed, while increases the flow area of pressure relief valve port A11, is subtracted with increase
The pressure P of pressure/overflow valve port C13, until the pressure of decompression/overflow valve port C1 is equal to the pressure P of control chamber 11K, while inlet valve
Mouth A1 will have more fluid to distribute to decompression/overflow valve port C1.
It is possible thereby to see, the torque square distributing valve of the utility model can cause the pressure of decompression/overflow valve port C1 to be equal to
The pressure of control chamber 11, the Ratio invariableness of the pressure of control chamber 11 and the pressure of oil inlet valve port A1, so decompression/overflow valve port C1
Pressure and oil inlet valve port A1 force pressure Ratio invariableness, can with when decompression/overflow valve port C1 is influenced be subject to extraneous factor
To change unlatching and the pass of connection area and control return port B1 between oil inlet valve port A1 and decompression/overflow valve port C1
It closes, becomes smaller in the pressure of decompression/overflow valve port C1, that is, during the external system more fluid of needs, increase oil inlet valve port A1
Connection area between decompression/overflow valve port C1 simultaneously closes return port B1 so that more hydraulic pressure supply in oil inlet valve port A1
It is used to external system；Become larger in the pressure of decompression/overflow valve port C1, that is, there is fluid and is taken for being more than in external system,
Connection blocking between oil inlet valve port A1 and decompression/overflow valve port C1 is opened simultaneously into return port B1 so that external system
Fluid returns to return port B1 through decompression/overflow valve port C1, then oil-feed tank.
The utility model additionally provides a kind of wheel walking hydraulic control system with above-mentioned torque distributing valve 100, uses
In self-travel type haulage equipment, driving force is provided to the driving wheel of equipment.The torque distributing valve 100 of the utility model is being applied
After above-mentioned torque distributing valve 100, it can effectively prevent motor from occurring suction and building the pressure.
As shown in figure 8, the wheel walking hydraulic control system of the utility model first embodiment, including：Three-way four-position electricity
Magnetic reversal valve 4, shuttle valve 5, above-mentioned torque distributing valve 100, the first motor 6 and the second motor 7.
Wherein, three-way four-position solenoid directional control valve 4, for controlling the advance of self-travel type haulage equipment and retrogressing, including master
Oil inlet P 2, main oil return inlet T 2, work oil inlet A2 and work oil return opening B2, main oil inlet P 2 are connected on hydraulic pump, main
Oil return inlet T 2 is connected with fuel tank.When the coil in 4 left side of three-way four-position solenoid directional control valve obtains electric, before self-travel type haulage equipment
Into, when the coil on 4 right side of three-way four-position solenoid directional control valve obtains electric, the retrogressing of self-travel type haulage equipment.
First motor 6 and the second motor 7 being connected in series with the first motor 6, the first motor 6 connect with work oil inlet A2
It connects, the second motor 7 is connected with work oil return opening B2.In the present embodiment, the first motor 6 is used for the left side wheel of driving equipment,
Second motor 7 is used for the right side wheels of driving equipment.
Shuttle valve 5 includes the first oil inlet A3, oil outlet B3 and the second oil inlet C3, the first oil inlet A3 and work oil inlet
A2 connections, the second oil inlet C3 are connected with work oil return opening B2.
The oil inlet valve port A1 of torque distributing valve 100 is connected with oil outlet B3, and return port B1 is connected with fuel tank, decompression/overflow
Stream valve port C1 is connected between the first motor 6 and the second motor 7.
