CN106762928B - Automobile hydraulic system and engineering truck with it - Google Patents
Automobile hydraulic system and engineering truck with it Download PDFInfo
- Publication number
- CN106762928B CN106762928B CN201710029806.7A CN201710029806A CN106762928B CN 106762928 B CN106762928 B CN 106762928B CN 201710029806 A CN201710029806 A CN 201710029806A CN 106762928 B CN106762928 B CN 106762928B
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- reversal valve
- valve
- outlet
- import
- spool
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Power Steering Mechanism (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The present invention relates to automobile hydraulic system, engineering trucks.Automobile hydraulic system includes：First pump and the second pump, by the engine driving of vehicle；Steering control valve, including the first reversal valve, the second reversal valve and pressure-control valve, steering control valve has first state and the second state, in first state, the import of first reversal valve is connected with the first outlet of the first reversal valve, the import of second reversal valve is connected with the second reversal valve first outlet, so that the first pump and the second pump provide hydraulic fluid to steering；In the second state, the import of the first reversal valve is both turned on the first reversal valve first outlet and second outlet, so that the pressure for the hydraulic fluid that the first outlet of pressure-control valve the first reversal valve of control is exported to steering.The technical solution for applying the application, power steering smaller problem when steering wheel is excessively sensitive when improving high engine speeds rotation existing in the prior art, low engine speed rotates.
Description
Technical field
The present invention relates to engineering machinery fields, in particular to a kind of automobile hydraulic system and with its engineering truck
.
Background technology
Loader-digger is widely used general, has served the multiple fields of national economy, hydraulic system includes
Steering boost system and equipment system.Steering boost system generally uses that reliability is higher, the lower machinery of manufacturing cost
Hydraulic booster, mechanical-hydraulic power-assisted are divided into gerotor type and normal streaming according to action mode.Due to constant pressure hydraulic force aid system
Fluid in pipeline is always to maintain high pressure conditions so that the service life of hydraulic booster system is not high, so loader-digger is all
Using the mechanical-hydraulic force aid system of normal streaming.
But constant flow hydraulic force aid system haves the shortcomings that intrinsic at present, and constant flow hydraulic force aid system uses constant displacement pump,
When loader-digger speed is very fast, since engine speed is higher, the fluid flow for pumping output is larger, leads to steering wheel " hair
Float ", lighter to the feeling of driver, the power of steering wheel rotation seems too small, is unfavorable for vehicle progress side of the driver to fast running
To control.When loader-digger travel speed is relatively low, since engine speed is relatively low, constant displacement pump output fluid flow compared with
Small, hydraulic steering cylinder stretching speed is slow, and the effect of power steering is poor, and steering wheel is relatively heavy to the feeling of driver, and driver turns to
Arduously.
Invention content
The present invention is intended to provide a kind of automobile hydraulic system and the engineering truck with it, are existed in the prior art with improving
High engine speeds rotation when steering wheel is excessively sensitive, low engine speed rotation when the smaller problem of power steering.
One side according to the ... of the embodiment of the present invention, the present invention provides a kind of automobile hydraulic systems, including：
First pump and the second pump, by the engine driving of vehicle；
Steering control valve, including the first reversal valve, the second reversal valve and pressure-control valve, the first reversal valve have import,
First outlet and second outlet, the first reversal valve can be connected to the first pump, and the first outlet of the first reversal valve is for being connected to vehicle
Steering, the second outlet of the first reversal valve is connected to pressure-control valve, and the second reversal valve has import, first outlet
And second outlet, the import of the second reversal valve can be connected to the second pump, the first outlet of the second reversal valve is for being connected to vehicle
Steering, the second outlet of the second reversal valve for being connected to fluid tank,
Steering control valve has first state and the second state,
In first state, the import of the first reversal valve is connected with the first outlet of the first reversal valve, the second reversal valve into
Mouth is connected with the second reversal valve first outlet, so that the first pump and the second pump provide hydraulic fluid to steering；
In the second state, the import of the first reversal valve is both turned on the first reversal valve first outlet and second outlet, so that
The pressure for the hydraulic fluid that the first outlet of pressure-control valve the first reversal valve of control is exported to steering.
Optionally, pressure-control valve includes counterbalance valve.
Optionally, also there is the first reversal valve control fluid inlet, control fluid inlet to be used to introduce the first pump output
Hydraulic fluid, to make the import of the first reversal valve go out with the first reversal valve first when the pressure of hydraulic fluid is higher than predetermined value
Mouth and second outlet are both turned on.
Optionally, the first reversal valve includes the first proportional reversing valve, and the first reversal valve includes the first spool, the first spool tool
There is the first position for only making the first outlet of the first reversal valve be connected with import and makes the first outlet and second of the first reversal valve
The second position be connected with import is exported, the first spool is at first position, the first outlet output hydraulic pressure of the first reversal valve
The pressure of fluid is less than the pressure for the hydraulic fluid that the first reversal valve import introduces.