The wheel of the utility model walks hydraulic control system when in use, when the left electricity of three-way four-position solenoid directional control valve 4
Magnet obtains electric, and self-travel type haulage equipment moves forward, and the work oil inlet A2 of three-way four-position solenoid directional control valve 4 is as hydraulic oil
Delivery outlet, hydraulic oil is introduced into the first motor 6, then flows into the second motor 7 by the first motor 6；Three-way four-position electromagnetism changes simultaneously
The first oil inlet A3 that the fluid exported to the work oil inlet A2 of valve 4 can also enter through shuttle valve 5 enters torque distributing valve 100
Oil inlet valve port A1, the inside of torque distributing valve 100 can establish oil pressure, and the pressure of decompression/overflow valve port C1 is equal to oil inlet valve port A1
Pressure half, be also equal to the half of the pressure of work oil inlet A2, and vehicle is in the state do not turned round, 6 He of the first motor
Rotating speed is identical between second motor 7, pressure of the pressure between the first motor 6 and the second motor 7 equal to work oil inlet A2
Half, whole system are in pressure balance.
As shown in figure 8, when device left is turned, the rotating speed of equipment revolver is less than the speed of equipment right wheel, i.e. the first horse
Rotating speed up to 6 needs to be less than the rotating speed of the second motor 7, and the second motor 7 plays an important role of hydraulic pump at this time, starts imbibition pressure oil,
The pressure among two motors is caused to become smaller reduction, i.e. the pressure of the decompression of torque distributing valve 100/overflow valve port C1 becomes smaller, at this point,
The pressure of decompression/overflow valve port C1 is less than the pressure of control chamber 11, and torque distributing valve 100 functions to, and spool 2 is to spool 2
Direction movement where second end, the connection area increase between decompression/overflow valve port C1 and oil inlet valve port A1, until decompression/
The pressure of overflow valve port C1 is identical with the pressure of control chamber 11, simultaneously closes off return port B1, the fluid that oil inlet valve port A1 enters
Between supplementing two motors, prevent the second motor 7 from dallying.When car traveling during it is right-handed when, the first motor 6 still by
Work oil inlet A2 DFF Direct Fuel Feeds, and revolver is still for driving wheel at this time, and right wheel is follower, the rotating ratio second of the first motor 6
The rotating speed of motor 7 is fast, and the hydraulic oil of the first motor 6 outflow is more than the hydraulic oil that sucks of the second motor 7 needs, cause two motors it
Between the pressure of decompression/overflow valve port C1 of pressure i.e. torque distributing valve 100 become higher, at this point, the pressure of decompression/overflow valve port C1
Power is more than the pressure of control chamber 11, and torque distributing valve 100 functions to, and spool 2 is moved to the direction where 2 first end of spool
Dynamic, the connection area between decompression/overflow valve port C1 and oil inlet valve port A1 reduces, until spool 2 by decompression/overflow valve port C1 with
Oil inlet valve port A1 is blocked, while return port B1 is opened, and extra fluid enters through decompression/overflow valve port C1 between two motors
Return port B1, is finally back to fuel tank, so as to avoid building the pressure between two motors.
When 4 the right electromagnet of three-way four-position solenoid directional control valve obtains electric, self-travel type haulage equipment travels backward, works at this time
Oil return opening B2 output hydraulic pressures oil, when self-travel type haulage equipment is in left-hand rotation and right-hand rotation, the control of wheel walking hydraulic control system
The control mode that mode processed moves forward with self-travel type haulage equipment is on the contrary, details are not described herein；Correspondingly, 5 basis of shuttle valve
The height selection high pressure oil of pressure is also by the sequence of movement of torque distributing valve 100.
As shown in figure 9, the wheel of the utility model second embodiment is walked, hydraulic control system is compared with first embodiment
For basic structure and principle it is essentially identical, the wheel of the utility model second embodiment walking hydraulic control system is compared with the
For one embodiment, the difference is that further including two four-way electromagnetic reversing valves 8, two motors pass through two four-way electromagnetics
Reversal valve 8 connects, and realizes series connection when two four-way electromagnetic reversing valves 8 power off.
Specifically, two four-way electromagnetic reversing valves 8 include main oil inlet P 4, main oil return inlet T 4, work oil inlet A4 and work
Make oil return opening B4, wherein, the main oil inlet P 4 of two four-way electromagnetic reversing valves 8 is returned with the work of three-way four-position solenoid directional control valve 4
Hydraulic fluid port B2 connections, the work oil inlet of the work oil return opening B4 and three-way four-position solenoid directional control valve 4 of two four-way electromagnetic reversing valves 8
A2 connections, one end of the first motor 6 are connected with the work oil inlet A2 of three-way four-position solenoid directional control valve 4, the first motor 6 it is another
End is connected with the work oil inlet A4 of two four-way electromagnetic reversing valves 8, second one end of motor 7 and subtracting for torque distributing valve 100
Pressure/overflow valve port C1 connections, the main oil return inlet T 4 of one end of the second motor 7 also with two four-way electromagnetic reversing valves 8 are connected, and second
The other end of motor 7 is connected on the work oil return opening B2 of three-way four-position solenoid directional control valve 4, and so connection can be in two four-ways
When solenoid directional control valve 8 powers off, realize that the first motor 6 is connected with the second motor 7.
2/2-way solenoid valve 9 is further included in the wheel walking hydraulic control system of the utility model second embodiment, two
Two three-way electromagnetic valves 9 of position are connected between one end of the second motor 7 and decompression/overflow valve port C1 of torque distributing valve 100, at two
When two three-way electromagnetic valves 9 and two four-way electromagnetic reversing valves 8 power on simultaneously, the first motor 6 is connected in parallel with the second motor 7, two
Two three-way electromagnetic valves 9 are closed, and disconnect the company between decompression/overflow valve port C1 of torque distributing valve 100 and one end of the second motor 7
It connects, system is walked for low speed at this time, the different distribution according to need flows that both sides motor can be hindered according to liquid, at this time need not torque point
Assignment of traffic is carried out with valve, realizes the high low speed switching of running gear at this time.
To sum up, the torque distributing valve 100 of the utility model and wheel walking hydraulic control system, can according to decompression/
The pressure change of overflow valve port C1 adjusts connected relation and oil return valve between decompression/overflow valve port C1 and oil inlet valve port A1
The opening and closing of mouth B1, and when decompression/overflow valve port C1 becomes larger, the connection of decompression/overflow valve port C1 and oil inlet valve port A1 is blocked,
Return port B1 is opened, the fluid in decompression/overflow valve port C1 flows back to fuel tank through return port B1, in decompression/overflow valve port
C1 increases the connection area between decompression/overflow valve port C1 and oil inlet valve port A1, while return port B1 is closed, and makes oil inlet
The fluid of valve port A1 provides fluid by decompression/overflow valve port C1 to external system, so as to fulfill the distribution to torque.
Each technical characteristic of embodiment described above can be combined arbitrarily, to make description succinct, not to above-mentioned reality
It applies all possible combination of each technical characteristic in example to be all described, as long as however, the combination of these technical characteristics is not deposited
In contradiction, the scope that this specification is recorded all is considered to be.
Embodiment described above only expresses the several embodiments of the utility model, and description is more specific and detailed,
But therefore it can not be interpreted as the limitation to utility model patent scope.It should be pointed out that the common skill for this field
For art personnel, without departing from the concept of the premise utility, various modifications and improvements can be made, these are belonged to
The scope of protection of the utility model.Therefore, the protection domain of the utility model patent should be determined by the appended claims.
Claims (10)
1. a kind of torque distributing valve, including valve pocket, the spool being housed in the valve pocket and the reset being housed in the valve pocket
Spring, the spool include first end and the second end opposite with the first end, and the resetting spring is to the of the spool
Two ends provide pretightning force, and the valve pocket is equipped with return port, decompression/overflow valve port and oil inlet valve port, which is characterized in that described
The pressure of oil inlet valve port is by spool ratio depressurization in the first end of the spool, the pressure of the decompression/overflow valve port
The second end of the spool is acted directly on by spool, and the pressure of the decompression/overflow valve port is by the oil inlet valve port
Fluid formed after the decompression of spool ratio into the decompression/overflow valve mouth, the first end of the spool and second end
Pressure application surface product is identical, and the spool controls the return port, the decompression/overflow valve port under the action of pressure at two ends
And the connected relation between the oil inlet valve port, the pressure of the decompression/overflow valve port is made to be equal to the pressure of the oil inlet valve port
Power passes through pressure of the spool ratio depressurization in the first end of the spool.