Optionally, the first reversal valve further includes being arranged in the first chamber of the first end of the first spool and setting in the first valve
The second chamber of the second end of core, the inlet communication of first chamber and the first reversal valve, to introduce the first spool to first
The hydraulic fluid of pushing is set, second chamber is connected to the first outlet of the first reversal valve, to introduce the first spool to second
Set the hydraulic fluid of pushing.
Optionally, the second reversal valve further includes the first elastomeric element, and the first elastomeric element is arranged in second chamber.
Optionally, the second reversal valve further includes control fluid inlet, and control fluid inlet is used to introduce the first pump output
Hydraulic fluid, to make the import of the second reversal valve be connected with first outlet when the pressure of hydraulic fluid is less than predetermined value.
Optionally, the second reversal valve includes the second spool, is arranged in the third chamber of the first end of the second spool and setting
In the 4th chamber of the second end of the second spool, the second spool has make the import of the second reversal valve be connected with first outlet the
One position and the second position for making import be connected with second outlet, third chamber are connected with the first outlet of the first reversal valve, with
The hydraulic fluid for pushing the second spool to its second position is introduced, the 4th chamber is connected with the import of the second reversal valve, to draw
Enter the hydraulic fluid for pushing the second spool to the first position of the second spool.
Optionally, the second reversal valve further includes the second elastomeric element, and the second elastomeric element is arranged in third chamber.
Optionally, the second reversal valve includes the second proportional reversing valve.
According to the another aspect of the application, a kind of engineering truck, including above-mentioned automobile hydraulic system are additionally provided.
Using the technical solution of the application, when low engine speed is run, steering control valve is in first state, first
State, the import of the first reversal valve are connected with the first outlet of the first reversal valve, the import of the second reversal valve and the second reversal valve
First outlet is connected, so that the first pump and the second pump provide hydraulic fluid to steering, therefore improves in the prior art
Power steering smaller problem when existing low engine speed rotation.When high engine speeds are run, steering control valve is in the
Two-state, in the second state, the import of the first reversal valve is both turned on the first reversal valve first outlet and second outlet, so that pressure
The pressure for the hydraulic fluid that the first outlet of force control valve the first reversal valve of control is exported to steering.Therefore it improves existing
Steering wheel excessively sensitive issue when high engine speeds present in technology rotate, advantageously accounts for side existing in the prior art
The problem unstable to disk.
By referring to the drawings to the detailed description of exemplary embodiment of the present invention, other feature of the invention and its
Advantage will become apparent.
Description of the drawings
In order to more clearly explain the embodiment of the invention or the technical proposal in the existing technology, to embodiment or will show below
There is attached drawing needed in technology description to be briefly described, it should be apparent that, the accompanying drawings in the following description is only this
Some embodiments of invention without having to pay creative labor, may be used also for those of ordinary skill in the art
With obtain other attached drawings according to these attached drawings.
Fig. 1 shows the automobile hydraulic system structural schematic diagram of the embodiment of the present invention；
Fig. 2 shows the partial schematic diagrams of the automobile hydraulic system of the embodiment of the present invention；
Fig. 3 shows the schematic diagram of the steering control valve of the automobile hydraulic system of the embodiment of the present invention；
Fig. 4 shows the front view of the steering control valve of the automobile hydraulic system of the embodiment of the present invention；
Fig. 5 shows the left view of the steering control valve of the automobile hydraulic system of the embodiment of the present invention；
Fig. 6 shows the diagrammatic cross-section at A-A in Fig. 5；
Fig. 7 shows the right view of the steering control valve of the automobile hydraulic system of the embodiment of the present invention；
Fig. 8 shows the diagrammatic cross-section at B-B in Fig. 7；
Fig. 9 shows the vertical view of the steering control valve of the automobile hydraulic system of the embodiment of the present invention；
Figure 10 shows the upward view of the steering control valve of the automobile hydraulic system of the embodiment of the present invention；And
Figure 11 shows the rearview of the steering control valve of the automobile hydraulic system of the embodiment of the present invention.
In figure：100, power part；200, steering；300, work system；400, the first executive device；30, control is turned to
Valve processed；40, turning gradient control valve；50, valve is excavated；60, loading valve；70,2/2-way solenoid directional control valve；1, safety valve；2, first
Reversal valve；3, engine；4, the first pump；5, the second pump；6, filter；7, fluid tank；8, overflow valve；9, the second reversal valve；10、
First check valve；11, the second check valve；12, steering cylinder；13, flux amplification valve；14, steering gear；15, pressure controls
Valve；16, fluid circuit；21, third locating part；22, the first taper valve core；23, third elastomeric element；24, valve body；25, first
Locating part；26, the first spool；27, the first elastomeric element；28, the second locating part；29, the second spool；210, the second elastic portion
Part；211, the 4th elastomeric element；212, the second taper valve core.