2. torque distributing valve according to claim 1, it is characterised in that：The valve pocket acts on the spool equipped with pressure
The control chamber and pressure of first end act on the feedback cavity of the spool second end, are equipped with and the inlet valve in the spool
The first oil duct and the connection decompression/overflow valve port and the second oil duct of the feedback cavity of mouth connection, the first of the spool
End, which is equipped with, connects first oil duct and the first damping hole of the control chamber, is additionally provided on the valve pocket and connects with the control chamber
The second damping hole that is logical and being connected with the return port.
3. torque distributing valve according to claim 2, it is characterised in that：First damping hole and second damping hole
Liquid resistance it is equal.
4. torque distributing valve according to claim 2, it is characterised in that：The peripheral wall of the spool is equipped with the first oil groove, institute
It states the first oil groove along the axial both ends to the spool of the spool to extend, first oil groove connects with second oil duct
Logical, first oil groove is connected with the decompression/overflow valve port, and the decompression/overflow valve port passes through first oil groove and institute
It states return port and the connection of oil inlet valve port, the spool controls first oil groove and described time under the action of pressure at two ends
The conducting and partition of fuel tap mouth, and control the conducting and partition of first oil groove and the oil inlet valve port.
5. torque distributing valve according to claim 4, it is characterised in that：The peripheral wall of the spool is additionally provided with the second oil groove,
In the axial direction of the spool, second oil groove and first oil groove are arranged at intervals, and first oil duct passes through described the
Two oil grooves are connected with the oil inlet valve port.
6. torque distributing valve according to claim 2, it is characterised in that：The first end of the spool is equipped with orifice plug, institute
The first damping hole is stated to be arranged on the orifice plug.
7. torque distributing valve according to claim 2, it is characterised in that：Filter screen is equipped in first oil duct.
The hydraulic control system 8. a kind of wheel is walked, which is characterized in that including：
Three-way four-position solenoid directional control valve for controlling the advance of self-travel type haulage equipment and retrogressing, including main oil inlet, is led back
Hydraulic fluid port, work oil inlet and work oil return opening, the main oil inlet of the three-way four-position solenoid directional control valve are connected with hydraulic pump, institute
The main oil return opening for stating three-way four-position solenoid directional control valve is connected with fuel tank；
First motor and the second motor being connected in series with first motor, first motor and the three-way four-position electromagnetism
The work oil inlet connection of reversal valve, second motor are connected with the work oil return opening of the three-way four-position solenoid directional control valve；
Shuttle valve, including the first oil inlet, the second oil inlet and oil outlet, the first oil inlet and the three-way four-position of the shuttle valve
The work oil inlet connection of solenoid directional control valve, the work of second oil inlet of shuttle valve and the three-way four-position solenoid directional control valve are returned
Hydraulic fluid port connects；
Such as claim 1-7 any one of them torque distributing valves, the oil inlet valve port is connected with the oil outlet of the shuttle valve, institute
It states return port to be connected with fuel tank, the decompression/overflow valve port is connected between first motor and second motor.
The hydraulic control system 9. wheel according to claim 8 is walked, it is characterised in that：Two four-way electromagnetics are further included to change
To valve, two four-way electromagnetic reversing valves include main oil inlet, main oil return opening, work oil inlet and work oil return opening, wherein,
The main oil inlet of two four-way electromagnetic reversing valves is connected with the work oil return opening of the three-way four-position solenoid directional control valve, described
The work oil return opening of two four-way electromagnetic reversing valves is connected with the work oil inlet of the three-way four-position solenoid directional control valve, and described
One end of one motor is connected with the work oil inlet of the three-way four-position solenoid directional control valve, the other end of first motor and institute
State the work oil inlet connection of two four-way electromagnetic reversing valves, one end of second motor and subtracting for the torque distributing valve
The connection of pressure/overflow valve port, the main oil return opening of one end of second motor also with two four-way electromagnetic reversing valves are connected, institute
The other end for stating the second motor is connected on the work oil return opening of the three-way four-position solenoid directional control valve, two four-way electromagnetics
When reversal valve powers off, first motor is connected with second motor.
The hydraulic control system 10. wheel according to claim 9 is walked, it is characterised in that：Further include 2/2-way electromagnetism
Valve, the 2/2-way solenoid valve are connected to one end of second motor and decompression/overflow valve port of the torque distributing valve
Between, when the 2/2-way solenoid valve and two four-way electromagnetic reversing valves power on simultaneously, first motor and institute
The second motor is stated to be connected in parallel, the 2/2-way solenoid valve is closed, disconnect decompression/overflow valve port of the torque distributing valve with
Connection between one end of second motor.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201721517156.2U CN207406559U (en) | 2017-11-14 | 2017-11-14 | Torque distributing valve and wheel walking hydraulic control system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201721517156.2U CN207406559U (en) | 2017-11-14 | 2017-11-14 | Torque distributing valve and wheel walking hydraulic control system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN207406559U true CN207406559U (en) | 2018-05-25 |
Family
ID=62319211
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201721517156.2U Withdrawn - After Issue CN207406559U (en) | 2017-11-14 | 2017-11-14 | Torque distributing valve and wheel walking hydraulic control system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN207406559U (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108953270A (en) * | 2018-08-24 | 2018-12-07 | 东莞海特帕沃液压科技有限公司 | A kind of control valve |
| CN109296527A (en) * | 2018-12-01 | 2019-02-01 | 李军 | A kind of reciprocating pump control valve |
| CN109779998A (en) * | 2017-11-14 | 2019-05-21 | 浙江华益精密机械股份有限公司 | Torque distributing valve and wheel walking hydraulic control system |
-
2017
- 2017-11-14 CN CN201721517156.2U patent/CN207406559U/en not_active Withdrawn - After Issue
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109779998A (en) * | 2017-11-14 | 2019-05-21 | 浙江华益精密机械股份有限公司 | Torque distributing valve and wheel walking hydraulic control system |
| CN109779998B (en) * | 2017-11-14 | 2023-11-24 | 浙江三尚智迪科技有限公司 | Torque distribution valve and wheel traveling hydraulic control system |
| CN108953270A (en) * | 2018-08-24 | 2018-12-07 | 东莞海特帕沃液压科技有限公司 | A kind of control valve |
| CN109296527A (en) * | 2018-12-01 | 2019-02-01 | 李军 | A kind of reciprocating pump control valve |
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| GR01 | Patent grant | ||
| CP01 | Change in the name or title of a patent holder |
Address after: 689 Jiefang Road, Diankou Industrial Zone, Zhuji County, Shaoxing City, Zhejiang Province Patentee after: Zhejiang Huayi Precision Machinery Co.,Ltd. Address before: 689 Jiefang Road, Diankou Industrial Zone, Zhuji County, Shaoxing City, Zhejiang Province Patentee before: ZHEJIANG HUAYI PRECISION MACHINERY Co.,Ltd. |
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| CP01 | Change in the name or title of a patent holder | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20180525 Effective date of abandoning: 20231124 |
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| AV01 | Patent right actively abandoned |
Granted publication date: 20180525 Effective date of abandoning: 20231124 |
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| AV01 | Patent right actively abandoned | ||
| AV01 | Patent right actively abandoned |