Specific implementation mode
Following will be combined with the drawings in the embodiments of the present invention, and technical solution in the embodiment of the present invention carries out clear, complete
Site preparation describes, it is clear that described embodiments are only a part of the embodiments of the present invention, instead of all the embodiments.Below
Description only actually at least one exemplary embodiment is illustrative, is never used as to the present invention and its application or makes
Any restrictions.Based on the embodiments of the present invention, those of ordinary skill in the art are not making creative work premise
Lower obtained every other embodiment, shall fall within the protection scope of the present invention.
Fig. 1 shows the structural schematic diagram of the automobile hydraulic system of the present embodiment, and Fig. 2 shows the offices of automobile hydraulic system
Portion's schematic diagram, Fig. 3 show the structural schematic diagram of the steering control valve of the present embodiment.The automobile hydraulic system of the present embodiment is to dig
Dig the hydraulic system of loading machine.
In conjunction with shown in Fig. 1 and Fig. 2, automobile hydraulic system includes power part 100, and power part 100 includes the first pump 4 and second
Pump 5, the first pump 4 and the first pump 5 are driven by the engine 3 of vehicle.The import of first pump 4 and the second pump 5 connects with fluid tank 4
It is logical.
Automobile hydraulic system further includes turning gradient control valve 40, and turning gradient control valve 40 goes out including import, first outlet and second
Mouthful.Turning gradient control valve 40 has first state and the second state, in first state, the import of turning gradient control valve 40 and first outlet
Conducting.In the second state, the first outlet and second outlet of turning gradient control valve 40 are connected with import.
Automobile hydraulic system further includes steering 200, the steering control valve 30 for controlling Vehicular turn and job family
System 300.Loader-digger includes excavation portion and loading part, and excavation portion includes scraper bowl, and loading part includes loader(-mounted) shovel.
Work system 300 includes for driving the first executive device 400 of dipper motion, for controlling the first executive device
Excavation valve 50, the second executive device for driving loader(-mounted) shovel to act and loading valve 60 for controlling the second executive device.
Loading valve 60 includes import, first outlet and second outlet.The import of loading valve 60 goes out with the first of pressure-gradient control valve 40
Mouth is connected to by fluid circuit 16, the inlet communication of the first outlet and 2/2-way solenoid directional control valve 70 of loading valve 60, two
The outlet of two electric change valves 70 and fluid tank.The second outlet of loading valve 60 and the inlet communication for excavating valve 50.
Steering control valve 30 includes the first reversal valve 2, the second reversal valve 9 and pressure-control valve 15, and the first reversal valve 2 has
The import of import, first outlet and second outlet, the first reversal valve 2 can be connected to the first pump 4, and the first of the first reversal valve 2
The steering for being connected to vehicle is exported, the second outlet of the first reversal valve 2 is connected to pressure-control valve 15, the second reversal valve
9 there is import, first outlet and second outlet, the import of the second reversal valve 9 can be connected to the second pump 5, the second reversal valve 9
First outlet is used to be connected to the steering of vehicle, and the second outlet of the second reversal valve 9 is for being connected to fluid tank 7.
Steering control valve 30 further includes safety valve 1, and the inlet communication of the import of safety valve 1 and the first reversal valve 2 installs valve
2 outlet is connected to the first outlet of the first reversal valve 2.
Steering control valve 30 has first state and the second state.When 3 low speed of engine is run, at steering control valve 30
In first state, in first state, the import of the first reversal valve 2 is connected with the first outlet of the first reversal valve 2, the second reversal valve
9 import is connected with 9 first outlet of the second reversal valve, so that the first pump 4 and the second pump 5 provide flow of pressurized to steering
Body, therefore improve power steering smaller problem when low engine speed existing in the prior art rotates.
In 3 high-speed cruising of engine, steering control valve 30 is in the second state, in the second state, the first reversal valve 2
Import is both turned on 2 first outlet of the first reversal valve and second outlet, so that pressure-control valve 15 controls the of the first reversal valve 2
One exports the pressure of the hydraulic fluid exported to steering.Therefore high engine speeds rotation existing in the prior art is improved
When steering wheel excessively sensitive issue, advantageously account for the unstable problem of steering wheel existing in the prior art.
Automobile hydraulic system further includes the filter 6 being arranged between the second outlet and fluid tank 7 of the second reversal valve 9,
Filter 6 flows to the hydraulic fluid of fluid tank 7 for filtering the second outlet of the second reversal valve 9.
Automobile hydraulic system further includes overflow valve 8, and the import of overflow valve 8 and second pump 5 outlet, overflow valve 8
Outlet and fluid tank, to control the pressure of the introduced hydraulic fluid of import of the second reversal valve 9.
Automobile hydraulic system further includes the first check valve 10, the import of the first check valve 10 and the first of the second reversal valve 9
Outlet, outlet and 200 inlet communication of steering of the first check valve 10.
Automobile hydraulic system further includes the second check valve 11, the import of the second check valve 11 and the first of the first reversal valve 2
Outlet, outlet and 200 inlet communication of steering of the second check valve 11.
In the present embodiment, pressure-control valve 15 includes counterbalance valve.When steering control valve 30 is in the second state, counterbalance valve energy
The pressure of enough hydraulic fluids for exporting the first outlet of the first reversal valve 2 to steering 200 is controlled in predetermined value, so as to turn
Tend to be constant to power-assisted.
Also there is first reversal valve 2 control fluid inlet, control fluid inlet to be used to introduce the flow of pressurized of 4 output of the first pump
Body, with make when the pressure of hydraulic fluid is higher than predetermined value the import of the first reversal valve 2 and 2 first outlet of the first reversal valve and
Second outlet is both turned on, so that pressure-control valve 15 controls the hydraulic pressure that the first outlet of the first reversal valve 2 is exported to steering
The pressure of fluid.
Fig. 4 shows that the front view of the steering control valve 30 of the present embodiment, Fig. 5 show the left view of steering control valve,
Fig. 6 shows the sectional view at the A-A of steering control valve 30.
In conjunction with shown in Fig. 4 to 6, first reversal valve 2 of the present embodiment includes the first proportional reversing valve, the first reversal valve 2 packet
The first spool 26 is included, the first spool 26 has the first position for only making the first outlet of the first reversal valve 2 be connected with import and makes
The second position that the first outlet and second outlet of first reversal valve 2 are connected with import, the first spool 26 at first position,
The pressure of the first outlet output hydraulic pressure fluid of first reversal valve 2 is less than the pressure for the hydraulic fluid that 2 import of the first reversal valve introduces
Power.
First reversal valve 2 further includes the first elastomeric element 27 for the first spool 26 to be urged to first position.First
Elastomeric element 27 is arranged in second chamber.Optionally, the first elastomeric element 27 includes spring.
First reversal valve 2 further includes being arranged in the first chamber of the first end of the first spool 26 and setting in the first spool 26
Second end second chamber, the inlet communication of first chamber and the first reversal valve 2, to introduce the first spool 26 to second
Set the hydraulic fluid of pushing.Second chamber is connected to the first outlet of the first reversal valve 2, to introduce the first spool 26 to first
The hydraulic fluid that position pushes.
As shown in fig. 6, steering control valve 30 includes valve body 24, the first hole is provided on valve body 24.First spool 26 is arranged
It can move in the first hole and along the first hole.The first end formation first chamber of first spool 26, the second of the first spool 26
End forms second chamber.
The first end of first spool 26 is additionally provided with the first locating part 25, and through-hole is provided on the first locating part 25, so that
Hydraulic fluid in first chamber can act on the first end with the first spool 26.
The hydraulic fluid of first pump, 4 output is delivered in the import and first chamber of the first reversal valve 2, the first reversal valve 2
First outlet output hydraulic fluid be delivered in second chamber.
When low engine speed is run, the hydraulic fluid of the import introducing of the first reversal valve 2 and the first of the first reversal valve 2
The pressure difference for exporting the hydraulic fluid of output is smaller, therefore the first spool 26 is maintained at first under the action of the first elastomeric element 27
Position.
When high engine speeds are run, the hydraulic fluid of the import introducing of the first reversal valve 2 and the first of the first reversal valve 2
The pressure difference for exporting the hydraulic fluid of output is larger, therefore the first spool 26 is moved to second chamber, to be in the second position.
Second reversal valve 9 further includes control fluid inlet, and control fluid inlet is used to introduce the flow of pressurized of 4 output of the first pump
Body, to make the import of the second reversal valve 9 be connected with first outlet when the pressure of hydraulic fluid is less than predetermined value.
Second reversal valve 9 include the second spool 29, be arranged the first end of the second spool 29 third chamber and setting exist
4th chamber of the second end of the second spool 29, the second spool 29, which has, makes the import of the second reversal valve 9 be connected with first outlet
First position and the second position that makes import be connected with second outlet.
Second reversal valve 9 further includes the second elastomeric element 210 for pushing the second spool 29 to first position, and second
Elastomeric element 210 is arranged in third chamber.Optionally, the second elastomeric element 27 includes spring.
The inlet communication of third chamber and the first reversal valve 2 is pushed the second spool 29 to its second position with introducing
Hydraulic fluid, the 4th chamber are connected to the first outlet of the second reversal valve 9, to introduce the second spool 29 the to the second spool
The hydraulic fluid that one position pushes.
The second hole is provided on the valve body 24 of steering control valve 30, the second spool 29 is arranged in the second hole and being capable of edge
It moves in the second hole.The first end of second spool 29 forms third chamber, and the second end of the second spool 29 forms the 4th chamber.
The second end of second spool 29 is additionally provided with the second locating part 28, and through-hole is provided on the second locating part 28, so that
The indoor hydraulic fluid of third chamber can act on the first end with the second spool 29.
Optionally, the second reversal valve 9 includes the second proportional reversing valve.
When low engine speed is run, the hydraulic fluid of the import introducing of the first reversal valve 2 and the first of the first reversal valve 2
The pressure difference for exporting the hydraulic fluid of output is smaller, therefore the first spool 26 is maintained at first under the action of the first elastomeric element 27
Position, the second spool 29 are maintained at first position the second elastomeric element 210 under, to which steering control valve 30 is in first
State.
When high engine speeds are run, the hydraulic fluid of the import introducing of the first reversal valve 2 and the first of the first reversal valve 2
The pressure difference for exporting the hydraulic fluid of output is larger, therefore the first spool 26 is moved to second chamber to be in the second position；Second
Spool 29 is moved to the 4th chamber to be in the second position, so that steering control valve 30 is in the second state.
It is shown in Figure 6, third hole is additionally provided on the valve body 24 of steering control valve 30, pressure-control valve 15 includes by
Third elastomeric element 23, the first taper valve core 22 and the third locating part 21 that the bottom end in three holes is set gradually.Third locating part 21
The side back to the first taper valve core 22 communicated with the import of pressure-control valve 15, the first taper valve core 22 back to third limit
The side of position part 21 is communicated with the outlet of pressure-control valve 15.
First-class body opening is provided on third locating part 21,22 core of the first cone valve coordinates with first-class body opening to change stream
Amount.
As shown in figure 8, being additionally provided with the 4th hole on the valve body 24 of steering control valve 30, safety valve 1 includes by the 4th hole
The 4th elastomeric element 211, the second taper valve core 212 and the 4th locating part 213 that bottom is set gradually.
The side back to the second taper valve core 212 of 4th locating part 213 is communicated with the import of safety valve 1, the second taper
The side back to the 4th locating part 213 of spool 212 is communicated with the outlet of safety valve 1.
In conjunction with shown in Fig. 4 to 11, hydraulic fluid port a, hydraulic fluid port b, oil are provided on the valve body 24 of the steering control valve 30 of the present embodiment
Mouth c, hydraulic fluid port d, hydraulic fluid port e, hydraulic fluid port f and hydraulic fluid port g.
Steering control valve 30 includes the first reversal valve 2, the second reversal valve 9, pressure-control valve 15, safety valve 1.Wherein pressure
The control port of control valve 15 is connected to hydraulic fluid port a, and the oil outlet of pressure-control valve 15 is connected to hydraulic fluid port g.
The import of safety valve 1, the import of the first reversal valve 2, the second reversal valve 9 the 4th chamber be connected to hydraulic fluid port f, pacify
The outlet of full valve 1, the first outlet of the first reversal valve 2, the second reversal valve 9 third chamber be connected to b mouthfuls.
The import of second reversal valve 9 is connected to hydraulic fluid port d, and the first outlet of the second reversal valve 9 is connected to hydraulic fluid port c；Second changes
It is connected to 9 second outlet of valve with hydraulic fluid port e.
Fig. 4 shows the front view of the steering control valve 30 of the present embodiment.As shown in figure 4, before steering control valve 30
Upper setting hydraulic fluid port a, fabrication hole h, fabrication hole i, fabrication hole j, fabrication hole k, fabrication hole l and fabrication hole m.
Fig. 5 shows the left view of the steering control valve 30 of the present embodiment, as shown in figure 5, on the left side of steering control valve
It is provided with fabrication hole n, fabrication hole o and fabrication hole p.
Fig. 7 shows the right view of the steering control valve 30 of the present embodiment, as shown in fig. 7, the course changing control of the present embodiment
Fabrication hole q, fabrication hole r, fabrication hole s and fabrication hole t are provided on the right side of valve 30.
Fig. 9 shows the vertical view of the steering control valve 30 of the present embodiment.As shown in figure 9, the top surface of steering control valve 30
From setting gradually hydraulic fluid port b, hydraulic fluid port c, hydraulic fluid port d, fabrication hole u and fabrication hole v.
Figure 10 shows the upward view of the steering control valve 30 of the present embodiment.As shown in Figure 10, the bottom of steering control valve 30
Hydraulic fluid port f, hydraulic fluid port e, fabrication hole w, fabrication hole x are set gradually from left to right on face.
Figure 11 shows the rearview of the steering control valve 30 of the present embodiment.As shown in figure 11, after steering control valve 30
Hydraulic fluid port g is set on face.
Fabrication hole u on 30 top surface of steering control valve drills through the fabrication hole o to the left side, fabrication hole v and the work on the right side
Fabrication hole i on skill hole q, front is drilled through.
There are three fabrication holes for left side brill, from fabrication hole n and the third hole, the top surface fabrication hole that are used to form pressure-control valve 15
U is drilled through, and the fabrication hole o and fabrication hole u on top surface, the fabrication hole x on bottom surface are drilled through, fabrication hole w on fabrication hole p and bottom surface,
Fabrication hole x and hydraulic fluid port f are drilled through.
The right side is bored there are four fabrication hole, the fabrication hole q and fabrication hole l on front, the fabrication hole v on top surface, on front
Fabrication hole h is drilled through, and fabrication hole r and fabrication hole m, the 4th hole for being used to form internal security valve drill through；Fabrication hole s and hydraulic fluid port d, oil
Mouth c is drilled through, and fabrication hole t and hydraulic fluid port d, hydraulic fluid port e are drilled through.
Shown in Fig. 4,6 and 10, bottom surface is bored there are two fabrication hole, fabrication hole w on the left side fabrication hole p, first change
It is drilled through to the first chamber of valve 2, fabrication hole x is drilled through with fabrication hole o, the fabrication hole p on the left side.
Front is bored there are six fabrication hole, and fabrication hole h is drilled through with fabrication hole q, the hydraulic fluid port b on the right side, fabrication hole j with for shape
It is drilled through at the 4th hole of safety valve, hydraulic fluid port b, fabrication hole k is drilled through with the 4th hole for being used to form safety valve；Fabrication hole i and top surface
On fabrication hole v, the first reversal valve 2 spring terminal drill through；Right side from top to bottom first fabrication hole l on the left of the right side on to
Lower first fabrication hole q, the second reversal valve 9 third chamber drill through, fabrication hole r, the second reversal valve on fabrication hole m and the right side
9 the 4th chambers drill through.
The automobile hydraulic system of the present embodiment is the hydraulic system of loader-digger, in the course of work of loader-digger
In:
When loader-digger is turned to, the hydraulic fluid of 4 offer of the first pump is delivered to by turning gradient control valve 40 to be turned
To system 200.
There are two types of states for the loader-digger steering procedure of the present embodiment：When middle steering of running at high speed, second is that low speed row
Sail middle steering.
It runs at high speed in steering procedure, the hydraulic fluid for flowing into steering 200 enters steering control valve 30.Above-mentioned liquid
What pressure fluid first passed around is the first proportional reversing valve 2, originally the first proportional reversing valve 2 is in the right side under spring force
Position, with throttling action when be in right position due to the first reversal valve 2, the import of the first reversal valve 2 and first outlet it
Between will produce certain pressure difference.
When loader-digger is run at high speed, the rotating speed of engine 3 is higher, and the flow by the first reversal valve 2 is larger, because
The chock pressure difference that this is generated is also larger because the inlet pressure of the first reversal valve 2 act on the first reversal valve 2 without spring terminal,
The pressure of the first outlet of first reversal valve 2 acts on the spring terminal of the first reversal valve 2.
When the spring terminal of the first reversal valve 2 and the pressure difference without spring terminal are more than spring force, the first reversal valve 2 can gradually to
Left position changes.Due to being proportioning valve using the first reversal valve 2, the first reversal valve 2 is changed from right position to left position, until passing through
First reversal valve 2 enter steering flow caused by the first reversal valve 2 import and first outlet between pressure difference with
Until spring dynamic balance.And extra hydraulic fluid is transported to by the channel and pressure-control valve 15 of 2 left position of the first reversal valve
Fluid tank 7.
By the hydraulic fluid of the first reversal valve 2, on the one hand diverted device 14 acts on flux amplification valve 13, so that flow
Amplifying valve 13 commutates, and the flux amplification valve 13 be on the other hand connected after check valve 11 and commutation enters steering cylinder 12,
To realize power steering, i.e., enter the hydraulic fluid flow rate of power-assisted oil cylinder by flux amplification valve when loader-digger is run at high speed
Be it is fixed, power-assisted oil cylinder stretch out the time be also it is fixed, it is only related with the spring force of the first reversal valve 2, not by its dependent variable
It influences, power-assisted oil cylinder stretching time and the spring force of the first reversal valve 2 have following relationship：
Wherein, t is that power-assisted oil cylinder stretches out the time；For power-assisted oil cylinder piston active area；L power-assisted oil cylinder piston strokes；S is
First proportional reversing valve core active area；K is the orifice shapes coefficient of the first proportional reversing valve, A1For the first proportional reversing valve mouth
Equivalent orifice size；F is the spring force of the first reversal valve 2.
Since the spring force of the second reversal valve 9 is slightly smaller than the spring force of the first reversal valve 2, so under the second reversal valve 9
Position enters system, and the hydraulic fluid of 5 output of the second pump passes through 6 direct fluid tank 7 of filter.
In loader-digger runs at a low speed steering procedure, flow into steering 200 hydraulic fluid be still first into
Enter the first reversal valve 2 in steering control valve 30, when being run at a low speed due to loader-digger, engine speed is relatively low, passes through
The flow of one reversal valve 2 is smaller, therefore the pressure difference between the import and first outlet of the first reversal valve 2 is also smaller, if the pressure difference
It is not enough to overcome the spring force of the first reversal valve 2, the first reversal valve 2 that can keep right position access system work under spring force
Make.At this time because the differential pressure action of 2 import of the first reversal valve and first outlet is in 9 upper and lower ends of the second reversal valve, and it is not enough to
Spring force, therefore the upper access system of the second reversal valve, the hydraulic fluid of 5 output of the second pump is overcome by check valve 10 and to lead to
The hydraulic fluid interflow of the first reversal valve 2 and check valve 11 is crossed, the Flow amplification that the hydraulic fluid behind interflow passes through the conducting that commutates
Valve 13 enters steering cylinder 12, realizes power steering.The movement of actual engine speed and steering control valve proportional valve spool
There is following relationship in position：
When running at high speed, (Q11>Or=Q) when, Δ L=L；
When running at a low speed, (Q11<When Q),
Wherein, the displacement variable for the spool 26 that Δ L changes valve 2 in steering control valve second；L is the second proportional reversing valve
Core displacement stroke；Q11For the rate of discharge of check valve 11；Q is the first proportional reversing valve spring set flow in steering control valve；K
For the orifice shapes coefficient of the spool of the first reversal valve 2；A is the first equivalent orifice size of proportional reversing valve mouth, and F is the first ratio
Commutate valve spring force；N is complete machine actual engine speed；Q is quantitative pumpage；S is the first proportional reversing valve core active area；
∝ is the second proportional reversing valve inflow-rate of water turbine and its open area fraction coefficient, and e is the second proportional reversing valve core opening area and its
The proportionality coefficient of displacement.
When loader-digger is not turned to, the flow that hydraulic pump 4 provides passes through the control stream of turning gradient control valve 40
To work system 300, loader-digger, which does not carry out turning to, is directed to two states：First, overall operation, equipment act；
Second is that complete machine straight-line travelling or idling parking.
When overall operation, equipment action, 2/2-way solenoid directional control valve 70 is powered, and electromagnet overcomes spring force to make two
Position two electric change valves, 70 upper access system, flow into work system 200 hydraulic oil initially enter loading valve 60, then by
The outlet of loading valve 60 and the access of fluid tank are cut off in 2/2-way solenoid directional control valve 70, hydraulic oil, which enters, excavates the progress of valve 50
Operation.When complete machine straight-line travelling or idling parking, 2/2-way solenoid directional control valve 70 is in off-position, and spring force makes two
The next access system of position two electric change valve 70, flows into the hydraulic oil of work system 200 after loading valve 60, directly from
2/2-way solenoid directional control valve 70 returns to fluid tank 7.It is to be noted that under both the above state, the stream of 5 output of the second pump
Amount flows back to fluid tank 7 through overflow valve 8.
The foregoing is merely exemplary embodiment of the present invention, are not intended to limit the invention, all spirit in the present invention
Within principle, any modification, equivalent replacement, improvement and so on should all be included in the protection scope of the present invention.
Claims (11)
1. a kind of automobile hydraulic system, which is characterized in that including：
First pump (4) and the second pump (5), are driven by the engine (3) of vehicle；
Steering control valve (30), including the first reversal valve (2), the second reversal valve (9) and pressure-control valve (15), described first changes
To valve (2) there is import, first outlet and second outlet, first reversal valve (2) can be connected to first pump (4),
The first outlet of first reversal valve (2) is used to be connected to the steering of vehicle, the second outlet of first reversal valve (2)
It being connected to the pressure-control valve (15), second reversal valve (9) has import, first outlet and a second outlet, and described the
The import of two reversal valves (9) can be connected to second pump (5), and the first outlet of second reversal valve (9) is for being connected to
The steering of vehicle, the second outlet of second reversal valve (9) are used to be connected to fluid tank (7),
The steering control valve (30) has first state and the second state,
In the first state, the import of first reversal valve (2) is connected with the first outlet of first reversal valve (2),
The import of second reversal valve (9) is connected with the second reversal valve (9) first outlet, so that the first pump (4) and described the
Two pumps (5) provide hydraulic fluid to the steering；
In second state, the import of first reversal valve (2) goes out with the first reversal valve (2) first outlet and second
It mouthful is both turned on, so that the pressure-control valve (15) controls the first outlet of first reversal valve (2) to the steering
The pressure of the hydraulic fluid of output.
2. automobile hydraulic system according to claim 1, which is characterized in that the pressure-control valve (15) includes back pressure
Valve.
3. automobile hydraulic system according to claim 1, which is characterized in that first reversal valve (2) also has control
Fluid inlet, the control fluid inlet is used to introduce the hydraulic fluid of the first pump (4) output, in the hydraulic fluid
Pressure make the import of first reversal valve (2) and the first reversal valve (2) first outlet and the when being higher than predetermined value
Two outlets are both turned on.
4. automobile hydraulic system according to claim 3, which is characterized in that first reversal valve (2) includes the first ratio
Example reversal valve, first reversal valve (2) include the first spool (26), and first spool (26), which has, only makes described first to change
The first position that is connected to the first outlet of valve (2) with import and the first outlet and second of first reversal valve (2) is made to go out
The second position that is connected with import of mouth, first spool (26) at the first position, first reversal valve (2)
The pressure of first outlet output hydraulic pressure fluid is less than the pressure for the hydraulic fluid that the first reversal valve (2) import introduces.
5. automobile hydraulic system according to claim 4, which is characterized in that
First reversal valve (2) further include setting in the first chamber of the first end of the first spool (26) and setting described the
The second chamber of the second end of one spool (26), the inlet communication of the first chamber and the first reversal valve (2), to introduce institute
State the hydraulic fluid that the first spool (26) is pushed to the first position, the second chamber and first reversal valve (2)
First outlet is connected to, to introduce the hydraulic fluid for pushing first spool (26) to the second position.
6. automobile hydraulic system according to claim 5, which is characterized in that first reversal valve (2) further includes first
Elastomeric element (27), first elastomeric element (27) are arranged in the second chamber.
7. automobile hydraulic system according to claim 1, which is characterized in that second reversal valve (9) further includes control
Fluid inlet, the control fluid inlet is used to introduce the hydraulic fluid of the first pump (4) output, in the hydraulic fluid
Pressure be less than predetermined value when the import of second reversal valve (9) is connected with first outlet.
8. automobile hydraulic system according to claim 7, which is characterized in that second reversal valve (9) includes the second valve
Core (29), setting are in the third chamber of the first end of second spool (29) and setting the second of second spool (29)
4th chamber at end, second spool (29) have make the import of the second reversal valve (9) be connected with first outlet first
The second position for setting and making import to be connected with second outlet, the first outlet of the third chamber and first reversal valve (2)
Conducting, to introduce hydraulic fluid from second spool (29) to its second position that push, the 4th chamber and described the
The import of two reversal valves (9) is connected, and is pushed second spool (29) to the first position of second spool with introducing
Hydraulic fluid.
9. automobile hydraulic system according to claim 8, which is characterized in that second reversal valve (9) further includes second
Elastomeric element (210), second elastomeric element (210) are arranged in the third chamber.
10. automobile hydraulic system according to claim 1, which is characterized in that second reversal valve (9) includes the second ratio
Example reversal valve.
11. a kind of engineering truck, which is characterized in that including the automobile hydraulic system described in any one of claims 1 to 10.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201710029806.7A CN106762928B (en) | 2017-01-17 | 2017-01-17 | Automobile hydraulic system and engineering truck with it |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201710029806.7A CN106762928B (en) | 2017-01-17 | 2017-01-17 | Automobile hydraulic system and engineering truck with it |
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| CN106762928B true CN106762928B (en) | 2018-10-16 |
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| CN111794958A (en) * | 2020-07-16 | 2020-10-20 | 潍柴动力股份有限公司 | Hydraulic pump and vehicle with same |
Citations (5)
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|---|---|---|---|---|
| CN102229328A (en) * | 2011-05-05 | 2011-11-02 | 四川大学 | Vehicle mechanical energy-saving hydraulic system with multi-pump confluence |
| CN102434502A (en) * | 2011-12-23 | 2012-05-02 | 四川大学 | Frequency-conversion pump controlled steering hydraulic system for loader |
| CN103016457A (en) * | 2012-12-05 | 2013-04-03 | 中联重科股份有限公司 | Hydraulic pump control system, vehicle and steering hydraulic system of vehicle |
| CN103085865A (en) * | 2012-11-30 | 2013-05-08 | 广西柳工机械股份有限公司 | Load sensitive turning hydraulic system of loading machine |
| CN206478053U (en) * | 2017-01-17 | 2017-09-08 | 徐工集团工程机械有限公司 | Automobile hydraulic system and the engineering truck with it |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5896041B2 (en) * | 2012-12-19 | 2016-03-30 | 株式会社島津製作所 | Hydraulic circuit and cargo handling vehicle |
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2017
- 2017-01-17 CN CN201710029806.7A patent/CN106762928B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102229328A (en) * | 2011-05-05 | 2011-11-02 | 四川大学 | Vehicle mechanical energy-saving hydraulic system with multi-pump confluence |
| CN102434502A (en) * | 2011-12-23 | 2012-05-02 | 四川大学 | Frequency-conversion pump controlled steering hydraulic system for loader |
| CN103085865A (en) * | 2012-11-30 | 2013-05-08 | 广西柳工机械股份有限公司 | Load sensitive turning hydraulic system of loading machine |
| CN103016457A (en) * | 2012-12-05 | 2013-04-03 | 中联重科股份有限公司 | Hydraulic pump control system, vehicle and steering hydraulic system of vehicle |
| CN206478053U (en) * | 2017-01-17 | 2017-09-08 | 徐工集团工程机械有限公司 | Automobile hydraulic system and the engineering truck with it |
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Effective date of registration: 20220729 Address after: 221004 26 Tuo Lan Shan Road, Xuzhou economic and Technological Development Zone, Jiangsu Patentee after: JIANGSU XUGONG ENGINEERING MACHINERY RESEARCH INSTITUTE Co.,Ltd. Address before: 221004 Industrial Zone, Xuzhou Economic Development Zone, Jiangsu, China Patentee before: XCMG CONSTRUCTION MACHINERY Co.,Ltd. |